CN111365260B

CN111365260B - Two-stage dynamic pressure gas suspension centrifugal compressor, refrigerant circulation system and refrigeration equipment

Info

Publication number: CN111365260B
Application number: CN201811593758.5A
Authority: CN
Inventors: 刘华; 张治平; 李宏波; 陈玉辉; 叶文腾
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2018-12-25
Filing date: 2018-12-25
Publication date: 2025-01-03
Anticipated expiration: 2038-12-25
Also published as: CN111365260A

Abstract

The present disclosure relates to a compressor, a refrigerant circulation system and a refrigeration device. The compressor includes: a housing and a motor drive system; the motor drive system includes a compressor rotor and a motor stator, the housing has a motor accommodating chamber and a compression chamber, the motor stator is fixedly arranged in the motor accommodating chamber and has a rotor mounting hole, and the compressor rotor is rotatably arranged in the housing; the motor stator is provided with a reflux flow hole extending along the axial direction of the compressor rotor, and part of the fluid in the motor accommodating chamber flows from one end of the motor stator to the other end of the motor stator through the reflux flow hole. The present disclosure can improve the internal cooling effect of the compressor.

Description

Double-stage dynamic pressure air suspension centrifugal compressor, refrigerant circulating system and refrigeration equipment

Technical Field

The disclosure relates to the field of compressors, and in particular relates to a two-stage dynamic pressure gas suspension centrifugal compressor, a refrigerant circulating system and refrigeration equipment.

Background

Centrifugal refrigeration compressors are high-speed compressors, in which the compressor rotor rotates at high speed during operation, and reliable bearings are required to support the rotor. The bearings used in conventional rotors mainly comprise rolling bearings, oil film bearings and magnetic suspension bearings. For rolling bearings and oil film bearings, the compressor requires an additional oil lubrication system and a complex oil supply circuit system, while having compatibility with the lubricant, and a separate system needs to be added to the system, which can result in an excessively complex and bulky overall system.

Because the bearing capacity of the rolling bearing and the oil film bearing is higher, the motor rotor used by the conventional centrifugal compressor is of an integrated structure, and the weight of the compressor rotor of the structure is relatively heavy, so that the critical rotating speed of the rotor is not beneficial to the improvement. When the integrated structure is used for manufacturing a large rotor, the processing process is relatively complicated, the requirement on equipment is relatively high, and the cost can be increased.

In addition, during operation of the compressor, heat is generated due to mechanical losses, mainly as a result of stator winding losses and rotor eddy current interactions, causing a sharp rise in the temperature inside the compressor. Without cooling, excessive heat will affect the life of the insulating material, reduce the output power of the motor, and cause the permanent magnets to demagnetize, burning out the compressor components in severe cases.

Therefore, in order to solve the complex oil way system of the compressor, the oil-free and environment-friendly magnetic suspension bearing appears. For the magnetic suspension bearing, an oil supply system and a separation system are omitted, but a more complex control system is added, and as the magnetic suspension bearing needs a stable power supply, a protection system is added to prevent the system from being suddenly powered off, so that the maintenance cost of the whole compressor is increased, and the structure is more complicated.

In order to solve the problem of critical rotation speed of the rotor of the compressor, the existing compressor mainly increases the critical rotation speed of the rotor by reducing the length of the rotor or increasing the rigidity of the bearing. However, the reduction in the length direction of the rotor is affected by the size of each component, and the optimization can be performed to a relatively small extent. The rigidity of the bearing is improved, the volume of the bearing is required to be increased at high rotation speed, the whole compressor is enlarged, and the development trend of miniaturization is violated.

For motor cooling problems, most centrifugal compressors of the prior art use evaporative or hydrojet cooling motors. The method mainly comprises the step that after a liquid refrigerant passes through a motor cooling flow passage, the heat on the surface of a stator is absorbed to be changed into a gas state. And then discharged from the front end of the motor cavity, and returns to the rear end of the motor cavity through a gap between the stator and the rotor to cool the surface of the motor rotor again. However, this cooling mainly involves the rotor and stator surfaces, the internal cooling is insufficient, the rotor has a concentrated temperature inside, and when the temperature is too high, the permanent magnets have demagnetizing phenomenon.

Disclosure of Invention

In view of the above, embodiments of the present disclosure provide a compressor, a refrigerant circulation system, and a refrigeration apparatus, which can improve the internal cooling effect of the compressor.

In one aspect of the present disclosure, a compressor is provided, comprising a housing and a motor drive system, the motor drive system comprising a compressor rotor and a motor stator, the housing having a motor receiving cavity and a compression cavity, the motor stator being fixedly disposed within the motor receiving cavity and having a rotor mounting hole, the compressor rotor being rotatably disposed within the housing;

And a reflux through hole extending along the axial direction of the compressor rotor is arranged in the motor stator, and part of fluid in the motor accommodating cavity flows from one end of the motor stator to the other end of the motor stator through the reflux through hole.

In some embodiments, the reflow via includes:

A return air hole above the compressor rotor for circulating air and/or,

And the liquid return hole is positioned below the compressor rotor and is used for circulating liquid.

In some embodiments, a compression system is also included that includes a volute having at least two volute lines over different angular ranges.

In some embodiments, the at least two volute lines include a first volute line and a second volute line distributed along a direction of airflow within the volute, the parting interface of the first volute line and the second volute line being 80 ° to 100 ° relative to a direction that is perpendicular from a center of the volute toward an airflow outlet of the volute.

In some embodiments, the first volute line is D-shaped, trapezoidal, or oval, and the second volute line is circular greater than 180 °.

In some embodiments, the compressor rotor comprises:

A motor rotor which is positioned in the motor accommodating cavity and penetrates through the rotor mounting hole and is provided with a hollow part and a vent hole, wherein the vent hole is communicated with the hollow part and the motor accommodating cavity, and

The compression unit rotating part is positioned in the compression cavity, is fixedly connected to the end part of the motor rotor and forms an air inlet passage communicated with the hollow part with the motor rotor, and fluid in the compression cavity enters the hollow part through the air inlet passage and enters the motor accommodating cavity through the vent hole.

In some embodiments, the compressor rotor comprises a motor rotor positioned in the motor accommodating cavity and penetrating the rotor mounting hole, and provided with a hollow part and a vent hole, wherein the vent hole is communicated with the hollow part and the motor accommodating cavity, and the motor rotor comprises:

A permanent magnet;

A first end shaft section fixedly arranged at a first end of the permanent magnet, and

And the second end shaft section is fixedly arranged at the second end of the permanent magnet.

In some embodiments, the compressor is a centrifugal compressor and the compression unit rotating portion is an impeller.

In some embodiments, further comprising a gas bearing by which the compressor rotor is rotatably supported within the housing.

In some embodiments, the first end shaft section includes a first axial bore and a plurality of first perforations communicating the first axial bore with the motor receiving cavity, the hollow portion includes the first axial bore, the vent includes the first perforations, and/or,

The second end shaft section includes a second axial bore and a plurality of second perforations communicating the second axial bore with the motor receiving cavity, the hollow portion includes the second axial bore, and the vent includes the second perforations.

In some embodiments, the end of the motor rotor is provided with an axial recess for mating with the compression unit rotating part, a first leakage groove recessed radially outward is provided on the side wall of the axial recess, the air intake passage includes the first leakage groove, and/or

The end face of the compression unit rotating part is matched with the end face of the motor rotor, the end face of the compression unit rotating part is provided with a second leakage groove, the air inlet passage comprises the second leakage groove, and/or

The end face of the compression unit rotating part is matched with the end face of the motor rotor, a third leakage groove is formed in the end face of the motor rotor, and the air inlet passage comprises the third leakage groove.

In some embodiments, the housing is provided with:

A cooling fluid inlet;

A spiral groove arranged on the inner wall of the shell and forming a spiral cooling flow passage with the outer peripheral surface of the motor stator, a first end of the spiral cooling flow passage being communicated with the cooling fluid inlet, a second end of the spiral cooling flow passage being communicated with the motor accommodating cavity at one end of the motor stator, and

And the cooling fluid outlet is communicated with the motor accommodating cavity at the other end of the motor stator.

Therefore, according to the embodiment of the disclosure, the backflow through hole extending along the axial direction of the compressor rotor is arranged in the motor stator, so that part of fluid in the motor accommodating cavity flows from one end of the motor stator to the other end of the motor stator through the backflow through hole, cooling inside the motor stator is realized by using the backflow through hole, the flow area of the fluid in backflow is increased, and heat dissipation of the motor is facilitated.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments of the disclosure and together with the description, serve to explain the principles of the disclosure.

The disclosure may be more clearly understood from the following detailed description taken in conjunction with the accompanying drawings in which:

FIG. 1 is a schematic structural view of some embodiments of a compressor according to the present disclosure;

FIGS. 2-3 are schematic structural views of two motor rotors, respectively, in some embodiments of compressors according to the present disclosure;

fig. 4a and 4b are schematic cross-sectional and structural views, respectively, of a volute in some embodiments of compressors according to the present disclosure;

FIGS. 5a and 5b are schematic cross-sectional views of a motor rotor and a motor stator, respectively, in some embodiments of compressors according to the present disclosure;

FIG. 6 is a schematic diagram of internal cooling fluid circulation in some embodiments of a compressor according to the present disclosure;

FIG. 7 is a schematic structural view of a compressor rotor in some embodiments of a compressor according to the present disclosure;

FIG. 8 is a schematic cross-sectional view of the motor rotor of the embodiment of FIG. 7;

FIG. 9 is a schematic view of the movable protrusion of the lock lever of the embodiment of FIG. 7;

FIG. 10 is a schematic structural view of a compressor rotor in some embodiments of a compressor according to the present disclosure;

FIG. 11 is a schematic structural view of connecting rods in a compressor rotor according to some embodiments of the compressor of the present disclosure;

FIG. 12 is a schematic structural view of a lock nut in a compressor rotor according to some embodiments of the compressor of the present disclosure;

FIG. 13 is a schematic structural view of a compressor rotor according to further embodiments of the compressor of the present disclosure;

FIG. 14 is a schematic view of a construction of other embodiments of a compressor according to the present disclosure;

FIG. 15 is a schematic structural view of a compressor rotor in some embodiments of a compressor according to the present disclosure;

FIG. 16 is a schematic view of a compressor rotor in accordance with further embodiments of the compressor of the present disclosure;

FIGS. 17-20 are schematic structural views of various motor rotors in some embodiments of compressors according to the present disclosure, respectively;

FIG. 21 is a schematic structural view of still other embodiments of compressors according to the present disclosure;

FIGS. 22-23 are schematic structural views of two compressor rotors, respectively, in some embodiments of compressors according to the present disclosure;

FIG. 24 is a schematic view of a structure of further embodiments of a compressor according to the present disclosure;

FIG. 25 is a schematic view of the internal cooling fluid circulation in the embodiment of FIG. 24;

FIG. 26 is a schematic cross-sectional structural view of a motor rotor in some embodiments of a compressor according to the present disclosure;

FIGS. 27-29 are schematic illustrations of three raised structures of a motor rotor surface in some embodiments of the compressor of the present disclosure, respectively;

FIG. 30 is a schematic view of a construction of other embodiments of a compressor according to the present disclosure;

FIG. 31 is a schematic view of the assembly of the bearing and bearing support of the embodiment of FIG. 30;

FIGS. 32 and 33 are schematic perspective and cross-sectional views, respectively, of a bearing support in some embodiments of compressors according to the present disclosure;

FIG. 34 is a partial structural schematic diagram of some embodiments of a compressor according to the present disclosure;

FIG. 35 is a schematic view of a combination of a fixed plate and a bearing mount in a bearing support assembly in some embodiments of a compressor according to the present disclosure;

FIG. 36 is a schematic view of the bearing support structure of the embodiment of FIG. 35;

FIG. 37 is a schematic view of a combined machining of bearing support assemblies in some embodiments of a compressor according to the present disclosure;

FIGS. 38 and 39 are schematic perspective and cross-sectional views, respectively, of a bearing support in further embodiments of a compressor according to the present disclosure;

FIG. 40 is a partial schematic view of a construction of other embodiments of a compressor according to the present disclosure;

FIG. 41 is a schematic view of a structure of some embodiments of a compressor according to the present disclosure;

FIGS. 42 and 43 are schematic cross-sectional and side structural views, respectively, of a diffuser in some embodiments of compressors according to the present disclosure;

FIG. 44 is a partial structural schematic diagram of some embodiments of a compressor according to the present disclosure;

FIG. 45 is a schematic view of a construction of other embodiments of a compressor according to the present disclosure;

FIG. 46 is a schematic structural view of still other embodiments of compressors according to the present disclosure;

FIG. 47 is a schematic view of mounting structures of a diffuser, a thrust disc, and a stationary plate in further embodiments of compressors according to the present disclosure;

FIG. 48 is a schematic view of the mounting structure of a diffuser, thrust disc, fixed plate, and bearing support in further embodiments of a compressor according to the present disclosure;

FIG. 49 is a schematic view of a fixed plate and bearing support in an integrated configuration in accordance with still other embodiments of the compressor of the present disclosure;

FIG. 50 is a schematic view of a mounting structure of a bearing support and a housing in further embodiments of a compressor according to the present disclosure;

Fig. 51 is a schematic structural view of a sealing structure in further embodiments of a compressor according to the present disclosure.

It should be understood that the dimensions of the various elements shown in the figures are not drawn to actual scale. Further, the same or similar reference numerals denote the same or similar members.

Detailed Description

Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. The description of the exemplary embodiments is merely illustrative, and is in no way intended to limit the disclosure, its application, or uses. The present disclosure may be embodied in many different forms and is not limited to the embodiments described herein. These embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art. It should be noted that the relative arrangement of parts and steps, the composition of materials, numerical expressions and numerical values set forth in these embodiments should be construed as exemplary only and not limiting unless otherwise specifically stated.

The terms "first," "second," and the like, as used in this disclosure, do not denote any order, quantity, or importance, but rather are used to distinguish one element from another. The word "comprising" or "comprises" and the like means that elements preceding the word encompass the elements recited after the word, and not exclude the possibility of also encompassing other elements. "upper", "lower", "left", "right", etc. are used merely to indicate relative positional relationships, which may also be changed when the absolute position of the object to be described is changed.

In this disclosure, when a particular device is described as being located between a first device and a second device, there may or may not be an intervening device between the particular device and either the first device or the second device. When it is described that a particular device is connected to other devices, the particular device may be directly connected to the other devices without intervening devices, or may be directly connected to the other devices without intervening devices.

All terms (including technical or scientific terms) used in this disclosure have the same meaning as commonly understood by one of ordinary skill in the art to which this disclosure belongs, unless specifically defined otherwise. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.

Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but are intended to be part of the specification where appropriate.

As shown in fig. 1, an internal structural schematic of some embodiments of the compressor of the present disclosure is shown. Referring to fig. 1 and 2-6, the present disclosure provides a compressor including a housing a-10, a compression system, a motor drive system, and a circulating air supply self-cooling system. In fig. 1, a housing a-10 has a motor accommodation chamber a-14 and a compression chamber.

The motor drive system may include a motor stator A-30 and a compressor rotor A-20. The motor stator a-30 may be fixedly disposed within the motor receiving cavity a-14 and have a rotor mounting hole a-31. The compressor rotor A-20 is rotatably provided in the housing A-10, and includes a motor rotor A-21 and a compression unit rotating part.

The motor rotor A-21 is positioned in the motor accommodating cavity A-14 and penetrates through the rotor mounting hole A-31. The motor rotor a-21 has a hollow portion and a vent hole (the vent hole is not shown in fig. 1) that communicates with both the hollow portion and the motor accommodation chamber a-14.

The compression system may include a volute, diffuser, bearing support, and the like. And the housing A-10 includes a motor cylinder A-11 and a volute provided at least one end of the motor cylinder A-11 in the axial direction. The volute may have at least two volute lines over different angular ranges. For example, the housing A-10 includes a motor cartridge A-11 and first and second volutes A-12 and A-13 disposed at axial ends of the motor cartridge A-11.

Referring to fig. 4a and 4b, in some embodiments, at least two types of volute lines include a first volute line a-1a and a second volute line a-1b distributed along the direction of airflow within the volute, where the parting interface of the first volute line a-1a and the second volute line a-1b is 80 ° to 100 ° with respect to a direction perpendicular to the direction of airflow outlet of the volute from the center of the volute, which ensures that flow velocity changes in the volute are not too severe. The parting interface is preferably at 90 ° with respect to a direction from the center of the volute perpendicularly directed towards the air flow outlet of the volute. Taking 90 ° as an example, the first volute line at 0 ° to 90 ° may take a D-shape, i.e. a shape similar to the capital letter D. The shape can enable the volute to be easy to clean sand during casting, and the structure is simpler. Instead of using a D-shape, the first volute line may also have a trapezoid or an ellipse. And the second volute line of 90-360 degrees is preferably circular with an angle greater than 180 degrees. That is, a large portion of the circular volute line is located inside the volute, which may reduce the outer wall size of the volute, thereby making the volute more compact. In addition, the volute can be subdivided into a plurality of transition sections at the parting interface so as to realize uniform transition of two volute molded lines, thereby eliminating fluctuation of air flow when flowing through the parting interface.

The compression unit rotating part is positioned in the compression cavity, is fixedly connected to the end part of the motor rotor A-21 and forms an air inlet passage communicated with the hollow part with the motor rotor A-21, and fluid in the compression cavity enters the hollow part through the air inlet passage and enters the motor accommodating cavity A-14 through the vent hole.

According to the compressor disclosed by the embodiment of the disclosure, the hollow part and the vent holes communicated with the hollow part and the motor accommodating cavity A-14 are formed in the motor rotor A-21, the air inlet passage communicated with the hollow part is formed between the compression unit rotating part and the motor rotor A-21, fluid in the compression unit rotating part can enter the hollow part through the air inlet passage, and along with the rotation of the motor rotor A-21, the fluid can flow out of the vent holes to the motor accommodating cavity A-14, so that the interior of the motor rotor A-21 can be cooled, the heating concentration problem of the motor rotor A-21 can be solved, the full cooling of a motor in the compressor is guaranteed, and the efficient and reliable operation is realized.

As shown in fig. 1, in some embodiments, the compressor may be a centrifugal compressor and the compression unit rotating portion is an impeller of the centrifugal compressor. The compression unit rotating part may be provided only at one side of the motor rotor, or may be provided at both sides of the motor rotor, respectively. The compression unit rotating parts on each side can be single-stage or multi-stage. For example, when the compression unit rotation portion is an impeller, the number of impellers on the motor rotor side may be one or two or more.

As shown in FIG. 1, in some embodiments, compressor rotor A-20 includes a motor rotor A-21, a primary impeller A-22, and a secondary impeller A-23. The compressor rotor A-20 further includes a first lock lever A-24, a second lock lever A-25, a first lock nut A-26, and a second lock nut A-27. The first-stage impeller A-22 is fixed at the left end of the motor rotor A-21 through a first locking rod A-24 and a first locking nut A-26, and the second-stage impeller A-23 is fixed at the right end of the motor rotor A-21 through a second locking rod A-25 and a second locking nut A-27. The first locking rod A-24 and the second locking rod A-25 can be integrally arranged with the motor rotor A-21, or can be separately arranged and then connected together in a connecting mode such as threaded connection. Corresponding to the first-stage impeller A-22 and the second-stage impeller A-23, two compression chambers are respectively a first-stage compression chamber A-15 and a second-stage compression chamber A-16. The primary impeller A-22 is positioned in the primary compression cavity A-15, and the secondary impeller A-23 is positioned in the secondary compression cavity A-16.

In some embodiments, not shown, the compressor may have other compression unit rotational portions, such as a screw, a moving scroll, a roller, etc. for example, the compression unit rotational portions may be provided by a screw.

As shown in FIG. 1, in some embodiments, the compressor further includes a motor stator A-30, a first diffuser A-40, a first bearing support A-50, a first radial bearing A-60, a second diffuser A-60, a second bearing support A-80, and a second radial bearing A-90, and first and second thrust bearings, not labeled.

As shown in fig. 1 and 6, a motor stator a-30 is fixed to a housing a-10 and has a rotor mounting hole a-31, and a motor rotor a-21 is penetrated in the rotor mounting hole a-31.

The first bearing support A-50 and the second bearing support A-80 are respectively fixed inside the motor cylinder A-11 of the shell A-10 and are respectively positioned at two axial ends of the motor stator A-30. The first radial bearing A-60 is located in the first bearing support A-50 and the second radial bearing A-90 is located in the second bearing support A-80. The first radial bearing a-60 and the second radial bearing a-90 are supported at both axial ends of the motor rotor a-21, respectively, so as to support the motor rotor a-21 in the motor accommodation chamber a-14 in the motor cylinder a-11 of the housing a-10.

The compressor rotor a-20 further includes a thrust disk a-28 provided at one axial end (left end in fig. 1) of the motor rotor a-21. A first thrust bearing is arranged between the first bearing support A-50 and the thrust disk A-28, and a second thrust bearing is arranged at one end of the first diffuser A-40, which is far away from the diffuser structure on the diffuser A-40, so that the motor rotor A-21 is positioned in the motor accommodating cavity A-14 of the housing A-10 at the upper limit in the axial direction.

The first diffuser A-40 and the second diffuser A-70 have diffusion structures, such as blades or diffusion surfaces, respectively, and are integrated with sealing structures, such as comb teeth, so that the first diffuser A-40 and the second diffuser A-70 are also used for isolating the space where the first-stage compression cavity A-15 and the motor accommodating cavity A-14 and the second impeller A-23 of the second-stage compression cavity A-16 are located from the motor accommodating cavity A-14, respectively, and preventing fluid in the first-stage compression cavity A-15 and the second-stage compression cavity A-16 from leaking into the motor accommodating cavity A-14 through gaps between the compressor rotor A-20 and the first diffuser A-40 and gaps between the compressor rotor A-20 and the second diffuser A-70.

As shown in fig. 1-3, 6, in some embodiments, the motor rotor includes permanent magnets a-211. The permanent magnets A-211 may generate a magnetic field for driving the motor rotor A-21 and the compressor rotor A-20 to rotate when the windings of the motor stator A-30 are energized.

The embodiment of the disclosure is suitable for motor cooling of various compressors, particularly suitable for motor cooling of compressors adopting permanent magnet synchronous motors, and is beneficial to solving the uniformity problem of motor cooling and avoiding motor damage caused by demagnetization of permanent magnets of a motor rotor in a high-temperature environment due to long-term operation.

As shown in fig. 1-3, 6, in some embodiments, motor rotor a-21 includes permanent magnets a-211, a first end shaft section a-212, and a second end shaft section a-213.

The permanent magnets a-211 may be solid cylinders as shown in fig. 2 or hollow cylinders with through holes as shown in fig. 3. The permanent magnet A-211 is used as a motor rotor A-21 and together with a motor stator A-30 to form a motor for driving the compressor rotor A-20 to rotate. The material of the permanent magnets a-211 is, for example, magnetic steel.

The first end shaft section A-212 is fixedly disposed at a first end of the permanent magnet A-211. The second end shaft section A-213 is fixedly disposed at a second end of the permanent magnet A-211.

As shown in fig. 2 and 3, in some embodiments, the motor rotor a-21 further includes a mounting sleeve a-214 integrally disposed at an end of the first end shaft section a-212 proximate the permanent magnet a-211. The permanent magnet A-211 and the second end shaft section A-213 are fixedly mounted in the mounting sleeve A-214 by means of a shrink fit.

In some embodiments, not shown, separate mounting sleeves may be provided, with the first end shaft section, the permanent magnet, and the second end shaft section all nested within the mounting sleeve by way of a shrink fit.

As shown in fig. 2 and3, in some embodiments, the first end shaft section a-212 includes a first axial bore a-2121 and a plurality of first perforations a-2122 that communicate the first axial bore a-2121 with the motor-receiving cavity a-14, the hollow portion includes the first axial bore a-2121, and the vent includes the first perforations a-2122. The second end shaft section A-213 includes a second axial bore A-2131 and a plurality of second perforations A-2132 communicating the second axial bore A-2131 with the motor receiving cavity A-14, the hollow including the second axial bore A-2131, the vent including the second perforations A-2132.

As shown in fig. 2, 3 and 6, the hollow portion and the vent hole are axisymmetrically distributed. The hollow part is an axial hole, and the vent hole is a radial hole. The plurality of vent holes are respectively and uniformly distributed on the corresponding shaft section along the axial direction and the circumferential direction. The number of ventilation holes of the two end shaft sections may be set to be the same and/or the angle may be set to be the same. The above arrangement is advantageous for dynamic balancing of the motor rotor A-21.

The plurality of vent holes of the motor rotor A-21 can be orderly arranged, staggered or spirally arranged, etc. The cross-sectional shape of the vent hole is not limited, and may be circular, square, triangular, or the like.

As shown in FIG. 2, in some embodiments, the first axial bore A-2121 and the second axial bore A-2131 are both axial through holes. In fig. 2, the permanent magnets a-211 are solid cylinders made of permanent magnets. At this time, air intake passages are provided at both ends of the motor rotor, respectively, and each air intake passage supplies fluid to the hollow portion at the corresponding end for cooling the motor rotor a-21.

For better cooling, the permanent magnet may be provided with one or several holes. These holes allow on the one hand the fluid to enter the interior of the permanent magnets for better cooling of the motor rotor, and on the other hand the hole or holes of the aforementioned holes communicating the two axial end faces of the permanent magnets also serve as hollows communicating the two sides of the motor rotor. In this case, the intake passages may be provided at both ends of the motor rotor, or the intake passages may be provided only at one end of the motor rotor.

As shown in FIG. 3, in some embodiments, one of the first axial hole A-2121 and the second axial hole A-2131 is an axial through hole, the other is a blind hole with an open end facing the permanent magnet A-211, and the permanent magnet A-211 has a third axial hole A-2111 communicating the first axial hole A-2121 and the second axial hole A-2131. The third axial hole A-2111 is preferably sized to have a diameter of less than or equal to 4mm, as affected by the permanent magnet material.

As shown in fig. 1 to 3 and 6, in some embodiments, an end portion of the motor rotor a-21 is provided with an axial recess for engagement with the compression unit rotating portion, and a first leakage groove recessed radially outward is provided on a side wall of the axial recess, and the intake passage includes the first leakage groove. In fig. 2 or 3, a first axial recess a-2123 is provided at the left end of the first end shaft section a-211 at the left end of the motor rotor a-21, and a second axial recess a-2133 is provided at the right end of the second end shaft section a-212 at the right end of the motor rotor a-21.

The first leakage groove of an embodiment will be described below with reference to fig. 5a by taking the left end face of the motor rotor a-21 as an example. As shown in fig. 5a, four first leakage grooves a-2124 are provided on a sidewall of a first axial recess a-2123 of a left end portion of a first end shaft section a-211 of a left end of the motor rotor a-21. The four first leakage grooves A-2124 are uniformly distributed along the axial direction of the motor rotor A-21. The first leakage groove a-2124 has a V-shaped cross-sectional shape.

In the embodiment shown in fig. 2, first leakage grooves are provided in the axial recesses at both the left and right ends of the motor rotor a-21. In the embodiment shown in fig. 3, a first leakage groove is provided in the axial recess a-2133 of the right end of the motor rotor a-21.

As shown in FIG. 2, a first axial recess A-2123 is provided at an end of the first axial hole A-2121 and a second axial recess A-2133 is provided at an end of the first axial hole A-2131.

As shown in FIG. 3, the first axial recess A-2123 is spaced apart from the first axial bore A-2121 at both ends of the first end shaft section A-212 with the middle being isolated by a partition wall A-2125. The second axial recess A-2133 is disposed at an end of the first axial bore A-2131.

In some embodiments, an end face of the compression unit rotating portion is fitted with an end face of the motor rotor a-21, the end face of the compression unit rotating portion being provided with a second leakage groove, and the intake passage includes the second leakage groove.

In some embodiments, the end face of the compression unit rotating portion is fitted with the end face of the motor rotor a-21, the end face of the motor rotor a-21 being provided with a third leakage groove, and the intake passage includes the third leakage groove.

In order for the intake passage to introduce the fluid in the compression chamber into the hollow portion of the motor rotor a-21, in some embodiments, two or three of the first leakage groove, the second leakage groove, and the third leakage groove may be included at the same time.

The cross-sectional shape of the various leak grooves is not limited, and may be, for example, arc, square, trapezoid, U-shape, or the like, in addition to V-shape. The number of the various leak grooves is not limited, and may be smaller than 4 or larger than 4, for example. The cross-section of the leakage groove is preferably sized to accommodate the passage of fluid for cooling the motor rotor a-21.

In the above embodiment, the motor rotor A-21 comprises a three-section structure, the left and right end shaft sections are processed into a hollow structure, and the middle is an integral permanent magnet, so that the structure is simplified, and the assembly is reduced. The motor rotor A-21 is provided with a plurality of vent holes, a plurality of perforations are formed on the motor rotor A-21 to form honeycomb-shaped holes, and when the motor rotor A-21 rotates at a high speed, heat in the motor rotor A-21 can be taken away by flowing fluid such as refrigerant through the hollow part and the vent holes.

As shown in fig. 1, 5b and 6, in some embodiments, the motor stator a-30 has an axially disposed return through hole therein. The fluid in the motor housing chamber a-14 flows partially from one end of the motor stator a-30 to the other end of the motor stator a-30 through the return through hole, and partially flows from one end of the motor stator a-30 to the other end of the motor stator a-30 through the fit clearance a-311 between the rotor mounting hole a-31 and the motor rotor a-21.

As shown in fig. 1, 5 and 6, the return through hole includes a return hole a-32 above the compressor rotor a-20 for circulating gas and/or a return hole a-33 below the compressor rotor a-20 for circulating liquid. Referring to FIG. 5, in some embodiments, the return vent includes three return air holes A-32 and three return liquid holes A-33.

The arrangement of the backflow through holes can cool the inside of the motor stator A-30, and the flow area of fluid in backflow is increased, so that heat dissipation of the motor is facilitated.

As shown in FIG. 6, in some embodiments, the housing A-10 is further provided with a cooling fluid inlet A-111, a spiral groove A-112, and a cooling fluid outlet A-113. The spiral groove A-112 is arranged on the inner wall of the motor cylinder A-11 of the shell A-10, forms a spiral cooling flow passage with the outer peripheral surface of the motor stator A-30, and a first end of the spiral cooling flow passage is communicated with the cooling fluid inlet A-111, and a second end of the spiral cooling flow passage is communicated with the motor accommodating cavity A-14 at one end (the left end shown in FIG. 6) of the motor stator A-30. The cooling fluid outlet a-113 communicates with the motor housing chamber a-14 at the other end (right end shown in fig. 6) of the motor stator a-30. The cooling fluid outlet a-113 is provided at the right end of the motor cylinder a-11.

After the gas in the compression cavity leaks into the hollow part of the motor rotor A-21 through the air inlet passage at one end or two ends of the motor rotor A-21, the motor rotor A-21 is cooled, and then is thrown out into the motor accommodating cavity A-14 from the vent hole on the motor rotor A-21 under the action of high-speed rotation of the motor rotor A-21, so that the heat in the motor rotor A-21 is taken away, the heat is mixed with the fluid entering the left end of the motor accommodating cavity A-14 through the spiral cooling flow passage, and the mixed fluid flows to the right end of the motor accommodating cavity through the matching gap A-311 between the backflow through hole and the rotor mounting hole A-31 and the motor rotor A-21, and then flows out of the compressor through the cooling fluid outlet A-113.

In the compressor of the present disclosure, the rotor may be supported on the housing by various types of bearings, such as a slide bearing, a rolling bearing, a hydraulic bearing, a magnetic suspension bearing, and the like.

In some embodiments, the compressor includes a gas bearing by which the compressor rotor A-20 is rotatably supported on the housing A-10. The gas bearing may be, for example, a dynamic pressure gas bearing or a static pressure gas bearing. The gas bearing can use the same gas as the working medium gas compressed by the compressor as suspension gas, so that the setting position of the vent hole of the motor rotor does not need to avoid the mounting position of the gas bearing.

Because the motor rotor is provided with the hollow part, the weight of the motor rotor is reduced, and the motor rotor is more suitable for gas bearing application.

As shown in FIG. 1, in some embodiments, the aforementioned first radial bearing A-60, second radial bearing A-90, first thrust bearing, and second thrust bearing are dynamic pressure gas bearings.

The operation and principle of the motor cooling fluid circulation will be described below with reference to fig. 1 to 6 by taking a refrigeration compressor used as a refrigerant circulation system as an example of the compressor of each of the above embodiments.

The refrigerant serving as cooling fluid enters the spiral cooling flow passage through the cooling fluid inlet A-111, the cooling fluid spirally flows between the motor cylinder A-11 and the motor stator A-30, and the cooling fluid flowing in the spiral flow passage continuously absorbs heat to reduce the temperature of the surface of the motor stator A-30. The refrigerant which is leaked from the two end parts of the motor rotor A-21 and serves as cooling fluid enters the hollow part of the motor rotor A-21, absorbs heat in the motor rotor A-21, and is thrown out from the vent holes of the motor rotor A-21 under the action of high-speed rotation to cool the interior of the motor rotor A-21. After the refrigerant gathers at the left end of the motor accommodating cavity A-14, a part of refrigerant flows to the right end of the motor accommodating cavity A-14 through a fit clearance A-311 between the motor stator A-30 and the motor rotor A-21, and absorbs heat of the outer surface of the motor rotor A-21. Meanwhile, as the upper part of the motor stator A-30 is provided with the air return hole A-32, the lower part is provided with the liquid return hole A-33, the gaseous refrigerant at the left end of the motor accommodating cavity A-14 can flow to the right end of the motor accommodating cavity A-14 through the air return hole A-32, and the liquid refrigerant at the left end of the motor accommodating cavity A-14 can flow to the right end of the motor accommodating cavity A-14 through the liquid return hole A-33, so that the heat in the motor stator A-30 is taken away, and the motor is cooled more fully.

When each radial bearing and each thrust bearing are gas bearings, the gas bearings are positioned in the motor accommodating cavity A-14, so that the refrigerant in the motor accommodating cavity A-14 can directly supply gas for the gas bearings and cool the gas bearings. Therefore, the compressor of the embodiment is beneficial to solving the internal cooling problem of the motor rotor A-21, can supply air for the air bearing of the compressor, omits an external air supply device and further improves the working stability and reliability of the compressor.

The compressor disclosed by the embodiment of the disclosure can cool the motor rotor uniformly, eliminates the phenomenon of local temperature deviation caused by concentrated heat, and is beneficial to ensuring safe and reliable operation of the compressor.

In the above-described embodiments, the structures of the compressor rotor and the motor rotor in the motor drive system are shown in conjunction with fig. 1 to 3 and 6, and the assembly structures of the gas bearing, the diffuser, the bearing mount, and the like are also shown by fig. 1. Other possible variations of the compressor rotor and motor rotor, motor drive system, gas bearing, diffuser and bearing support structures, and the assembly structures with respect to each other will be described in several embodiments. It should be noted that the specific features of the present disclosure described in these embodiments may be combined in any suitable manner without contradiction. In order to avoid unnecessary repetition, various possible combinations of embodiments of the present utility model are not described in detail.

Rotor structural modification example 1

Referring to fig. 7-9, in some embodiments, a compressor rotor is provided that includes a motor rotor B-10, a lock lever B-20, a compression unit rotating part, and a locking member.

As shown in fig. 7, the motor rotor B-10 includes a plurality of rotor segments fixedly connected in an axial direction, the plurality of rotor segments having axial through holes B-15. The locking rod B-20 penetrates through the axial through hole B-15. The compression unit rotating part is positioned at the end of the motor rotor B-10 and is connected to the locking lever B-20. The locking member locks the compression unit rotating portion to the locking lever B-20. The lock lever, the compression unit rotating portion, and the locking member form a pressing structure that applies pressure toward the axially inner side to the motor rotor B-10.

In the compressor rotor disclosed by the disclosure, the motor rotor B-10 comprises a plurality of rotor sections fixedly connected along the axial direction, the locking rod B-20 is arranged in the motor rotor B-10 in a penetrating manner, the locking rod, the compression unit rotating part and the locking part form a compression structure for applying pressure towards the axial inner side to the motor rotor B-10, and the motor rotor B-10 can be processed in a segmented manner, and meanwhile, the connection between the rotor sections of the motor rotor B-10 with the plurality of rotor sections is more reliable and firm.

As shown in fig. 7, in some embodiments, the compressor may be a centrifugal compressor and the compression unit rotating portion is a centrifugal impeller of the centrifugal compressor. The compression unit rotating part may be provided only at one side of the motor rotor, or may be provided at both sides of the motor rotor, respectively. The compression unit rotating parts on each side can be single-stage or multi-stage. For example, when the compression unit rotation portion is an impeller, the number of impellers on the motor rotor side may be one or two or more.

In some embodiments, the two ends of the locking lever B-20 are respectively connected with the compression unit rotating parts.

In some embodiments, the end of the locking bar B-20 is provided with external threads and the locking member comprises a locking nut that mates with the external threads of the locking bar B-20.

As shown in FIG. 7, in some embodiments, the compressor rotor includes a motor rotor B-10, a primary centrifugal impeller B-30, and a secondary centrifugal impeller B-50. External threads are respectively arranged at the left end and the right end of the locking rod B-20. The primary centrifugal impeller B-30 is locked to the left end of the locking lever B-20 by a first locking nut B-40 as a locking member. The secondary centrifugal impeller B-50 is locked to the right end of the locking lever B-20 by a second locking nut B-60 as a locking member.

As shown in FIGS. 7 and 8, in some embodiments, the axial through bore B-15 includes a small diameter section B-151 and a large diameter section having a diameter greater than the small diameter section B-151.

The axial through hole B-15 comprises a small-diameter section B-151 and a large-diameter section with the diameter larger than that of the small-diameter section B-151, and the motor rotor can be made into a hollow structure as much as possible according to the properties of each rotor section of the motor rotor B-10, so that the integral weight of the motor rotor B-10 and the compressor rotor is reduced, and the critical rotating speed of the compressor rotor is improved.

In some embodiments, the lock lever B-20 includes a lever body B-21 and a projection. The rod body B-21 is matched with the small diameter section B-151 of the axial through hole B-15. The protruding part is arranged on the rod body B-21, protrudes outwards from the rod body B-21 in the radial direction, and is matched with the large-diameter section of the axial through hole B-15.

The whole rigidity of the locking rod B-20 can be improved on the basis of not excessively increasing the whole weight of the compressor rotor by arranging the convex part, thereby being beneficial to the dynamic balance of the compressor rotor.

In some embodiments, the protrusion is a convex ring. The convex ring can provide support for each position of the rod body B-21 in the circumferential direction, which is beneficial to dynamic balance of the compressor rotor.

In some embodiments, the axial middle part of the motor rotor B-10 comprises a permanent magnet B-11, the small-diameter section B-151 is positioned at the axial middle part of the axial through hole B-15, and the two large-diameter sections are respectively positioned at two ends of the axial through hole B-15. As shown in fig. 7 and 8, the two large diameter sections are a first large diameter section B-152 located at the left end of the motor rotor and a second large diameter section B-153 located at the right end of the motor rotor B-10, respectively.

For a motor rotor B-10 having a plurality of rotor segments, the axial middle portion is generally the arrangement position of the permanent magnets, and the arrangement of the small-diameter segments at this portion can reduce the influence of the arrangement of the axial through holes on the permanent magnets. The two axial ends of the motor rotor B-10 are non-magnetic bodies, and the large-diameter section is arranged at the position, so that the overall weight of the motor rotor and the compressor rotor is reduced, and the critical rotation speed of the compressor rotor is improved.

As shown in fig. 7, the lock lever B-20 includes two projections which are respectively engaged with the two large diameter sections. The arrangement is beneficial to improving the overall rigidity of the locking rod B-20, thereby being beneficial to dynamic balance of the compressor rotor.

As shown in fig. 7, one of the two protrusions is a fixed protrusion B-22 fixed to the rod body B-21, and the other is a movable protrusion B-23 movable with respect to the rod body B-21. The fixed protruding part B-22 and the movable protruding part B-23 are respectively arranged, so that the locking rod B-20 and the motor rotor B-10 can be assembled conveniently.

In the embodiment shown in FIG. 7, the fixed projection B-22 is engaged with the first large diameter section B-152 and the movable projection B-23 is engaged with the second large diameter section B-153.

In some embodiments, not shown, both projections may be movable projections movable relative to the rod body.

In some embodiments, the movable protrusion B-23 is keyed to the inner wall of the axial through-hole B-15 to limit the circumferential position of the movable protrusion B-23 relative to the axial through-hole B-15.

As shown in fig. 7 to 9, a key groove B-1531 is provided in the hole wall of the second large diameter section B-153, and a key B-232 is provided on the outer periphery of the movable protrusion B-23. When the center hole B-231 of the movable protrusion B-23 is fitted between the rod body B-21, which has been inserted into the axial through hole B-15 of the motor rotor B-10, and the inner wall of the second large-diameter boss B-153, the key B-232 is engaged with the key groove B-1531, and the circumferential position of the movable protrusion B-23 is defined.

In the form of square keys shown in fig. 7 to 9, in the embodiment not shown, the keys may be fixed to the motor rotor and provided with grooves on the movable protrusions, or the keys may be independent and provided with key grooves on the motor rotor B-10 and the movable protrusions, respectively. The key form is not limited to square keys, but may be round keys, half keys, splines, or the like.

In some embodiments, as shown in FIG. 7, a shoulder is provided on the rod body B-21, and the movable protrusion B-23 is located between the end face of one end of the motor rotor B-10 and the shoulder. For example, the movable projection B-23 may abut against a shoulder. This arrangement is advantageous in defining the axial position of the movable protrusion B-23 and in ensuring the rigidity of the lock lever B-20 to be stable.

In some embodiments, the compression unit rotating part of one end of the motor rotor B-10 where the movable protruding part B-23 is located comprises an axial boss extending into the axial through hole B-15, and the movable protruding part B-23 is axially limited between the shaft shoulder and the end face of the axial boss.

As shown in fig. 7, the left end of the second centrifugal impeller B-50 has an axial boss, the outer circumference of which is matched with the inner wall of the right end of the second large-diameter section B-153, and the left end surface of the axial boss and the shaft shoulder on the rod body B-21 can limit the axial position of the movable protruding part B-23 within a certain range. When the distance between the left end face of the axial boss and the shaft shoulder is set to be equal to or slightly larger than the distance between the two axial ends of the movable protruding part B-23, the axial position of the movable protruding part B-23 is basically determined, so that the stability of the rigidity of the locking rod B-20 is guaranteed, and the dynamic balance of the compressor rotor is guaranteed.

In some embodiments, the fit clearance of the fixed projection B-22 with the corresponding large diameter section is less than the fit clearance of the rod body B-21 with the small diameter section B-151. This arrangement facilitates quick assembly of the compressor rotor.

In some embodiments, the movable protrusion B-23 is in interference fit with the corresponding large diameter section, and the movable protrusion B-23 is in clearance fit with the rod body B-21. This arrangement facilitates quick assembly of the compressor rotor.

As shown in FIG. 7, in some embodiments, a plurality of rotor segments of motor rotor B-10 include permanent magnets B-11, a first end shaft segment B-12, and a second end shaft segment B-13. The first end shaft section B-12 is fixedly arranged at one end of the permanent magnet B-11. The second end shaft section B-13 is fixedly arranged at the other end of the permanent magnet B-11.

The permanent magnet B-11 may be a hollow cylinder with an axial through hole. The permanent magnet B-11 is used as a motor rotor B-10 to form a motor for driving the compressor rotor to rotate together with a motor stator of the compressor. The material of the permanent magnet B-11 is, for example, magnetic steel.

As shown in FIG. 7, in some embodiments, the motor rotor B-10 further includes a mounting sleeve B-14 integrally disposed at an end of the first end shaft section B-12 proximate the permanent magnet B-11. The permanent magnet B-11 and the second end shaft section B-13 are fixedly arranged in the mounting sleeve B-14 in a hot sleeve mode.

Some embodiments of the present disclosure are described in more detail below in conjunction with fig. 7-9.

As shown in fig. 7 to 9, the motor rotor B-10 of the compressor rotor of the embodiment of the present disclosure includes three rotor segments of permanent magnets B-11, first and second end shaft segments B-12 and B-13, and one mounting sleeve B-14. The left end of the mounting sleeve B-14 is integrally provided with the right end of the first end shaft section B-12. The first end shaft section B-12, the second end shaft section B-13 and the permanent magnet B-11 are all processed into a hollow structure with axial through holes. The second end shaft section B-13 is similar to the first end shaft section B-12 in structure but symmetrically arranged, and the left end of the second end shaft section B-13 is in a step form, so that the outer peripheral diameter of the motor rotor B-10 is equal after the three rotor sections are connected.

Each rotor segment is separately processed and guaranteed to be reasonably accurate, and then assembled to form the motor rotor B-10. In the process of assembling the motor rotor B-10, the permanent magnet B-11 and the second end shaft section B-13 are first adhesively fixed together. The first end shaft section B-12 and the mounting sleeve B-14 are then heated to a higher temperature, e.g., 700-900 ℃, and the permanent magnet B-11 and the second end shaft section B-13 are then quickly nested into the mounting sleeve B-14. The method can shorten the time of hot sleeve type interference connection and improve the assembly success rate. Because the motor rotor B-10 is acted by centrifugal force in the high-speed rotation process, the material expansion phenomenon exists, and the interference is preferably larger in order to prevent the loosening of parts after the interference is reduced.

Because the three rotor sections are hollow structures, the gas generated in the hot jacket process can be discharged from the axial through hole B-15, no additional exhaust holes are needed, the processing is convenient, and the production efficiency of the motor rotor B-10 is improved.

The diameter of the axial through hole inside the permanent magnet B-11 is approximately the same as the diameter of the corresponding rod segment of the rod body B-21 of the locking rod B-20. Considering the property of the permanent magnet material, the diameter of the axial through hole inside the permanent magnet B-11 is preferably 1/4 to 1/3 times of the outer diameter of the permanent magnet. As shown in FIG. 7, the axial through-hole inside the permanent magnet B-11 constitutes a part of the hole section of the small-diameter section B-151 of the axial through-hole B-15 of the motor rotor B-10.

The axial through holes in the permanent magnet B-11 are in clearance fit with the corresponding rod sections of the rod body B-21, and the fit clearance can be 0.03-0.05 mm, for example. The roughness of the surface of the axial through hole of the permanent magnet B-11, which is in contact with the rod body B-21, can be 0.8-1.6 mu m, and the roughness range is favorable for preventing the surface peak value from affecting the assembly.

Because the wall thickness of the mounting sleeve is relatively thin, a certain degree of strength problem exists after interference connection, and the connection reliability can be improved by using the locking rod B-20 in the radial middle of the motor rotor B-20.

Considering that the length of the locking bar B-20 is relatively long, the rigidity and strength thereof are affected, the fixing projection B-22 in the form of a supporting and positioning step is formed at the left end thereof to increase the rigidity so as to reduce the deflection of the locking bar B-20. The fixing projection B-22 is clearance fitted with the first large diameter section B-152. The fit clearance of the fixing projection B-22 with the first large diameter section B-152 may be smaller than the fit clearance of the permanent magnet B-11 with the corresponding rod section B-21 of the lock rod B-20. The fit clearance between the fixing protrusion B-22 and the first large diameter section B-152 may be, for example, 0.01-0.03 mm.

The right end of the locking rod B-20 is radially positioned by adopting a movable protruding part B-23. The central bore B-231 of the movable projection B-23 is in clearance fit with the corresponding segment B-21 of the locking lever B-20. The movable protruding part B-23 is in interference fit with the inner wall of the second large-diameter section B-153 arranged in the second end shaft section B-13 by small interference so as to radially position the right end of the locking rod B-20.

As shown in FIGS. 8 and 9, the circumferential positioning of the movable protrusion B-23 is achieved by the cooperation of the key B-232 fixedly provided on the movable protrusion B-23 and the key groove B-1531 provided on the inner wall of the second large diameter section B-153.

The second large-diameter section B-153 is in interference fit with the movable protruding portion B-23, the diameter of the second large-diameter section B-153 is in negative deviation, the outer diameter of the movable protruding portion B-23 is in positive deviation, and the total interference can be 0.01-0.02 mm.

In the assembly process of the motor rotor B-10, the locking rod B-20 and the centrifugal impeller, the movable protruding part B-23 and the motor rotor B-10 are assembled in a cold mode, the movable protruding part B-23 is firstly assembled leftwards along the direction of the key slot B-1531, then the rod body B-21 of the locking rod B-20 is inserted into the axial through hole B-15 of the motor rotor B-10 at the left end of the motor rotor B-10, then the first-stage centrifugal impeller B-30 and the second-stage centrifugal impeller B-50 are respectively assembled at the left end and the right end of the rod body B-21, and then the first-stage centrifugal impeller B-30 and the second-stage centrifugal impeller B-50 are respectively pressed against the left end and the right end of the motor rotor B-10 through the first locking nut B-40 and the second locking nut B-60 in a reverse screwing mode. After the assembly, the locking rod B-20, the primary centrifugal impeller B-30, the secondary centrifugal impeller B-50, the first locking nut B-40 and the second locking nut B-60 form a compression structure, and pressure towards the inner side in the axial direction is applied to the motor rotor B-10, so that the connecting columns among the rotor sections of the motor rotor B-10 are firm and stable.

The two end shaft sections are respectively arranged at the two axial ends of the permanent magnet B-11, and the two axial end surfaces of the motor rotor are respectively provided with the one-stage centrifugal impeller, so that the problem of overlong motor rotor caused by the fact that the two-stage centrifugal impellers of the two-stage centrifugal compressor are arranged at the same end of the motor rotor can be effectively avoided.

As shown in fig. 7, the two centrifugal impellers are positioned at the hollow parts of the end parts of the first end shaft section B-12 and the end part of the second end shaft section B-13, namely at the two axial ends of the axial through hole B-15, and the radial and axial positioning of the centrifugal impellers relative to the motor rotor B-10 is performed by means of positioning rabbets on the back surfaces of the centrifugal impellers.

The right section of the rod body of the locking rod B-20 is provided with a shaft shoulder, and the movable protruding part B-23 is positioned between the shaft shoulder and the axial boss end face of the positioning spigot of the secondary centrifugal impeller B-50. The axial boss of the locating spigot of the secondary centrifugal impeller B-50 is in clearance fit with the movable protruding part B-23, and the fit clearance is 0.01-0.02 mm, for example. The arrangement can effectively prevent the movable protruding part B-23 from moving axially in the second large-diameter section B-153, and is beneficial to preventing the secondary centrifugal impeller B-50 from being over-positioned axially in the assembly process.

When the axial boss of the locating spigot of the secondary centrifugal impeller B-50 is matched with the clearance distance of the movable protruding part B-23 in a small clearance way, the axial locating of the locking rod B-20 can be realized through the shaft shoulder.

According to the description, the compressor rotor of the embodiment of the disclosure can effectively improve the connection strength of the rotor sections of the motor rotor with a plurality of rotor sections, can further improve the working stability and reliability of the compressor and the motor thereof where the compressor rotor is located by reducing the length of the cantilever end and improving the critical rotation speed of the rotor, can realize high rotation speed work, can also make the structure of the compressor simpler, and has simpler system and smaller size.

Based on the above description of the rotor structure modification, the embodiments of the present disclosure also provide a compressor, including the compressor rotor of the foregoing embodiments of the present disclosure. The compressor of the embodiments of the present disclosure has the same advantages as the compressor rotor of the embodiments of the present disclosure. Further, in some embodiments, the compressor may include a gas bearing on which the compressor rotor is supported. The gas bearings may include radial bearings and thrust bearings. The gas bearing may be a dynamic pressure gas bearing or a static pressure gas bearing. The compressor rotor of the embodiment of the disclosure has higher working stability and reliability, and is suitable for being supported by adopting a gas bearing. The compressed working medium can be used as suspension gas by adopting the gas bearing, so that a lubricating oil system and an oil separation system which are required when a rolling bearing or an oil film bearing is adopted are omitted, and the complexity and the occupied space of a fluid system, such as a refrigerant circulation system, where the compressor is positioned can be reduced.

Rotor structural modification II

Referring to fig. 10, in some embodiments, there is provided a compressor rotor including an impeller C-1, a rotor shaft C-2, and a connection rod C-3, the impeller C-1 being provided with a first connection hole C-11, the rotor shaft C-2 being provided with a second connection hole C-21, one end of the connection rod C-3 being inserted into the first connection hole C-11 and the connection rod C-3 being detachably connected with the impeller C-1, the other end of the connection rod C-3 being inserted into the second connection hole C-21, and the connection rod C-3 being detachably connected with the rotor shaft C-2.

In the above embodiment, the compressor rotor includes the connecting rod C-3, one end of the connecting rod C-3 is inserted into the first connecting hole C-11 and detachably connected with the impeller C-1, and the other end of the connecting rod C-3 is inserted into the second connecting hole C-21 and detachably connected with the rotor shaft C-2, so that the impeller C-1 and the rotor shaft C-2 are more convenient to mount and dismount, the problem of difficult dismounting in the prior art due to the adoption of the shrink fit mode is solved, meanwhile, heating equipment is not needed, the process and equipment for assembling the impeller are simplified, the assembly efficiency is effectively improved, and the operability of later maintenance is improved.

Further, as shown in FIG. 11, the circumferential side of the connecting rod C-3 is provided with a boss C-31 extending in the radial direction, and the boss C-31 is used for supporting the connecting rod C-3. The boss C-31 can support the connecting rod C-3, effectively prevent the connecting rod cantilever from being too long to cause deflection to be large, prevent the connecting rod C-3 from deforming when the rotor shaft rotates at a high speed, effectively increase the strength of the connecting rod and prolong the service life of the connecting rod. The boss C-31 is also beneficial to ensuring concentricity of the connecting rod C-3 with the impeller C-1 and the rotor shaft C-2.

The bosses C-31 may be arranged at intervals or may be arranged continuously in the circumferential direction, thereby forming a convex ring.

The number of the bosses C-31 can be flexibly set according to the requirement, for example, the number of the bosses C-31 is one, the bosses C-31 are arranged at the middle section of the connecting rod C-3, the number of the bosses C-31 can also be multiple, and the bosses C-31 can be arranged at the same axial position of the connecting rod C-3 and are arranged at intervals along the radial direction, and can also be respectively arranged at different axial positions of the connecting rod C-3 so as to realize better support.

In contrast, the axial length of the rotor shaft C-2 is longer than that of the impeller C-1, so that the length of the second connecting hole C-21 is longer than that of the first connecting hole C-11, and the boss C-31 can be arranged in the second connecting hole C-21 and is in clearance fit with the inner wall surface of the second connecting hole C-21 to support the connecting rod C-3, which is beneficial to realizing a relatively balanced supporting effect.

The boss C-31 and the second connecting hole C-21 are in clearance fit, the fit clearance is 0.03 mm-0.05 mm, and the axial length of the boss C-31 is optionally larger than 10mm for ensuring effective support.

Optionally, the second connecting hole C-21 is a blind hole. The provision of the second connecting hole C-21 as a blind hole has the advantage of facilitating the connection of the connecting rod C-3 with the rotor shaft C-2 and ensuring sufficient strength of the rotor shaft C-2.

The connection mode of the connecting rod C-3 and the rotor shaft C-2 can be selected in various ways. Optionally, an inner thread is arranged at one end of the second connecting hole C-21 far away from the impeller C-1, an outer thread is arranged at one end of the connecting rod C-3 far away from the impeller C-1, and the connecting rod C-3 is connected with the rotor shaft C-2 through threads. The threaded connection mode is convenient to install and detach, compared with the key connection mode, the stress concentration problem can be relieved, and the strength of the connecting rod C-3 is effectively improved. In order to ensure the connection reliability, the connecting rod C-3 and the rotor shaft C-2 can be bonded and fixed through the fixing glue after being screwed through threads.

Specifically, the second connecting hole C-21 comprises a first hole section, a second hole section and a third hole section, wherein the first hole section is close to the impeller C-1, the second hole section is arranged on one side of the first hole section far away from the impeller C-1, the diameter of the second hole section is smaller than that of the first hole section, the third hole section is arranged on one side of the second hole section far away from the impeller C-1, the diameter of the third hole section is smaller than that of the second hole section, and the inner wall of the third hole section is provided with internal threads.

Wherein, the one end that keeps away from impeller C-1 of first hole section is equipped with the chamfer, and the setting of this chamfer can make things convenient for the seting up of first hole section, reduces the processing degree of difficulty.

Accordingly, as shown in FIG. 11, the connecting rod C-3 includes a first rod segment C-32, a second rod segment C-33 and a third rod segment C-34, the first rod segment C-32 is disposed within the first bore segment, and an end surface of the first rod segment C-32 remote from the impeller C-1 is in abutting contact with an end surface of the first bore segment to axially position the connecting rod C-3. The end face of the first rod section C-32 far away from the impeller C-1 and the end face of the first hole section are high in machining precision, for example, the roughness Ra of the two end faces is smaller than or equal to 3.2um, and the coaxiality of the two end faces relative to the center line of the rotor shaft C-2 is smaller than or equal to 0.05mm, so that accurate positioning is achieved.

The diameter of the second rod section C-33 is smaller than that of the first rod section C-32, the second rod section C-33 is arranged in the second hole section, the length of the second rod section C-33 along the axial direction is smaller than or equal to that of the second hole section, and the second rod section C-33 is used for radially positioning the connecting rod C-3. And the second rod section C-33 is in clearance fit with the second hole section, and the clearance is controlled to be 0.01 mm-0.03 mm. The length of the second pole segment C-33 is optionally greater than or equal to 10mm for better radial positioning.

The diameter of the third rod section C-34 is smaller than that of the second rod section C-33, the third rod section C-34 is arranged in the third hole section, and the periphery of the third rod section C-34 is provided with external threads which are matched and locked with the internal threads in the third hole section.

As shown in fig. 10, the first connection hole C-11 is a through hole. The advantage of setting up like this is, can conveniently realize connecting rod C-3 and impeller C-1's connection, shifts the connection position from impeller C-1 and rotor shaft C-2's less space to impeller C-1's one side that keeps away from rotor shaft C-2, and operable space is great, is convenient for realize more reliable connection.

As shown in FIG. 12, the side of the first rod segment C-32 of the connecting rod C-3, which is far from the second rod segment C-33, is provided with a force application segment C-35, and the side of the force application segment C-35, which is far from the first rod segment C-32, is provided with a fourth rod segment C-36.

The section of the force application section C-35 is hexagonal in shape so as to be convenient for being matched with a screwing tool. The diameter of the force application section C-35 is smaller than that of the first rod section C-32, and the diameter of the fourth rod section C-36 is smaller than that of the force application section C-35.

In order to match the diameter change of the force application section C-35 and the fourth rod section C-36 on the connecting rod C-3, the first connecting hole C-11 is also a stepped hole, and the diameter of the hole section close to the rotor shaft C-2 is larger than that of the hole section far away from the rotor shaft C-2. The portion of the first rod section C-32 and the force application section C-35 of the connecting rod C-3 are located in the larger diameter bore section of the first connecting bore C-11. The fourth shank segment C-36 mates with the smaller diameter bore segment of the first connecting bore C-11.

The specific connection mode of the connecting rod C-3 and the impeller C-1 can be selected in various ways. For easy operation and assembly and disassembly, the compressor rotor further comprises a connecting piece for connecting the connecting rod C-3 and the impeller C-1.

Optionally, the connector is a lock nut C-4. Through setting up lock nut C-4, adopt threaded connection mode to realize connecting rod C-3 and impeller C-1's connection, not only install and dismantle all more convenient, compare in key connection mode in addition, can alleviate stress concentration problem, effectively improve connecting rod C-3's intensity.

As shown in FIG. 12, the lock nut C-4 is provided with a connecting hole including a first connecting hole section C-41 and a second connecting hole section C-42, the first connecting hole section C-41 having a larger diameter than the second connecting hole section C-42, and the first connecting hole section C-41 being closer to the impeller C-1 than the second connecting hole section C-42. The structure of the lock nut C-4 can enable the lock nut C-4 to penetrate into the connecting rod C-3 more smoothly, the first connecting hole section C-41 with larger diameter has a guiding function, moreover, the connecting rod C-3 is in threaded fit with the second connecting hole section C-42, the first connecting hole section C-41 is arranged to be a light section, the end face of the lock nut C-4 can be contacted with the end face of the impeller C-1 to tightly prop up, interference with the root of the tail end of the external thread on the connecting rod C-3 is effectively avoided, or the impeller C-1 cannot be tightly propped up, and connection reliability is guaranteed.

The periphery of the fourth rod section C-36 is provided with external threads, the inner wall of the second connecting hole section C-42 of the locking nut C-4 is provided with internal threads, the fourth rod section C-36 and the locking nut C-4 are locked through threaded fit, and the locking nut C-4 is tightly propped against the end face of the impeller C-1, so that the locking of the connecting rod C-3 and the impeller C-1 is realized.

The external threads on the fourth leg C-36 and the external threads on the third leg C-34 may be the same or different in gauge. The external thread on the fourth rod section C-36 and the external thread on the third rod section C-34 have the same rotation direction as the rotor shaft C-2, so that the loosening of the threads in the rotation process is effectively prevented.

Optionally, an insertion portion C-12 is provided at an end of the impeller C-1 adjacent to the rotor shaft C-2, and the insertion portion C-12 is inserted into the second connection hole C-21. By arranging the insertion part C-12, the impeller C-1 and the rotor shaft C-2 can be positioned in advance, and further connection is facilitated.

The machining precision of the outer peripheral surface of the insertion part C-12 is higher than that of the non-insertion part, and the part of the inner wall surface of the second connecting hole C-21 matched with the insertion part C-12 is higher than that of other parts of the inner wall surface, so that the accurate positioning is realized.

The insertion part C-12 is in clearance fit with the second connecting hole C-21, and the clearance can ensure smooth insertion, and meanwhile, the impeller C-1 cannot jump too much in the rotating process of the rotor shaft C-2.

Optionally, one end of the impeller C-1, which is close to the rotor shaft C-2, is provided with a first matching end face, and one end of the rotor shaft C-2, which is close to the impeller C-1, is provided with a second matching end face, wherein the first matching end face is in tight contact with the second matching end face.

The first mating end surface may be a boss protruding toward the rotor shaft C-2 with respect to an end surface of the impeller C-1 near the rotor shaft C-2, and a radial dimension of the boss is smaller than a radial dimension of the end surface of the impeller C-1. By arranging the boss, only the end face of the boss can be finished, the whole end face of the impeller C-1 does not need to be finished, the processing cost is saved, meanwhile, the boss is convenient to process, and the processing difficulty is reduced.

Similarly, the second mating end surface may be a segment of a boss protruding in a direction toward the impeller C-1 with respect to an end surface of the rotor shaft C-2 near the impeller C-1, the radial dimension of the boss being smaller than the radial dimension of the end surface of the rotor shaft C-2. By arranging the boss, only the end face of the boss can be finished, the whole end face of the rotor shaft C-2 does not need to be finished, the processing cost is saved, meanwhile, the boss is convenient to process, and the processing difficulty is reduced.

As shown in fig. 13, the compressor rotor includes two rotor shafts C-2, and magnetic steel is disposed between the two rotor shafts C-2. Wherein, the right section of the left rotor shaft C-2 is provided with a containing groove, the magnetic steel is arranged in the containing groove, and the right rotor shaft C-2 is also at least partially positioned in the containing groove, so that the connection between the two sections of rotor shafts C-2 and the middle magnetic steel is realized through the groove wall of the containing groove. The diameter of the left section of the rotor shaft C-2 on the right side is smaller than that of the right section thereof so as to be limited by a step formed at the diameter change when the left section is inserted into the receiving groove.

Correspondingly, the compressor rotor comprises two impellers C-1, the left rotor shaft C-2 and one of the impellers C-1 can be connected in the connecting mode in the embodiment, and the right rotor shaft C-2 and the other impeller C-1 can also be connected in the connecting mode in the embodiment.

By way of illustration of the various compressor rotor embodiments corresponding to the present rotor structural variations, one or more of the following advantages may be appreciated:

1. The rotor shaft is connected with the impeller through the connecting rod, so that the installation and the disassembly are relatively convenient, the problem that the hot sleeve matching mode is difficult to disassemble is solved, meanwhile, heating equipment is not needed, the process and the equipment for assembling the impeller are simplified, the assembly efficiency is effectively improved, and the later maintenance is convenient;

2. the connecting rod is provided with a boss for supporting the connecting rod, so that the strength of the connecting rod is improved;

3. The connecting rod is in threaded connection with the impeller and the rotor shaft, so that the problem of stress concentration is relieved compared with a key connection mode;

4. the connecting rod is a stepped shaft, so that the connecting rod is effectively positioned, and the assembly efficiency is improved;

5. the stepped hole is formed in the lock nut, so that the lock nut is effectively guaranteed to be in tight contact with the end face of the impeller in a propping mode, and a good locking effect is achieved.

Based on the above description of the rotor structure modification, the embodiments of the present disclosure also provide a compressor, including the compressor rotor of the foregoing embodiments of the present disclosure. The compressor of the embodiments of the present disclosure has the same advantages as the compressor rotor of the embodiments of the present disclosure. In some embodiments, the compressor further comprises a gas bearing on which the compressor rotor is supported. The compressor can be a centrifugal compressor, and the connection reliability of the impeller and the rotor shaft is high, so that the refrigerating capacity of the compressor is improved.

Rotor structural modification III

Referring to fig. 14-16, in some embodiments, a compressor rotor is provided that includes a main shaft, an impeller D-14, and a locking member. The end part of the main shaft is provided with a cavity D-111 so as to form a shaft core D-112 at the center of the main shaft, the end part of the shaft core D-112 extends out of the end part of the main shaft so as to be provided with an impeller D-14, the shaft core D-112 serves as a supporting part of the impeller D-14, the impeller D-14 is sleeved at the outer end of the shaft core D-112 and is axially positioned through the end part of an outer ring of the main shaft, and a locking part is used for locking the impeller D-14 on the shaft core D-112. The impeller D-14 may be mounted at only one end of the main shaft or at both ends.

The compressor rotor has at least one of the following advantages:

(1) The impeller and the main shaft are fixed through the locking part, so that the impeller is detachably arranged relative to the main shaft, the difficulty in disassembling and assembling the impeller can be reduced, the assembly process and required equipment of the impeller are simplified, and the assembly efficiency and the operability of disassembling and inspection work and maintenance are improved.

(2) Compared with a hot sleeve or key groove connection mode, the installation mode can prevent the main shaft or the impeller from deforming, can also ensure the installation strength of the impeller, and avoids stress concentration, thereby improving the compression capacity of the compressor.

(3) The axle core is through directly forming when processing the cavity, makes axle core and the other parts processing of main shaft form an organic whole, need not to additionally install the axle core in the cavity of main shaft, can further reduce the assembly degree of difficulty, increases the joint strength of axle core and main shaft, still can guarantee the position accuracy of axle core, effectively solves the problem of beating of rotor front end, reduces cantilever end length to improve compressor's job stabilization nature and reliability.

(4) By arranging the cavity on the main shaft, the weight of the rotor can be reduced, the critical rotation speed of the rotor can be improved, and the limit working capacity of the compressor can be further improved.

In some embodiments, the cavity D-111 is centrally symmetric with respect to the axis of the spindle. When the rotor works, the weight of the main shaft is uniformly distributed, and unbalanced force applied to the rotor in the high-speed rotation process can be reduced.

For example, the cavity D-111 can be a ring groove concentric with the main shaft, and the ring groove is arranged along the whole circumference of the main shaft, so that the ring groove has a better weight reduction effect, is easy to form a shaft core D-112 after processing, and is beneficial to mounting and positioning the impeller D-14. Or the cavity D-111 comprises a plurality of discrete holes, each hole is symmetrical relative to the center of the axis of the main shaft, and the holes can be round holes, linear or arc oblong holes and the like.

As shown in FIG. 15, the inner end of the impeller D-14 is provided with a positioning part D-141, the positioning part D-141 extends into the cavity D-111, the outer side wall of the positioning part D-141 is matched with the inner side wall of the cavity D-111 so as to radially position the impeller D-14, and a gap is reserved between the inner side wall of the positioning part D-141 and the inner side wall of the cavity D-111. In order to better solve the radial runout of the impeller D-14 at the front end, the length of the embedded positioning part D-141 in the cavity D-111 can reach a preset length, for example, more than 20 mm.

The radial positioning of the impeller D-14 is convenient to ensure the radial installation accuracy of the impeller D-14 in the assembly process, the inner side wall of the positioning part D-141 and the inner side wall of the cavity D-111 are provided with gaps, the over-positioning of the impeller D-14 can be avoided, in addition, the installation mode that the inner end of the impeller D-14 extends into the main shaft can improve the integral strength of the rotor of the compressor, the deflection deformation of the end part of the rotor can be reduced, and the rotation stability of the rotor is improved.

In order to reduce the front-end deflection caused by the overlong shaft core D-112, the radial width of the cavity D-111 is the same as the radial thickness of the impeller positioning part D-141, and the precision is precisely controlled, for example, a gap of 0.01-0.02mm can be ensured. The positioning of the shaft core D-112, the impeller D-14 and the main shaft in the structure is mutually limited, so that the integral rigidity of the structure can be improved.

For the embodiment in which the cavity D-111 is a ring groove, the positioning portion D-141 is a positioning ring, the positioning ring extends into the ring groove, and an outer sidewall of the positioning portion D-141 is matched with an inner sidewall of the ring groove to radially position the impeller D-14, and a gap is formed between the inner sidewall of the positioning portion D-141 and the inner sidewall of the ring groove (i.e., an outer sidewall of the shaft core).

As shown in FIG. 15, the outer end of the shaft core D-112 is a threaded section, and the locking component comprises a locking nut D-16, and the locking nut D-16 is screwed on the outer end of the shaft core D-112 to lock the impeller D-14. The locking nut D-16 is easy to disassemble, and the locking reliability can be ensured. Alternatively, the locking component may be locked by a buckle or the like.

Further, the outer end of the shaft core D-112 exceeds the outer end of the locking nut D-16, so that the locking nut D-16 is prevented from being withdrawn outwards after long-term use, and the locking reliability of the impeller D-14 during high-speed rotation is ensured. The overhanging length of the shaft core D-112 is required to meet the total length of the impeller locking thread section, the impeller positioning smooth section and the safety margin.

Still referring to fig. 15, the impeller D-14 is provided with a stepped hole with a gradually decreasing diameter from inside to outside, the outer end of the shaft core D-112 is a stepped shaft with a gradually decreasing diameter from inside to outside, and a hole section with the smallest diameter of the stepped hole is matched with a shaft section with the smallest diameter of the stepped shaft. The shaft core D-112 is designed into a stepped shaft, so that weight reduction can be realized on the basis of ensuring structural strength, and the shaft diameter is gradually reduced to be matched with the mounting hole of the impeller D-14, so that the stress on the shaft core D-112 can be reduced.

In fig. 15, the stepped shaft includes, in order from inside to outside, a first shaft portion D-1121, a second shaft portion D-1122, and a third shaft portion D-1123, the impeller D-14 being mounted on the third shaft portion D-1123, the third shaft portion D-1123 being positioned with an optical axis at an inner end thereof and being provided with a screw thread at an outer end thereof to mount the lock nut D-16.

As shown in FIG. 15, the main shaft is of a sectional structure and comprises a first shaft section D-11, a second shaft section D-12 and a third shaft section D-13 which are sequentially installed along the axial direction and are independent in structure, and the second shaft section D-12 is positioned between the first shaft section D-11 and the third shaft section D-13. The second shaft section D-12 is a permanent magnet and is used as magnetic steel, and the sectional type main shaft is favorable for arranging the magnetic steel in the middle. The outer ends of the first shaft section D-11 and the third shaft section D-13 are respectively provided with a cavity D-111, and impellers D-14 are respectively arranged on corresponding shaft cores D-112, so that the two-stage compressor can be used. The thickness of the inner end solid structures of the first shaft section D-11 and the third shaft section D-13 directly influences the deflection and stability of the front end of the shaft core D-112, so that the thickness cannot be too thin, and the processing size can be more than 30 mm.

Further, the main shaft also comprises a connecting piece for connecting the first shaft section D-11, the second shaft section D-12 and the third shaft section D-13. The connecting piece can be of a cylindrical structure, so that the connecting strength of the rotor can be improved, the magnetic steel can be protected, and the jumping problem of the front end of the rotor can be reduced.

With the structure shown in fig. 15, the connecting member includes a first cylinder D-15, the first cylinder D-15 being coaxially disposed on the first shaft section D-11 at an end near the second shaft section D-12, and at least part of the length of the second shaft section D-12 and the third shaft section D-13 being located within the first cylinder D-15. The first cylinder D-15 can be thermally sleeved on the second shaft section D-12 and the third shaft section D-13 in a heated state, so that connection of three parts is realized, and connection is reliable.

Further, the diameter of the part of the third shaft section D-13 positioned in the first cylinder body D-15 is reduced, and a stepped shaft is formed, so that the first cylinder body D-15 is flush with the side surface of the part of the third shaft section D-13 positioned outside the first cylinder body D-15, and the dynamic balance of the rotor during working can be effectively ensured. Furthermore, the axial positioning of the first cylinder D-15 can be performed by means of the shoulder of the third shaft section D-13.

Further, the bottom of the first shaft section D-11 corresponding to the cavity D-111 along the axial direction is provided with an exhaust hole. Because the end of the first shaft section D-11, which is close to the first cylinder D-15, is of a solid structure, when the second shaft section D-12 and the third shaft section D-13 are assembled into the first cylinder D-15, the gas in the sealed area formed by the second shaft section D-12 and the first cylinder D-15 can be released, so that the installation is smooth.

As shown in FIG. 16, the connecting member includes a second cylinder D-17 integrally sleeved on the side walls of the first shaft section D-11, the second shaft section D-12 and the third shaft section D-13. The outer surface of the main shaft adopts an integral cylinder body, so that the integral continuity of the outer surface of the rotor can be ensured, gaps are avoided between the cylinder body and part of the shaft sections, and a better protection effect is achieved. With this construction, the shaft segments can also be fitted into the second cylinder D-17 by means of a shrink fit.

Further, both ends of the second cylinder D-17 are flush with the outer edges of the contact surfaces of the first shaft section D-11 and the third shaft section D-13, respectively. Referring to fig. 14 and 15, in order to match the thrust disk D-4 with the main shaft, the end of the main shaft may be provided with a reduced-size portion D-113, the reduced-size portion D-113 forming a shoulder on the main shaft, and the second cylinder D-17 may be extended only to the shoulder position.

Further, the outer end of the contact surface of the first shaft section D-11 or the third shaft section D-13 and the second cylinder body D-17 is provided with a limiting part for limiting the axial position of the second cylinder body D-17, so that the second cylinder body D-17 is easy to install and position. The limiting part can be in a step shape, and the outer diameter of the limiting part is consistent with the outer diameter of the second cylinder D-17.

The first cylinder D-15 and the second cylinder D-17 are used as magnetic steel jackets, the thickness cannot be too thick so as not to influence the magnetism of the motor, the strength of the jackets cannot be influenced too thin, and the selectable range is 3 mm-5 mm. Because the magnetic steel sheath has the function of connection, the high-temperature alloy steel material with good performance can be used for processing.

Based on the foregoing embodiments of the compressor rotor, the present disclosure also provides a compressor including the compressor rotor D-1 of each of the above embodiments. As shown in fig. 14, the compressor may be a centrifugal compressor. Alternatively, the compressor may be a centrifugal refrigeration compressor or a screw refrigeration compressor or the like.

The impeller mounting mode can prevent the main shaft or the impeller from deforming, can ensure the mounting strength of the impeller and avoid stress concentration, thereby improving the compression capacity of the compressor and being easy to detach when maintenance is needed; in addition, the connection strength of the shaft core and the main shaft can be increased by directly forming the shaft core through processing, the position precision of the shaft core is ensured, the jumping problem of the front end of the rotor can be effectively solved, and the working stability and the reliability of the compressor are improved.

As shown in FIG. 14, the two-stage centrifugal compressor comprises a first volute D-2, a second volute D-8 and a middle housing D-6, wherein the first volute D-2 and the second volute D-8 are respectively arranged at two ends of the middle housing D-6 along the axial direction to jointly form a compressor housing. The compressor rotor D-1 is arranged at the center of the compressor shell, two ends of the main shaft are respectively provided with an impeller D-14, the inner ends of the impellers D-14 are provided with diffusers D-3, when the impellers D-14 rotate at high speed, gas rotates along with the impellers, the gas is thrown into the rear diffuser D-3 to be diffused under the action of centrifugal force, and the gas with increased pressure is discharged from the spiral case.

In order to support the main shaft, radial bearings are arranged at two ends of the main shaft, the radial bearings are supported by bearing supports D-5, the bearing supports D-5 are connected to the middle shell D-6, and the radial bearings can be dynamic pressure gas bearings. A stator assembly D-7 is arranged between the main shaft and the middle shell D-6.

Because the impeller D-14 can generate axial force in the working process, two thrust bearings are arranged at one end of the main shaft and can be respectively fixed at the opposite ends of the diffuser D-3 and the bearing support D-5, and gaps are reserved between the two thrust bearings and the two ends of the thrust disc D-4 to form the thrust bearings. The radial bearing and the thrust bearing can be magnetic suspension bearings besides adopting air suspension bearings.

The working principle of the compressor is that in the working process of the compressor, a compressor rotor D-1 rotates at a high speed, gas enters a diffuser D-3 through a left impeller D-14, the gas enters a first volute D-2 after being compressed at one stage, a gas exhaust channel on the first volute D-2 guides the compressed gas into a right impeller D-14, the compressed gas enters the right diffuser D-3 after being centrifuged by the right impeller D-14, the gas enters a second volute D-8 after being compressed at two stages, and the gas is discharged out of the compressor through a gas exhaust channel on the second volute D-8.

Rotor structural modification IV

As shown in fig. 17, a schematic structural view of some embodiments of the motor rotor of the present disclosure is provided. Referring to fig. 17, in some embodiments, there is provided a motor rotor including a magnetic portion E-1 for rotating by an energizing coil and a shaft body E-2 connected to the magnetic portion E-1 and extending away from the magnetic portion E-1 in an axial direction of the motor rotor, the shaft body E-2 being provided with a cavity E-3 extending in the axial direction thereof.

The cavity E-3 extending along the axial direction of the motor rotor of the compressor is arranged on the motor rotor of the compressor, so that the weight of the electronic rotor is reduced, and the highest rotating speed of the motor rotor is improved.

In this embodiment, the cavity E-3 extends from an end of the shaft E-2 remote from the magnetic portion E-1 to an end of the shaft E-2 adjacent to the magnetic portion E-1.

In another embodiment, as shown in FIG. 18, the cavity includes a first cavity E-31 and a second cavity E-32 spaced from the first cavity E-31. A solid shaft body is arranged between the first cavity E-31 and the second cavity E-32, and plays a supporting role, so that the structural strength of the motor rotor is improved.

In another embodiment, as shown in FIG. 19, the cavity E-3 extends from an end of the shaft E-2 away from the magnetic portion E-1 toward the magnetic portion E-1 and is spaced from an end of the shaft E-2 adjacent to the magnetic portion E-1, with a solid shaft between the cavity E-3 and the magnetic portion E-1.

The shaft body E-2 comprises a first shaft body E-21 arranged at a first end of the magnetic part E-1 along the axial direction of the motor rotor, the motor rotor further comprises a sleeve E-4 connected with the first shaft body E-21, and the magnetic part E-1 is sleeved in the sleeve E-4.

In this embodiment, the sleeve E-4 is integrally formed with the first shaft E-21. In other alternative embodiments, the first shaft body E-21 is partially or entirely sleeved in the sleeve E-4.

The shaft body E-2 further comprises a second shaft body E-22 arranged at the second end of the magnetic part E-1 along the axial direction of the motor rotor, and the second shaft body E-22 is at least partially sleeved in the sleeve E-4.

The motor rotor further includes a first flow passage for discharging gas in the sleeve E-4 when the magnetic portion E-1 is fitted into the sleeve E-4.

The first flow path includes a cavity E-3 provided in the first shaft E-21. The cavity E-3 in the first shaft body E-21 extends from one end of the first shaft body E-21 adjacent to the magnetic portion E-1 to the other end. During the process of thermally sleeving the magnetic part E-1 in the sleeve E-4, the gas in the sleeve E-4 is discharged through the cavity E-3 on the first shaft body E-21.

In some embodiments, the cavity E-3 on the first shaft body E-21 extends from one end of the first shaft body E-21 adjacent to the magnetic portion E-1 towards the other end, and the first shaft body E-21 is further provided with a through hole for communicating the cavity E-3 with the external space of the shaft body E-2, optionally extending in the radial direction of the shaft body E-2. The cavity E-3 may not necessarily extend to an end of the first shaft body E-21 adjacent to the magnetic portion E-1, and during the process of shrink-fitting the magnetic portion E-1 into the sleeve E-4, the gas in the sleeve E-4 is discharged through the cavity E-3 of the first shaft body E-21 and the through hole.

The motor rotor further includes a second flow passage for exhausting gas in the sleeve E-4 when the second shaft body E-22 is fitted into the sleeve E-4.

The second flow path includes a cavity E-3 provided in the second shaft body E-22. The cavity E-3 on the second shaft body E-22 extends from one end of the second shaft body E-22 adjacent to the magnetic portion E-1 toward the other end. During the process of thermally sleeving the second shaft body E-22 in the sleeve E-4, the gas in the sleeve E-4 is discharged through the cavity E-3 provided on the second shaft body E-22.

In some embodiments, the cavity E-3 extends from one end adjacent to the magnetic portion E-1 toward the other end, and the second shaft body E-22 is further provided with a through hole communicating with the external space of the shaft body E-2 of the cavity E-3. Optionally, the through hole extends in a radial direction of the second shaft body E-2. During the process of thermally sleeving the second shaft body E-22 in the sleeve E-4, the gas in the sleeve E-4 is discharged through the cavity E-3 and the through hole provided on the second shaft body E-22.

In some embodiments, the cavity E-3 extends from an end of the second shaft body E-22 remote from the magnetic portion E-1 toward the magnetic portion E-1, the cavity E-3 is spaced from the magnetic portion E-1, and the solid shafts of the cavity E-3 and the magnetic portion E-1 are provided with an air discharge duct.

Fig. 18 shows a schematic structural view of a motor rotor of another alternative embodiment, which includes a first flow path for discharging gas in the sleeve E-4 when the magnetic part E-1 is thermally fit into the sleeve E-4, the first flow path including a first duct E-5 provided on the magnetic part E-1, the first duct E-5 extending from one end of the magnetic part E-1 in the axial direction of the motor rotor to the other end. During the thermal insertion of the magnetic portion E-1 into the sleeve E-4, the gas within the sleeve E-4 may be expelled through the first orifice E-5 in the magnetic portion E-1.

As shown in FIG. 18, the cavity E-3 provided on the first shaft body E-21 includes a first cavity E-31 and a second cavity E-32 spaced apart from the first cavity E-31.

The motor rotor further includes a second flow path for exhausting gas in the sleeve E-4 during the process of sheathing the second shaft body E-22 into the sleeve E-4, the second flow path including a cavity E-3 provided on the second shaft body E-22, the cavity E-3 extending from one end of the second shaft body E-22 adjacent to the magnetic portion E-1 to the other end.

In some embodiments, the second shaft body E-22 is provided with a through hole for communicating the cavity E-3 with the external space of the shaft body E-2. The cavity E-3 on the second shaft body E-22 extends from one end adjacent to the magnetic portion E-1 toward the other end, and the cavity E-3 may not necessarily extend to the end of the second shaft body E-22 remote from the magnetic portion E-1.

Fig. 19 shows a schematic structural view of a motor rotor of another alternative embodiment, which includes a first flow path for exhausting gas in the sleeve E-4 when the magnetic part E-1 is thermally fitted into the sleeve E-4, the first flow path including a cavity E-3 provided on the first shaft body E-21 and a second duct E-6 for communicating the cavity E-3 and an inner cavity of the sleeve E-4.

In this embodiment, the cavity E-3 on the first shaft E-21 extends from one end of the first shaft E-21 away from the magnetic portion E-1 toward the magnetic portion E-1, the cavity E-3 is spaced from the inner cavity of the sleeve E-4, a second hole E-6 is formed in the solid shaft between the cavity E-3 and the inner cavity of the sleeve E-4, and two ends of the second hole E-6 are respectively communicated with the cavity E-3 and the inner cavity of the sleeve E-4.

During the process of sleeving the magnetic part E-1 into the sleeve E-4, the gas in the sleeve E-4 is discharged through the second pore canal E-6 and the cavity E-3 arranged on the first shaft body E-21.

In some embodiments, the second flow path for venting gas when the second shaft body E-22 is nested into the sleeve E-4 includes a first orifice provided on the magnetic portion E-1 and a cavity E-3 provided on the first shaft body E-21.

Referring to fig. 17 to 19, the motor rotor of the present embodiment mainly includes three sections, namely, a first shaft body E-21, a magnetic portion E-1, and a second shaft body E-22, wherein the middle section is the magnetic portion E-1, and cavities E-3 extending axially are provided on the first shaft body E-21 and the second shaft body E-22. The whole quality of the motor rotor is reduced, so that the critical rotating speed of the rotor is improved, and the bearing capacity of the bearing is improved.

The compressor adopting the rotor structure modification example can be a two-stage dynamic pressure air suspension centrifugal compressor. The compressor comprises a first compression part, a second compression part for compressing the refrigerant compressed by the first compression part, a motor for driving the first compression part and the second compression part, and a circulating air supply self-cooling system. The circulating air supply self-cooling system provides a refrigerant for cooling and/or lubricating the bearing E-12 in the cavity of the compressor.

The motor rotor system of the compressor mainly comprises a centrifugal impeller of a first compression part, a hollow first shaft body E-21, a magnetic part E-1, a hollow second shaft body E-22, a centrifugal impeller of a second compression part and a thrust bearing thrust body. Wherein, the shaft body E-2 of the motor rotor of the compressor comprises a hollow structure and a solid structure. The motor rotor of the structure type can be applied to rotary machines such as centrifugal refrigeration compressors, screw refrigeration compressors and the like.

The bearing related to the scheme can be a sliding bearing, a rolling bearing, a magnetic suspension bearing or an air suspension bearing, and the air suspension bearing is preferable due to the fact that the oil-free environment-friendly structure is simple.

The novel three-section hollow high-speed rotor structure is shown in FIG. 18, and the motor rotor mainly comprises a first shaft body E-21, a magnetic part E-1 and a second shaft body E-22, wherein the left and right shaft bodies E-2 are processed into a hollow structure, and the middle part of the novel three-section hollow high-speed rotor structure is an integral magnetic part E-1, so that a middle mandrel is omitted, the structure is simplified, and the assembly is reduced. The first shaft body E-21 at the left end is processed into a two-section hollow structure, the left end is a cooling gas channel, and the right end is a hollow sleeve for assembling the magnetic part E-1. Or the right second shaft body E-22 is processed to be similar to the first shaft body E-21 in structure, the left first shaft body E-21 solid part can be arranged at a position far away from the magnetic part E-1, a first pore canal E-5 is processed in the center of the magnetic part E-1, and the first pore canal can be a light hole or a threaded hole. The number of the first pore channels E-5 is reasonably arranged according to the space structure. Similarly, the second shaft body E-22 at the right end may use the same structure as the first shaft body E-21. The hollow structures of the left and right first shaft bodies E-21 and the second shaft bodies E-22 can be also processed into full holes or processed into small holes and threaded holes at solid parts, but the diameters of the holes need to be strictly controlled, so that the contact area between the shaft and the magnetic part E-1 is prevented from being too small, and the magnetic part E-1 is prevented from being damaged, namely D _Hole(s)≤(1/2)D_{Magnetic part}. The volumes of the cavities E-3 of the two sections of the shaft body E-2 are kept the same or differ by the volume of the sleeve sections, or the center of gravity of the motor rotor is close to the center of the integral rotor through the adjustment of the solid sections of the shaft body E-2.

The motor rotor is subjected to split type machining, and the first shaft body E-21, the second shaft body E-22 and the magnetic part E-1 are respectively machined, so that the required key size can be effectively ensured, the machining complexity is simplified, the rotor inspection is facilitated, and the inspection precision is improved. A small hole can be machined in the centers of the two sections of shaft bodies E-2 and the magnetic part E-1, but is influenced by the material of the magnetic part E-1, and the size of the small hole cannot be too large, and is preferably smaller than or equal to E-4mm in phi D ₃. Because the gas existing in the motor rotor in the hot sheathing process can not be discharged, small hole exhaust is required to be added to the solid part of the first shaft body E-21 or the second shaft body E-22, and the aperture is 2-3 mm.

Through the structure, the problem of bearing capacity of the bearing is effectively solved, the critical rotation speed of the rotor is improved by reducing the length of the cantilever end, and the working stability and reliability of the motor are further improved.

Rotor structural modification five

Fig. 20 shows a schematic structural view of a motor rotor of the compressor of the present embodiment. Referring to fig. 20, in some embodiments, a motor rotor includes a magnetic portion F-1 for rotating by an energizing coil F-13 and a shaft body F-2 connected to the magnetic portion F-1 and extending away from the magnetic portion F-1 in an axial direction of the motor rotor, the shaft body F-2 including a cavity F-3 extending in the axial direction thereof and a connecting portion F-5 for connecting a compression work member, the connecting portion F-5 and the cavity F-3 being spaced apart. Wherein the connecting part F-5 is arranged at the end part of the shaft body.

The cavity F-3 extending along the axial direction of the motor rotor is arranged on the motor rotor in the embodiment, so that the weight of the electronic rotor is reduced, and the highest rotating speed of the motor rotor is improved.

The cavity F-3 is arranged at intervals with the connecting part for connecting the compression working part, and the motor rotor is provided with the weight-reducing cavity F-3 and simultaneously reserves the connecting part for installing the compression working part, so that the motor rotor has the advantages of simple structure, easiness in processing and low manufacturing cost.

The shaft body F-2 includes a first shaft body F-21 located at a first end of the magnetic portion F-1 in the axial direction and a second shaft body F-22 located at a second end of the magnetic portion F-1 in the axial direction.

The cavity F-3 in the first shaft body F-21 extends from an end of the first shaft body F-21 adjacent to the magnetic portion F-1 toward the first end provided with the connecting portion F-5. The cavity F-3 in the second shaft body F-22 extends from one end of the second shaft body F-22 adjacent to the magnetic portion F-1 toward the other end. Optionally, an end of the second shaft body F-22 remote from the magnetic portion F-1 is provided with a connecting portion F-5.

The motor rotor also comprises a sleeve F-4 connected with the shaft body F-2, and the magnetic part F-1 is sleeved in the sleeve F-4. At least part of the first shaft body F-21 and at least part of the second shaft body F-22 are sleeved in the sleeve F-4.

In the process of assembling the motor rotor, the first shaft body F-21, the magnetic part F-1 and the second shaft body F-22 can be integrally sleeved into the sleeve F-4 with two open ends, and in the process of installing the first shaft body F-21, the magnetic part F-1 and the second shaft body F-22 into the sleeve, the gas in the sleeve F-4 can be discharged through the port of the sleeve F-4, so that an additional exhaust runner is not required.

As shown in FIG. 21, in some embodiments, the sleeve F-4 and the first shaft F-21 are integral. The magnetic part F-1 and the second shaft body F-22 are sleeved in the sleeve F-4 in sequence. The motor rotor further includes a first flow passage for discharging gas inside the sleeve F-4 when the magnetic portion F-1 is fitted into the sleeve F-4.

Optionally, the first flow passage includes a first duct provided on the magnetic portion F-1, the first duct extending from one end to the other end of the magnetic portion F-1 in the axial direction of the motor rotor. When the magnetic part F-1 is sleeved into the sleeve F-4, the gas in the sleeve F-4 is discharged to the side of the magnetic part F-1, which is opposite to the first shaft body F-21, through the first pore canal.

Optionally, the first flow passage includes a second orifice disposed on the first shaft F-21, the second orifice communicating with the cavity F-3 on the first shaft F-21. When the magnetic part F-1 is sleeved into the sleeve F-4, the gas in the sleeve F-4 is discharged through the cavity F-3 and the second pore canal on the first shaft body F-21.

According to another aspect of the present invention, there is also provided a compressor, and fig. 21 shows a schematic structural view of the compressor of the present embodiment. As shown in fig. 21, the compressor of the present embodiment includes a motor rotor including a magnetic portion F-1 and a shaft body F-2 connected to the magnetic portion F-1.

The compressor also includes a centrifugal compressor driven by the motor rotor. The centrifugal compression part comprises a centrifugal impeller F-8 arranged on a connecting part F-5 of the motor rotor, a diffuser F-9 used for compressing the refrigerant accelerated by the centrifugal impeller F-8 and a volute F-10 used for discharging the compressed refrigerant.

The centrifugal compression portion includes a first centrifugal compression portion disposed at a first end of the motor rotor and a second centrifugal compression portion disposed at a second end of the motor rotor. The air suction port of the second centrifugal compression part is communicated with the air discharge port of the first centrifugal compression part, and the second centrifugal compression part is used for compressing the refrigerant compressed by the first centrifugal compression part.

The compressor further includes a bearing support F-11 and a bearing F-12 mounted on the bearing support F-11, the bearing F-12 for carrying a motor rotor. The bearing F-12 is an air suspension bearing. Preferably, the gas suspension bearing is a dynamic pressure gas suspension bearing.

As shown in fig. 20, the motor rotor of the compressor of the present embodiment mainly comprises three sections, namely a first shaft body F-21, a magnetic portion F-1 and a second shaft body F-22, wherein the middle section is the magnetic portion F-1, and cavities F-3 extending axially are provided on the first shaft body F-21 and the second shaft body F-22. The whole quality of the motor rotor is reduced, so that the critical rotating speed of the rotor is improved, and the bearing capacity of the bearing is improved.

The compressor of the embodiment is a two-stage dynamic pressure air suspension centrifugal compressor. The compressor comprises a first compression part, a second compression part for compressing the refrigerant compressed by the first compression part, a motor for driving the first compression part and the second compression part, and a circulating air supply self-cooling system. The circulating air supply self-cooling system provides a refrigerant for cooling and/or lubricating the bearing F-12 in the cavity of the compressor.

The motor rotor system of the compressor mainly comprises a centrifugal impeller F-8 of a first compression part, a hollow first shaft body F-21, a magnetic part F-1, a hollow second shaft body F-22, and a centrifugal impeller F-8 of a second compression part, and a thrust bearing thrust body. Wherein, the shaft body F-2 of the motor rotor of the compressor comprises a hollow structure and a solid structure. The motor rotor of the structure type can be applied to rotary machines such as centrifugal refrigeration compressors, screw refrigeration compressors and the like.

As shown in fig. 21, the motor rotor mainly comprises a first shaft body F-21, a magnetic part F-1 and a second shaft body F-22, wherein the left and right shaft bodies F-2 are processed into a hollow structure, and the middle part of the motor rotor is an integral magnetic part F-1, so that a middle core shaft is omitted, the structure is simplified, and the assembly is reduced. The connecting part F-5 of the first shaft body F-21, which is far away from the magnetic part and is used for installing the impeller, is of a solid structure, and the cavity F-3 on the first shaft body F-21 extends from one end of the first shaft body F-21 adjacent to the magnetic part to the other end.

The right-end second shaft body F-22 is of a similar structure to the first shaft body F-21, and the first shaft body F-21 and the second shaft body F-22 are symmetrically arranged on both sides of the magnetic portion F-1.

Sleeve F-4 is sleeved on the outer surfaces of the first shaft body F-21, the magnetic part F-1 and the second shaft body F-22 so as to connect the first shaft body F-21, the magnetic part F-1 and the second shaft body F-22 together. The three parts are in interference connection with the sleeve, the sleeve F-4 integrally penetrates through the three parts, and the structure does not need to be additionally provided with an exhaust hole in the installation process, so that hot jacket gas can be effectively prevented from being discharged.

The connecting parts F-5 at the two ends of the motor rotor are solid structures. The connection F-5 is used for installing the centrifugal impeller F-8. The centrifugal impeller F-8 and the connecting part F-5 are axially locked by using a locking nut, and meanwhile, the radial positioning of the centrifugal impeller F-8 can be connected by using interference or clearance.

The inner diameter of the cavity F-3 on the shaft body F-2 needs to be strictly controlled to prevent the damage of the magnetic part F-1, namely D _Hole(s)≤(1/2)D_{Magnetic part}, due to the small contact area between the shaft body and the magnetic part F-1. The volumes of the cavities F-3 on the two shaft bodies F-2 are kept the same, or the gravity center is close to the center of the integral rotor by adjusting the solid sections of the shaft bodies. The motor rotor is subjected to split type machining, and the first shaft body F-21, the second shaft body F-22 and the magnetic part F-1 are respectively machined, so that the required key size can be effectively ensured, the machining complexity is simplified, the rotor inspection is facilitated, and the inspection precision is improved. The hollow structure is close to the side of the magnetic part F-1, so that the machining precision of the hole can be reduced, and the machining efficiency can be improved.

The dynamic pressure gas suspension bearing is used, so that the compressor does not need to use lubricating oil and a control system, the compressor is more environment-friendly and simpler in structure, the problem of difficulty in integrated processing and inspection of a rotor of the compressor is solved, the critical rotating speed of the rotor is effectively improved, the working reliability and safety of a shafting are ensured, and the maintenance cost of the compressor is reduced.

Rotor structural modification six

As shown in fig. 22 and 23, an embodiment of the present invention discloses a compressor rotor. The compressor rotor includes a motor rotor G-10, a locking lever G-20, an impeller, and a locking member G-40.

As shown in fig. 22, the motor rotor G-10 includes a plurality of rotor segments fixedly connected in the axial direction. The impeller is located at the end of the motor rotor G-10 and is connected to the locking lever G-20. The locking member G-40 locks the impeller to the locking lever G-20. The end shaft section G-12 of one end of the motor rotor G-10 is provided with a first cavity G-121 at an outer end and a second cavity G-122 at an inner end, and a mounting portion G-123 is provided between the first cavity G-121 and the second cavity G-122, the mounting portion G-123 being adjacent to one end of the motor rotor G-10, and a locking lever G-20 extending into the first cavity G-121 and being fixed to the mounting portion G-123 and being coaxial with the motor rotor G-10.

In some embodiments, the mounting portion G-123 is configured as an inwardly protruding annular protrusion, and the inner end of the locking lever G-20 is secured in a central hole of the annular protrusion.

In some embodiments, the mounting portion G-123 is configured as a plurality of protrusions protruding inward and spaced apart circumferentially, and the inner end of the locking lever G-20 is fixed between the plurality of protrusions.

An interference fit may be used between the inner end of the locking lever G-20 and the mounting portion G-123.

In the invention, the first cavity G-121 and the second cavity G-122 are arranged in the motor rotor G-10, so that the motor rotor G-10 is as light as possible, thereby being beneficial to reducing the overall weight of the motor rotor G-10 and the compressor rotor and improving the critical rotation speed of the compressor rotor. And the mounting part G-123 is adjacent to the end part of the motor rotor, thereby reducing the cantilever length of the locking rod G-20, improving the jumping problem of the impeller, and improving the overall rigidity of the locking rod G-20, thereby facilitating the dynamic balance of the compressor rotor.

As shown in fig. 22, in some embodiments, the compressor may be a centrifugal compressor and the impeller is a centrifugal impeller of the centrifugal compressor. Other compressors such as screw refrigeration compressors may also be used.

The impeller may be provided only on one side of the motor rotor G-10, or may be provided on both sides of the motor rotor G-10, respectively. The impellers on each side may be single-stage or multi-stage. For example, the number of impellers on one side of the motor rotor may be one or two or more.

In some embodiments, as shown in FIGS. 22 and 23, the locking lever G-20 is connected at both ends to the impeller, respectively.

The end of the locking lever G-20 is provided with external threads, and the locking component comprises a locking nut matched with the external threads of the locking lever G-20.

As shown in FIG. 22, in some embodiments, the compressor rotor includes a motor rotor G-10, a primary centrifugal impeller G-30, and a secondary centrifugal impeller G-50. External threads are respectively arranged at the left end and the right end of the locking rod G-20. The primary centrifugal impeller G-30 is locked to the left end of the locking lever G-20 by a locking nut G-40 as a locking member. The secondary centrifugal impeller G-50 is locked to the right end of the locking lever G-20 by a locking nut G-40 as a locking member.

As shown in FIG. 22, in some embodiments, a plurality of rotor segments of the motor rotor G-10 include a permanent magnet G-11 and two end shaft segments G-12. Two end shaft sections G-12 are fixed at two ends of the permanent magnet G-11

The permanent magnet G-11 may be solid and may be columnar in shape. The permanent magnet G-11 is used as a motor rotor G-10 to form a motor for driving the compressor rotor to rotate together with a motor stator of the compressor. The material of the permanent magnet G-11 is, for example, magnetic steel.

As shown in fig. 22, the motor rotor G-10 of the compressor rotor of the embodiment of the present invention includes a permanent magnet G-11, two end shaft sections G-12, and a magnetic steel sheath G-14. The left end of the magnetic steel sheath G-14 and the right end of the first end shaft section G-12 are integrally arranged, and the magnetic steel sheath G-14 is tightly sleeved on the outer circumferences of the permanent magnet and the right end shaft section G-12 so as to connect the permanent magnet G-11 with the two end shaft sections G-12.

In some embodiments, as shown in FIG. 23, the magnetic steel sheath G-14, the permanent magnet G-11 and the two end shaft segments G-12 are separated from each other, the magnetic steel sheath G-14 is securely sleeved over the entire outer circumference of the permanent magnet G-11 and the two end shaft segments G-12, for example, by heat-sleeving, i.e., heating the magnetic steel sheath G-14, and then sleeving the magnetic steel sheath over the permanent magnet G-11 and the two end shaft segments G-12.

Modification of motor drive system

Referring to fig. 24 and 25, in some embodiments, the motor drive system provided by the present disclosure may include a motor cylinder N-15, a motor stator N-16, and a motor rotor N-14. The motor cylinder N-15 has a motor accommodation chamber. The motor stator N-16 is disposed within the motor receiving cavity. The motor rotor N-14 is rotatably arranged in the motor accommodating cavity, the motor stator N-16 is sleeved on the outer side of the motor rotor N-14, an air gap channel Q is formed between the inner peripheral wall of the motor stator and the outer peripheral wall of the motor rotor N-14, and a cooling medium channel used for enabling cooling medium to flow through and arranged in a bending mode is arranged in the air gap channel Q.

The cooling medium in the embodiment of the invention can be fully contacted with the outer peripheral wall of the motor rotor and the inner peripheral wall of the motor stator when passing along the bent cooling medium channel, so as to fully cool the motor, thereby improving the cooling effect of the motor.

In this embodiment as well, as shown in fig. 25 and 26, the cooling medium passage includes a first spiral groove N-144 provided on the outer peripheral wall of the motor rotor N-14. The cooling medium passes through the air gap passage Q under the guiding action of the first spiral groove N-144 to absorb heat of the outer peripheral wall of the motor rotor so as to cool more sufficiently.

In the present embodiment, the spiral direction of the first spiral groove N-144 is the same as the rotation direction of the motor rotor N-14.

As shown in fig. 26 to 29, the outer peripheral wall of the motor rotor N-14 is provided with protrusions N-145 extending in a spiral shape, and first spiral grooves N-144 are formed between adjacent protrusions N-145. The cross section of the protrusion N-145 of this embodiment is right trapezoid (shown in fig. 27) or triangle (shown in fig. 28) or circle (shown in fig. 29) or rectangle.

The first helical groove of this embodiment may be a single helix or a double helix.

As shown in fig. 26, the motor rotor N-14 of the present embodiment includes a shaft body and a permanent magnet N-143 provided in the shaft body, and a first spiral groove is provided on the outer peripheral wall of a portion of the shaft body connected to the permanent magnet N-143. In the embodiment, the first spiral groove is formed in the peripheral wall of the part, connected with the permanent magnet N-143, of the shaft body, so that the cooling medium can sufficiently cool the permanent magnet, and the permanent magnet is prevented from being demagnetized due to overhigh temperature, so that the reliability of the motor is improved. In this embodiment, as shown in fig. 26, the shaft body includes a first end shaft section N-141 and a second end shaft section N-142, the first end shaft section N-141 has a mounting sleeve, the permanent magnet N-143 and the second end shaft section N-142 are both mounted in the mounting sleeve, and the first spiral groove is provided on the first end shaft section N-141.

The shaft body of the embodiment also has a hollow portion at the end portion and a vent hole communicating with the hollow portion and the motor accommodation chamber, and the cooling medium enters the motor accommodation chamber through the hollow portion and the vent hole.

As shown in fig. 26, the first end shaft section N-141 of the present embodiment includes a hollow portion N-146 and a vent hole N-147 that communicates the hollow portion N-146 with the motor accommodation chamber. When the motor rotor N-14 rotates at a high speed, heat in the motor rotor N-14 can be taken away by flowing a fluid such as a refrigerant through the hollow portion N-146 and the ventilation hole N-147. The second end shaft section N-142 of the present embodiment is also symmetrically provided with a hollow portion and a vent hole.

In the above embodiment, the motor rotor N-14 comprises a three-section structure, the left and right end shaft sections are processed into a hollow structure, and the middle is an integral permanent magnet, so that the structure is simplified, and the assembly is reduced.

As shown in FIG. 25, the motor cylinder N-15 of the present embodiment is provided with a cooling medium inlet N-152, a second spiral groove N-151, and a cooling medium outlet N-153. The second spiral groove N-151 is arranged on the inner wall of the motor cylinder N-15, and a motor cylinder spiral flow passage is formed between the second spiral groove N-151 and the outer peripheral wall of the motor stator N-16. The cooling medium enters the motor cylinder spiral passage through the cooling medium inlet N-152 to cool the motor stator N-16.

The cooling medium enters from the cooling medium inlet N-152 and enters into the left end of the motor accommodating cavity through the second spiral groove N-151, the cooling medium forms high pressure after being gathered at the left end of the motor accommodating cavity, then the cooling medium flows to the right end through an air gap channel between the motor stator and the motor rotor under the guiding action of the second spiral groove of the peripheral wall of the motor rotor N-14, and the heat of the outer surface of the motor rotor is absorbed in the process, so that the cooling is more sufficient.

As shown in fig. 24, the present embodiment also provides a compressor including the motor driving system of the above embodiment, and the first scroll casing N-11 and the second scroll casing N-19 provided at both axial ends (left and right ends in fig. 24) of the motor cylinder N-15, respectively. The compressor of the present embodiment further includes a primary impeller N-20 and a secondary impeller N-21 respectively fixed to both ends of the motor rotor N-14. Corresponding to the first-stage impeller N-20 and the second-stage impeller N-21, two compression chambers are respectively a first-stage compression chamber and a second-stage compression chamber. The first-stage impeller N-20 is positioned in the first-stage compression cavity, and the second-stage impeller N-21 is positioned in the second-stage compression cavity.

The compressor of this embodiment further includes a first diffuser N-12, a first bearing support N-13, a first radial bearing N-22, a second diffuser N-18, a second bearing support N-17, and a second radial bearing N-23, and a first thrust bearing and a second thrust bearing. The first bearing support N-13 and the second bearing support N-17 are respectively fixed inside the motor cylinder N-15 and are respectively positioned at two axial ends of the motor stator N-16. The first radial bearing N-22 is located in the first bearing support N-13 and the second radial bearing N-23 is located in the second bearing support N-17. The first radial bearing N-22 and the second radial bearing N-23 are supported at both axial ends of the motor rotor N-15, respectively, so as to support the motor rotor N-14 in the motor accommodation chamber of the motor cylinder N-15.

The compressor further includes a thrust disc N-24 provided at one axial end (left end in fig. 24) of the motor rotor N-14. A first thrust bearing is arranged between the first bearing support N-13 and the thrust disc N-24, and a second thrust bearing is arranged at one end of the first diffuser N-12, which is far away from a diffusion structure on the diffuser N-12, so that the motor rotor N-14 is positioned in the motor cylinder N-15 at the upper limit of the axial direction.

The bearing of this embodiment may be a sliding bearing, a rolling bearing, a magnetic suspension bearing, or an air suspension bearing.

When the bearing is an air suspension bearing, the cooling medium enters the motor accommodating cavity of the motor cylinder body, and the radial bearing is positioned in the motor accommodating cavity, so that the cooling medium can directly supply air for the radial bearing and cool the radial bearing. Meanwhile, the cooling medium in the motor accommodating cavity can enter the left cavity through the upper edge opening of the bearing support under the high pressure effect to supply air and cool the thrust bearing.

As shown in fig. 24, in some embodiments, the compressor may be a centrifugal compressor.

The operation and principle of the motor cooling medium circulation will be described below with reference to fig. 24 to 26 by taking a refrigeration compressor used as a cooling medium circulation system as an example of the compressor of each of the above embodiments. The cooling medium is a refrigerant at this time.

When the refrigerant enters the motor cylinder spiral flow channel through the cooling medium inlet N-152, the refrigerant spirally flows between the motor cylinder N-15 and the motor stator N-16, the refrigerant flowing in the motor cylinder spiral flow channel continuously absorbs heat to reduce the temperature of the surface of the motor stator N-16, and after the refrigerant continuously circulates, the refrigerant enters the left end of the motor accommodating cavity of the motor from the flow channel outlet N-154. When more refrigerants gather in the cavity at the left end to form high pressure, the refrigerants flow to the right end through the air gap channel Q between the motor stator N-16 and the motor rotor N-14 under the guiding action of the first spiral groove of the motor rotor N-14, and the heat of the outer surface of the motor rotor N-14 is absorbed, so that the cooling is more sufficient. Because a large amount of refrigerants gather at the left end to form high pressure, the matched part of the motor rotor and the motor stator is designed into a spiral line shape, the refrigerant gathered at the left end has a guiding effect, and the left end refrigerants can flow to the right end through an air gap channel between the stator and the motor rotor under the rotation effect and the high pressure effect to cool the outer surface of the motor rotor and the inner surface of the motor stator again.

The refrigerant enters the motor accommodating cavity of the motor after passing through the spiral flow passage of the motor cylinder body, and the refrigerant can directly supply air for the radial bearing and cool the radial bearing as the radial bearing is positioned in the motor accommodating cavity. And simultaneously, the refrigerant in the motor accommodating cavity supplies air and cools the thrust bearing through the upper edge opening of the bearing support under the high pressure.

From the above, the compressor of the embodiment not only effectively solves the cooling problem of the compressor, but also supplies air for the compressor bearing, and omits an external air supply device.

Bearing support structure modification example one

As shown in fig. 32-33, a schematic structural view of some embodiments of the bearing support of the present disclosure is shown. Referring to fig. 32 and 33, in some embodiments, the present disclosure provides a bearing support H-2 including a first end and a second end. The second end and the first end of the bearing support H-2 may be opposite ends in the axial direction of the bearing support H-2. The radial dimension of at least part of the bearing support H-2 increases gradually in the direction from the first end to the second end of the bearing support H-2. The axial direction of the bearing support H-2 is consistent with the axial direction of the shaft supported by the bearing. The radial direction of the bearing support H-2 is consistent with the radial direction of the shaft supported by the bearing. In some embodiments, the shaft supported by the bearing is the rotor H-8 of the compressor. In some embodiments, the radial dimension of the first end of the bearing support H-2 is smaller than the radial dimension of the second end. In some embodiments, bearing support H-2 also includes bearing hole H-21, bearing hole H-21 for mounting a bearing.

In some embodiments, bearing support H-2 further includes an annular groove H-22, with annular groove H-22 disposed about bearing aperture H-21. In some embodiments, the second end of the bearing support H-2 includes a stop H-23, the stop H-23 being adapted to abut against the inside of the piece to be mounted.

In some embodiments, the second end of the bearing support H-2 includes a connection portion H-24, the connection portion H-24 extending radially outward of the bearing support H-2 relative to the stop portion H-23 for connection with a piece to be mounted. In some embodiments, a spigot is formed between the limiting part H-23 and the connecting part H-24 for being matched and positioned with the piece to be installed. In some embodiments, the component to be mounted is a shell H-1 of the compressor. In some embodiments, the connecting portion H-24 is annular and disposed circumferentially about the spacing portion H-23.

In some embodiments, bearing support H-2 further includes bearing hole H-21, bearing hole H-21 being disposed along an axial direction of bearing support H-2 for mounting a bearing. In some embodiments, bearing support H-2 further includes a vent H-25, vent H-25 being disposed radially of bearing support H-2, a first end of vent H-25 being in communication with bearing hole H-21, and a second end of vent H-25 being in communication with a radially outer portion of bearing support H-2.

As shown in fig. 30, a schematic diagram of a compressor is provided for some embodiments. Referring to FIG. 30, in some embodiments, the compressor includes a housing H-1. End caps may be provided at both ends of the housing H-1 along the central axis. The compressor may include a motor rotor H-8 and a motor stator H-9 disposed within a housing H-1. The motor rotor H-8 is disposed along the central axis of the housing H-1. The motor stator H-9 is arranged between the inner wall of the shell H-1 and the motor rotor H-8 and is fixedly connected with the inner wall of the shell H-1. In some embodiments, both ends of motor rotor H-8 are provided with radial bearings H-3 and bearing supports H-2.

In some embodiments, the compressor includes a bearing support H-2, the bearing support H-2 being disposed within the housing H-1. Further, the bearing support H-2 is suitable for a gas bearing, such as a dynamic pressure gas bearing. In some embodiments, a first end of bearing support H-2 is adjacent to an end cap portion of housing H-1 and a second end of bearing support H-2 is coupled to an inner wall of housing H-1.

In some embodiments, the first and second ends of the bearing support H-2 are axially opposite ends of the bearing support H-2, the first end of the bearing support H-2 being proximate to the end of the housing H-1 relative to the second end of the bearing support H-2. The end of the housing H-1 is the end of the housing H-1 near the bearing support H-2. In some embodiments, the radial dimension of at least a portion of bearing support H-2 increases gradually in the direction from the first end to the second end of bearing support H-2.

The inventor finds that the radial force born by the bearing support H-2 is basically equal to the gravity of the rotor, the radial load is relatively small, the radial strength requirement of the bearing support H-2 is not high, but when the bearing support H-2 bears the radial load and the axial load at the same time, the bearing support H-2 also needs to have certain structural strength to bear the radial load and the axial load, so that the radial dimension of at least part of the bearing support H-2 provided by the disclosure is gradually increased, the radial strength requirement can be met, and the radial dimension is gradually increased, so that the structural strength of the bearing support H-2 can be improved.

In the related art, the radial dimension of the whole bearing support H-2 is set to be consistent by increasing the wall thickness and additionally arranging reinforcing ribs, so that the structural strength of the bearing support H-2 is increased, and the problems of increased equipment weight and increased cost are caused.

The inventor also finds that the axial load borne by the bearing support H-2 is larger than the radial load, and the axial load is transmitted to the bearing support H-2 through the thrust bearing H-4 and the thrust bearing fixing plate H-5, so that the first end of the bearing support H-2 provided by the disclosure is matched with the thrust bearing fixing plate H-5 and the thrust bearing H-4, the radial dimension of the first end of the bearing support H-2 is smaller than the radial dimension of the second end of the bearing support H-2 connected with the shell H-1, and the radial dimension of at least part of the bearing support H-2 is gradually increased along the direction from the first end to the second end of the bearing support H-2, so that the axial force can be well transmitted to the shell H-1 of the compressor motor, the strength of the bearing support H-2 is improved, and the service life of the bearing support H-2 is prolonged.

In some embodiments, the radial dimension of the bearing support H-2 in the direction from the first end to the second end of the bearing support H-2 increases gradually, and the bearing support structure can meet the strength requirement and reliably transmit power.

In some embodiments, bearing support H-2 is V-shaped, and has high structural strength and is convenient for casting. The dynamic pressure bearing high-precision assembly can be guaranteed, and the stability of a bearing rotor system can be improved. In some embodiments, the radial dimension of the first end of bearing support H-2 is less than the radial dimension of the second end of bearing support H-2.

In some embodiments, bearing support H-2 includes bearing hole H-21, bearing hole H-21 for mounting a bearing. In some embodiments, bearing support H-2 includes an annular groove H-22, with annular groove H-22 disposed about bearing aperture H-21. Optionally, the cross section of the annular groove H-22 is V-shaped and is matched with the V-shaped structure of the bearing support H-2.

The bearing support H-2 is hollowed out around the bearing hole H-21 to form a V-shaped annular groove H-22 so as to ensure that the wall thickness of the casting is relatively uniform, reduce the dead weight of the support and facilitate casting and forming.

In some embodiments, the inner wall of the housing H-1 is provided with a mounting portion extending towards the center of the housing H-1 for connection with the second end of the bearing support H-2. In some embodiments, the second end of the bearing support H-2 includes a stop H-23, the stop H-23 abutting against the inside of the mounting portion.

In some embodiments, the second end of the bearing support H-2 further includes a connecting portion H-24, the connecting portion H-24 extending radially outward of the bearing support H-2 relative to the spacing portion H-23 for connection with the mounting portion.

In some embodiments, a spigot is formed between the limiting portion H-23 and the connecting portion H-24 for mating positioning with the mounting portion. In some embodiments, the connecting portion H-24 is connected with the mounting portion arranged on the inner wall of the shell H-1 through a pin, and the bearing support H-2 can ensure high-precision assembly of the bearing through the mode that the pin and the arranged mounting spigot are positioned together.

In some embodiments, the connecting portion H-24 is annular and disposed circumferentially about the spacing portion H-23. In some embodiments, bearing support H-2 includes bearing hole H-21, bearing hole H-21 for mounting a bearing. In some embodiments, bearing support H-2 includes a vent H-25, vent H-25 being disposed radially of bearing support H-2, a first end of vent H-25 being in communication with bearing aperture H-21, and a second end of vent H-25 being in communication with a radially outer portion of bearing support H-2.

In some embodiments, the compressor includes a radial bearing H-3, the radial bearing H-3 being disposed within the bearing bore H-21. Further, the radial bearing H-3 is connected with the bearing support H-2 in an interference fit manner.

In some embodiments, the compressor further includes a thrust bearing H-4, the thrust bearing H-4 being disposed at a first end of the bearing support H-2. The air hole H-25 communicates the space where the radial bearing H-3 is located with the space where the thrust bearing H-4 is located, so that the working back pressure of the thrust bearing H-4 and the working back pressure of the radial bearing H-3 are consistent, and the stability of a bearing rotor system is improved.

Optionally, 4-12 vent holes H-25 which are used for communicating the space where the radial bearing H-3 is located with the space where the thrust bearing H-4 is located are uniformly distributed on the bearing support H-2, so that the radial bearing H-3 and the thrust bearing H-4 can be ensured to be in the same working environment, and the stability of a bearing rotor system is improved.

In some embodiments, the compressor includes a thrust bearing retainer plate H-5, the thrust bearing retainer plate H-5 being disposed between the thrust bearing H-4 and the first end of the bearing support H-2. The thrust bearing fixing plate H-5 is fixedly connected with the first end of the bearing support H-2. The thrust bearing H-4 is fixedly connected with the thrust bearing fixing plate H-5.

The thrust bearing fixing plate H-5 is provided with a fitting portion extending outwardly for fitting with a hole provided on the first end portion of the bearing holder H-2. Further, the bearing hole H-21 formed in the bearing support H-2 comprises a first hole and a second hole, the first hole is close to the first end of the bearing support H-2 relative to the second hole, the aperture of the first hole is larger than that of the second hole, the radial bearing H-3 is arranged in the bearing hole H-21, and a gap between the radial bearing H-3 and the first hole is used for accommodating a matching part formed in the thrust bearing fixing plate H-5.

The first end of the bearing support H-2 is the mounting end of the thrust bearing fixing plate H-5, and the thrust bearing H-4 is locked on the thrust bearing fixing plate H-5 through a screw.

Radial bearings H-3 are arranged in bearing holes H-21 in the bearing support H-2, the bearing support H-2 is positioned on a shell H-1 of the compressor motor through pins and rabbets, and vent holes H-25 arranged on the bearing support H-2 are used for guaranteeing that working air pressure environments of the thrust bearings H-4 and the radial bearings H-3 are consistent.

In some embodiments, the compressor includes a rotor H-8 and a stator H-9. The rotor H-8 is disposed along the central axis of the housing H-1. The stator H-9 is arranged between the inner wall of the shell H-1 and the rotor H-8 and is fixedly connected with the inner wall of the shell H-1.

Both ends of the rotor H-8 are provided with radial bearings H-3 and bearing supports H-2. One end of the rotor H-8 is provided with a thrust bearing H-4 and a thrust bearing fixing plate H-5, and the radial bearing H-3 is axially limited by the thrust bearing fixing plate H-5.

In some embodiments, the compressor includes a thrust disc H-6 and a diffuser H-7. The diffuser H-7 is provided at an end of the housing H-1. The thrust disk H-6 is fixedly arranged on the rotor H-8, thrust bearings H-4 are arranged on two opposite sides of the thrust disk H-6, the thrust bearing H-4 on one side is fixedly arranged on the thrust bearing fixing plate H-5, and the thrust bearing H-4 on the other side is fixedly arranged on the diffuser H-7. Further, the radial bearing H-3 and the thrust bearing H-4 are gas bearings. Further, the radial bearing H-3 and the thrust bearing H-4 are dynamic pressure gas bearings.

The dynamic pressure gas bearing supported rotary machine has extremely high requirements on the coaxial bearings H-3 on both sides of the rotor H-8, and if the coaxiality is poor, the bearing performance is lowered, and if serious, the rotor cannot float.

The bearing support H-2 provided by the disclosure adopts a double positioning mode of the pin and the spigot together in the positioning aspect, the coaxiality of the assembled bearing can be ensured by the spigot, then the pin is used for accurate positioning, the pin can be horizontally arranged or vertically arranged, the final positioning is completed by the spigot and the pin, and the micron-sized coaxiality of the two radial bearings H-3 is ensured.

The bearing support H-2 is provided with a plurality of (for example, four) vent holes H-25, so that the bearing support H-2 is communicated left and right (left and right in FIG. 30), namely, one side where the thrust bearing H-4 is located is left, and one side where the radial bearing H-3 is located is right, and the running back pressures of the thrust bearing H-4 and the radial bearing H-3 are ensured to be the same and stable.

For example, for a centrifugal refrigeration compressor, the ventilation holes H-25 can also ensure that the back pressure of the thrust bearing H-4 and the radial bearing H-3 is always equal to the pressure in the motor cavity of the compressor, and the stability of the bearing rotor system can be improved by stabilizing and the same bearing back pressure.

In summary, the bearing support H-2 provided by the disclosure has high structural strength and long service life, adopts double positioning of the spigot and the pin, has high bearing assembly precision, and improves the stability of a bearing rotor system by communicating the inside and the outside of the bearing support H-2 through the vent hole H-25.

Bearing support structure modification II

In connection with fig. 34-37, the present invention provides a bearing support assembly that, in one illustrative embodiment, includes a fixed plate I-51 and a bearing mount I-52. The bearing support I-52 is provided with a through hole I-522 for installing the radial bearing I-8, the fixing plate I-51 is detachably installed at one end of the bearing support I-52 along the axial direction, and the side surface of the fixing plate I-51, which is far away from the bearing support I-52, is used for installing the thrust bearing. The fixing plate I-51 may be mounted to the bearing support I-52 by fasteners.

As shown in FIG. 36, since the through hole I-522 of the bearing support I-52 is used for mounting the radial bearing I-8 and the end face A is used for mounting the fixing plate I-51, the mounting perpendicularity of the fixing plate I-51 with respect to the axis is affected, and thus the perpendicularity of the thrust bearing with respect to the radial bearing is affected. The fixing plate I-51 and the bearing support I-52 in the embodiment adopt split structures, which are beneficial to ensuring the perpendicularity relation between the through hole I-522 and the end face A during processing, and are beneficial to ensuring the coaxiality of the two bearing supports I-52 corresponding to the through hole I-522 when the two radial bearings I-8 are arranged, thereby ensuring the coaxiality of the two radial bearings I-8. Therefore, the assembly precision of the bearing can be improved by ensuring the machining precision, so that the stability of a bearing rotor system is improved, the machining qualification rate of parts can be improved, and the machining cost is reduced.

As shown in FIG. 34, the fixed plate I-51 also serves to limit displacement of the radial bearing I-8 axially toward and away from the bearing support I-52. Therefore, the fixing plate I-51 can be used for mounting the first thrust bearing I-10' and axially limiting the radial bearing I-8, so that the structure of the bearing support assembly is more compact, the parallelism between the mounting surface of the first thrust bearing I-10' and the axial limiting surface of the radial bearing I-8 is guaranteed through the processing parallelism at two sides of the fixing plate I-51, and the mounting precision of the first thrust bearing I-10' and the radial bearing I-8 is improved.

As shown in FIG. 35, one end of the fixing plate I-51 facing the bearing support I-52 is provided with a positioning ring I-511, the bearing support I-52 is provided with an annular first groove I-521, and the positioning ring I-511 is embedded into the first groove I-521 to radially position the fixing plate I-51, and a gap is reserved between the fixing plate I-51 and the main shaft I-1. Moreover, the inner wall I-512 of the positioning ring I-511 is matched with the outer wall of a part of the length section of the radial bearing I-8, and is used for supporting the part of the length section of the radial bearing I-8 and simultaneously playing an axial thrust role on the radial bearing I-8. In order to realize axial thrust, a hole matched with the radial bearing I-8 on the fixed plate I-51 is formed along part of the thickness of the fixed plate I-51, and a thrust platform is reserved at one end far away from the bearing support I-52.

Referring to fig. 35 and 37, the bearing support assembly of the present invention further includes a housing I-6, and the bearing support I-52 has a first end coupled to the fixing plate I-51 and a second end coupled to the housing I-6, and the bearing support I-52 has a sectional profile that gradually increases from the first end to the second end due to the fact that the outer diameter of the thrust bearing is smaller than the inner diameter of the housing I-6.

For weight reduction, as shown in fig. 35, a weight reduction groove I-524 may be further provided on a side of the bearing support I-52 away from the thrust bearing, for example, the weight reduction groove I-524 may be provided in a ring shape, with an inner wall parallel to the axis, and an outer wall in conformity with the contour shape of the bearing support I-52.

The V-shaped bearing support I-52 can improve the overall structural strength of the bearing support I-52 by adopting a structure with gradually changed sectional areas, the stress distribution is uniform everywhere, the bearing capacity can be optimized, the outer side wall is an inclined surface which is easy to realize through casting, and the die draft angle is realized when casting is carried out through a die.

Further, as shown in FIG. 35, the bearing support I-52 is provided with a vent I-526 for conforming the working environment of the radial bearing I-8 to the first thrust bearing I-10', such as conforming the working back pressure and temperature of the radial bearing I-8 to the first thrust bearing I-10'. The motor cavity is internally provided with a refrigerant inlet and outlet for cooling the motor, when the compressor normally operates, the pressure and the temperature of the whole motor cavity are stable, the working environment of the thrust bearing and the radial bearing is the same as that of the motor cavity, namely gas circulation is ensured, the back pressure is relatively stable, and if the back pressure fluctuation is too large, the bearing air film fluctuation can be caused, so that the bearing performance is influenced.

As shown in FIG. 36, the bearing support I-52 is provided with an operation hole I-523 in a radial direction so that a vibration sensor or a temperature sensor is mounted on the outer wall of the radial bearing I-8 through the operation hole I-523 to monitor the operation state of the radial bearing I-8. The radial outer hole section of the operation hole I-523 can be used as a bypass hole, so that the thrust bearing is guaranteed to be the same as the radial bearing I-8 and the motor cavity in pressure and temperature, and the radial inner hole section of the operation hole I-523 plays a role in radiating heat of the radial bearing I-8.

In some embodiments, as shown in connection with fig. 36 and 37, the second end of the bearing support I-52 is provided with a flange I-525 and a spigot I-527 is provided at the outer end of the flange I-525, the bearing support I-52 is mounted in the housing I-6 via the flange I-525 and secured by fasteners, while the bearing support I-52 is positioned radially by means of the spigot I-527 and axially by means of the end of the flange I-525.

The spigot I-527 is used for carrying out first repositioning on connection of the bearing support I-52 and the shell I-6, can carry out preliminary positioning on the installation position relation of the bearing support I-52 and the shell I-6, further, the bearing support assembly further comprises a pin, a pin hole I-528 is arranged on a flange plate I-525 of the bearing support I-52, the pin hole I-528 and the pin hole on the shell I-6 can be penetrated through by the pin, and second repositioning is carried out on connection of the bearing support I-52 and the shell I-6 so as to carry out accurate positioning on the installation position relation of the bearing support I-52 and the shell I-6. The pins may be axially disposed or radially disposed.

By adopting double positioning, the embodiment can accurately ensure the installation precision of the bearing support I-52 in the shell I-6, thereby improving the position precision between the radial bearing I-8 and the thrust bearing.

As shown in fig. 36 and 37, the bearing support I-52 is provided in the housing I-6, and the through hole I-522 of the bearing support I-52 and the end face a for mounting the fixing plate I-51 are configured to be processed to a preset size in a state where the bearing support I-52 and the housing I-6 are assembled as a combined body.

In the embodiment, the bearing is processed in a state of being positioned between the bearing support I-52 and the shell I-6 and forming the combined body, so that the mounting precision of the bearing can be ensured through the processing precision of the combined body, and the perpendicularity between the through hole I-522 and the end face A can be ensured through one-time positioning and clamping.

Further, as shown in FIG. 37, two bearing holders I-52 are provided in the housing I-6 at intervals in the axial direction for supporting two different positions of the spindle I-1, and through holes I-522 of the two bearing holders I-52 are configured to be machined to a preset size in a state where the two bearing holders I-52 are assembled with the housing I-6.

In the embodiment, the two through holes I-522 can be sequentially processed from one side of the assembly by positioning the two bearing supports I-52 and the shell I-6 and processing the two bearing supports in a state of forming the assembly, and the size and the coaxiality of the two through holes I-522 can be ensured by one-time positioning and clamping.

Because each key part on the bearing support I-52 is processed in one positioning and clamping process, the coaxiality of the two through holes I-522 and the perpendicularity of each bearing support I-52 corresponding to the through hole I-522 and the end face A can be improved, so that the coaxiality of the two radial bearings I-8 and the perpendicularity of the thrust bearing are ensured, and the working stability of a rotor system is further improved. Through practical measurement, the coaxiality of the two radial bearings I-8 and the perpendicularity of the radial bearings I-8 and the thrust bearing can be improved to be within 5 micrometers.

The specific manner in which the bearing support assembly is manufactured is described below. During machining, the two bearing supports I-52 are first repositioned through the spigot I-527 to be matched with the shell I-6, then the flange plate I-525 is fixed with the shell I-6 through a fastener, and then dowel fixing is performed. Subsequently, the shell I-6 and the two bearing supports I-52 are used as an integral assembly to be positioned on processing equipment, the end faces A matched with the fixing plates I-51 of the two bearing supports I-52 are processed to ensure the perpendicularity of the thrust bearing and the radial bearing I-8, and then through holes I-522 of the two bearing supports I-52 are sequentially processed from one side to ensure the coaxiality of the two radial bearings I-8.

After the machining is completed, the bearing support I-52 is disassembled, the radial bearing I-8 is installed into the through hole I-522 of the bearing support I-52 in a hot-set mode, and then the fixing plate I-51 is installed at the first end of the bearing support I-52. The bearing support I-52 with the mounting plate I-51 mounted thereon may then be secured to the housing I-6, and the bearing support I-52 may be positioned via the spigot I-527 and the pin location as determined during machining.

If the dynamic pressure gas bearings are adopted for each bearing, the machining precision of the bearing is high, the assembly position precision is required to be extremely high, if the assembly precision is reduced, the bearing performance is reduced, the rotor cannot float up seriously, and if two or more dynamic pressure radial bearings are adopted, the coaxiality of the bearings is required to be in a micron level, and the perpendicularity of all thrust surfaces relative to the center of the rotor is required to be also in a micron level. The method can process the through holes I-522 and the end faces A of the two bearing supports I-52 in one positioning and clamping procedure, and can improve the processing precision and the subsequent assembly precision.

Next, the present invention provides a method for manufacturing a bearing support assembly according to the above embodiments, including, in some embodiments:

Step I-101, assembling a bearing support I-52 and a shell I-6 into a combined body;

i-102, positioning and clamping the combined body on processing equipment, wherein the processing equipment can be a machine tool and the like;

and step I-103, processing the through hole I-522 of the bearing support I-52 and the end face A for installing the fixing plate I-51 to a preset size through one-time positioning and clamping.

In the embodiment, the bearing is processed in a state of being positioned between the bearing support I-52 and the shell I-6 and forming the combined body, the mounting precision of the bearing can be ensured through the processing precision of the combined body, and the unified processing standard can be adopted through one-time positioning and clamping to ensure the processing perpendicularity of the through hole I-522 and the end face A, so that the perpendicularity of the radial bearing I-8 and the thrust bearing is ensured.

In some embodiments, two bearing supports I-52 are arranged in the shell I-6 at intervals along the axial direction, and after the two bearing supports I-52 and the shell I-6 are assembled into a combined body through the step I-101, the processing method further comprises the following steps of:

And I-104, processing through holes I-522 of the two bearing supports I-52 to a preset size through one-time positioning and clamping.

The execution sequence of the steps I-104 and I-103 is not limited, and during actual machining, the two through holes I-522 and the end face A are finished in one positioning and clamping procedure according to the convenience of machining.

In the embodiment, the two bearing supports I-52 and the shell I-6 are positioned and processed in a state of forming the combined body, the mounting precision of the bearing can be ensured through the processing precision of the combined body, a uniform processing standard can be adopted through one-time positioning and clamping, and the size and the coaxiality of the two through holes I-522 can be ensured through one-time positioning and clamping.

In some embodiments, the step I-104 of machining the through holes I-522 of the two bearing supports I-52 to a preset size through one positioning and clamping specifically comprises sequentially machining the through holes I-522 of the two bearing supports I-52 to the preset size from one side of the shell I-6.

The through holes I-522 can be machined in a boring mode, and the machining cutter sequentially machines the two through holes I-522 from one side of the shell I-6 through axial feeding, so that the machining efficiency can be improved, and the coaxiality of the two through holes I-522 is further improved.

In some embodiments, the end of the bearing support I-52 connected with the shell I-6 is provided with a spigot I-527, and the step of assembling the bearing support I-52 and the shell I-6 into a combined body in the step of I-101 specifically comprises the following steps:

I-101A, carrying out first repositioning on the bearing support I-52 and the shell I-6 through the spigot I-527 in a matching way;

Step I-101B, fixing the bearing support I-52 and the shell I-6 through a fastener;

and I-101C, after the flange plate is fixed with the shell I-6, pinning for second repositioning.

In this embodiment, steps I-101 through I-103 are sequentially performed.

After preliminary positioning through the spigot I-527, the position relation between the bearing support I-52 and the shell I-6 is restrained by a fastener, on the basis of the original pin hole I-528, the pin holes are matched on the bearing support I-52 and the shell I-6, the pin is inserted into the pin holes, the bearing support I-52 and the shell I-6 are prevented from being subjected to larger cutting force in the machining process by the pin, and accurate positioning can be provided for the subsequent product assembling process. By adopting double positioning, the mounting precision of the bearing support I-52 in the shell I-6 can be accurately ensured, so that the position precision between the radial bearing I-8 and the thrust bearing is improved.

Further, after the processing is completed, the processing method further comprises:

step I-105, disassembling the assembly formed by assembling the bearing support I-52 and the shell I-6, so as to assemble the radial bearing I-8 in a state that the bearing support I-52 is separated from the shell I-6.

After the machining is completed, the bearing support I-52 is disassembled, the radial bearing I-8 is installed into the through hole I-522 of the bearing support I-52 in a hot-set mode, and then the fixing plate I-51 is installed at the first end of the bearing support I-52. The bearing support I-52 can be fixedly mounted on the housing I-6 by means of pin positions determined during machining. The bearing support I-52 ensures the assembly precision of the bearing through a double positioning mode of the spigot I-527 and the pin, and improves the stability of a bearing rotor system.

Finally, the invention also provides a compressor comprising the bearing support assembly of the embodiment. For example, the compressor is a centrifugal compressor. Alternatively, the compressor may be a centrifugal refrigeration compressor or a screw refrigeration compressor or the like.

The working principle of the centrifugal compressor is that a main shaft I-1 rotates at a high speed in the working process of the compressor, gas is accelerated by a left impeller I-2 and then enters a diffuser I-3, the gas is subjected to primary compression and pressurization by the diffuser I-3 and then enters a first volute, a gas exhaust channel on the first volute guides compressed gas into a right impeller I-2, the compressed gas enters the right diffuser I-3 after the centrifugal action of the right impeller I-2, and the gas enters a second volute after secondary compression and is discharged out of the compressor through a gas exhaust channel on the second volute.

As shown in FIG. 34, the centrifugal compressor of the present invention further includes a main shaft I-1, a diffuser I-3, a thrust disk I-4, and a second thrust bearing I-10, the thrust disk I-4 being configured to be rotatable with the main shaft I-1 and axially located between the diffuser I-3 and a fixed plate I-51. The first thrust bearing I-10' is arranged at one end of the fixed plate I-51 far away from the bearing support I-52, and the second thrust bearing I-10 is arranged at one end of the diffuser I-3 far away from the diffusion surface. Specifically, the thrust disc I-4 is provided with a thrust part I-41, and the left and right surfaces of the thrust part I-41 and thrust bearings on two sides form a working surface which can bear bidirectional axial force, so that the running stability and reliability of the compressor in full working condition running and reversing are ensured.

Further, the thrust disc I-4 may further include a connection portion I-42, where the thrust disc I-4 is connected to the thrust portion I-41 and sleeved on the spindle I-1, and a through hole is formed at the bottom of the second groove I-31, and the connection portion I-42 is embedded in the through hole. The connection portion I-42 may be an interference fit with the spindle I-1 such that the thrust disc I-4 may rotate with the spindle I-1. The diffuser I-3 and the fixing plate I-51 are fixedly arranged, and a gap is reserved between the diffuser I-3 and the main shaft I-1. For example, thrust disc I-4 may be a cylindrical stepped structure.

For example, the first thrust bearing I-10', the second thrust bearing I-10 and/or the radial bearing I-8 may be a hydrostatic or hydrodynamic gas thrust bearing, or may also be a magnetic levitation bearing.

Taking fig. 34 as an example, because a gap is formed between the thrust bearing and the thrust disc I-4, gas can form a gas film with pressure in the gap to play a role in thrust and lubrication, and because the thrust bearing is arranged in the cavity of the compressor, the gas can enter the cavity environment, and during the rotation process of the rotor, the gas can be brought into the gap to form the dynamic pressure gas thrust bearing.

In the centrifugal compressor of the embodiment, the thrust disc can be matched with thrust bearings on two sides, and can bear axial forces in left and right directions, so that the stability of the compressor in the process of full-working-condition operation and anti-operation is ensured. The compressor operation condition refers to the evaporation temperature and the condensation temperature of the system where the compressor is located, and the full condition refers to the operation of the compressor in a certain evaporation temperature range and a certain condensation temperature range, and when the compressor is stopped, the reverse rotation condition after stopping can occur due to the fact that the exhaust pressure is higher than Yu Xiqi.

Further, the thrust disk I-4 has a gap between both sides thereof and the first thrust bearing I-10' and the second thrust bearing I-10, and the gap between both sides is defined by the diffuser I-3 abutting against the fixed plate I-51.

The fixing plate I-51 and the diffuser I-3 are mutually abutted to carry out combined limiting, so that the position of the thrust disc I-4 and the gap between the thrust disc I-4 and thrust bearings on two sides are limited, the gap between the thrust bearings can be accurately ensured, the assembly difficulty is reduced, the assembly efficiency and the assembly precision are improved, the working performance of the thrust bearings is ensured, and the running stability of the compressor is improved.

Further, still referring to fig. 34, a second groove I-31 is provided at an end of the diffuser I-3 remote from the diffuser surface, a first thrust bearing I-10' is provided at the bottom of the second groove I-52 in the axial direction, a fixing plate I-51 is fixed to the diffuser I-3, and a thrust portion I-41 of the thrust disc I-4 is located in the second groove I-31.

Since the bearing support I-52 needs to be fixed to the housing I-6 of the compressor, it is fixed in position, thereby axially positioning the fixing plate I-51. The diffuser I-3 is also fixed on the shell I-6, and the diffuser I-3 and the fixing plate I-51 are abutted against each other, so that the clearance between the thrust bearings at two sides can be accurately ensured through the axial depth of the second groove I-31, the assembly precision can be improved, the assembly difficulty can be reduced, the assembly efficiency can be improved, the performance of the thrust bearings can be ensured, the performance reduction and even failure of the thrust bearings caused by inaccurate clearance control can be prevented, and the operation stability of the compressor can be improved.

As shown in fig. 34, the depth of the second groove I-31 includes the thickness of the thrust portion I-41, the thickness of the both side thrust bearings, and the gap of the both side thrust bearings, and thus, in order to secure the gap of the both side thrust bearings, the gap can be controlled by increasing the depth of the second groove I-31, the thickness of the thrust portion I-41, and the thickness of the both side thrust bearings. The design depth and the tolerance range of the second groove I-31 are reversely pushed according to the clearance range, the thrust part I-41 thickness tolerance range and the thrust bearing thickness tolerance range which are required to be achieved by the thrust bearing. Therefore, the thrust bearing clearance can be ensured by improving the machining precision of the depth of the second groove I-31, the assembly precision can be improved, the assembly difficulty is reduced, and the assembly efficiency is improved.

In some embodiments, the first thrust bearing I-10' is directly secured to the bottom of the second groove I-31. The diffuser I-3 and the thrust bearing fixing plate are integrated into one part, the bottom of the second groove I-31 can be used as the fixing plate in the second thrust bearing I-10, and the axial size of the bearing supporting assembly can be further reduced without additionally arranging the thrust bearing fixing plate, so that the structure is more compact.

In a specific construction, referring to FIG. 34, a first thrust bearing I-10' is secured to a retainer plate I-51 by fasteners, a second thrust bearing I-10 is secured to a diffuser I-3 by fasteners, the retainer plate I-51 is secured to the diffuser I-3 by fasteners, and a locating spigot is provided on the outer periphery of the diffuser I-3 for locating engagement with a housing I-6.

Bearing support structure modification III

Referring to fig. 38 to 40, an embodiment of the present invention provides a compressor including a bearing housing J-1, a radial bearing J-2, a main shaft J-4, and a thrust bearing J-3. The bearing support J-1 includes a first through hole J-11, and the radial bearing J-2 is mounted in the first through hole J-11. The main shaft J-4 is simultaneously arranged on the radial bearing J-2 and the thrust bearing J-3, and the thrust bearing J-3 is abutted against the side surface of the bearing support J-1.

The side surface of one side of the bearing support J-1 is used as a mounting surface J-17 of the thrust bearing J-3, so that the mounting and positioning of the thrust bearing J-3 are realized. Radial bearing J-2 is also mounted directly to bearing support J-1. The bearing support J-1 serves to position the thrust bearing J-3 and the radial bearing J-2 at the same time. The perpendicularity of the mounting face J-17 is more easily ensured at the time of the part processing.

In some embodiments, thrust bearing J-3 has no support, and thrust bearing J-3 is lamellar. One side of the thrust bearing J-3 directly abuts against the side of the bearing support J-1, and the other side directly abuts against the thrust disk J-6. No other load bearing, locating or mounting structure is provided between the thrust bearing J-3 and the mounting face J-17. The radial bearing J-2 comprises a base body and a supporting body fixed with the inner wall of a through hole of the base body, wherein the supporting body is a cylindrical sheet. The base body is used for realizing the installation of the radial bearing J-2.

Because the radial force of the rotary machine is basically equal to the gravity of the rotor, the radial load is relatively small, the radial strength requirement of the bearing support J-1 is not high, and the bearing support J-1 is easier to meet the radial strength requirement. And the axial load is larger than the radial load, and the axial load is transmitted to the bearing support J-1 through the thrust bearing J-3.

According to the technical scheme, the bearing support J-1 integrates two functions, namely, a supporting function on the radial bearing J-2 and a positioning and fixing function on the thrust bearing J-3. The machining precision of the bearing support J-1 is achieved, and the requirement on micron-scale verticality is met when the thrust bearing J-3 is installed. In addition, the radial bearing J-2 and the thrust bearing J-3 are positioned at the same time by the bearing support J-1, and the thickness occupied by the thrust bearing fixing plate is reduced because the thrust bearing fixing plate is not required to be arranged. Further, two radial bearings J-2 support the main shaft J-4, and the thrust bearing J-3 is used for bearing axial force and axially positioning the main shaft J-4. The above structure also shortens the length of the main shaft J-4, and the whole compressor is reduced in size and weight.

Referring to fig. 38, a positioning step surface J-12 is provided in the first through hole J-11, and an end surface of the radial bearing J-2 abuts against the positioning step surface J-12.

Referring to fig. 38 and 39, the bearing support J-1 is in interference fit with the radial bearing J-2, and the radial bearing J-2 is axially limited by the positioning step surface J-12. The positioning step surface J-12 is specifically a step surface, one end of the radial bearing J-2 is propped against the positioning step surface J-12, positioning of the radial bearing J-2 on the bearing support J-1 is realized, other positioning components are not required, the system structure is simplified, and the compressor structure is more compact.

Referring to fig. 38 and 40, in some embodiments, a thrust disc J-6 is mounted to a side of thrust bearing J-3 facing away from bearing support J-1. The thrust bearing J-3 is in direct contact with the thrust disc J-6.

Referring to fig. 38, in some embodiments, the bearing support J-1 is provided with a second through hole J-13, and the second through hole J-13 is used to communicate the cavity J-18 where the thrust bearing J-3 is located with the first through hole J-11 where the radial bearing J-2 is located, so that the radial bearing J-2 and the thrust bearing J-3 have the same working environment.

The working environment refers to temperature and pressure, in particular such that the working environment of the thrust bearing J-3 and the radial bearing J-2 is identical to the motor cavity.

The central axis of the second through hole J-13 is perpendicular to the central axis of the first through hole J-11 or forms an included angle. The second through hole J-13 is, for example, a plurality of holes having different diameters.

In some embodiments, the number of second through holes J-13 is 2-14. Such as 2, 4, 8, 12.

According to the technical scheme, 2 to 12 second through holes J-13 communicated with the left and right channels are uniformly arranged on the bearing support J-1, so that the radial bearing J-2 and the thrust bearing J-3 have the same working environment. The motor cavity is provided with a cooling motor, the refrigerant flows in and out, when the compressor runs normally, the pressure and the temperature of the whole motor cavity are stable, the working environments of the thrust bearing J-3 and the radial bearing J-2 are the same as those of the motor cavity, namely, the gas circulation is ensured, the back pressure is relatively stable, the fluctuation of a bearing gas film is reduced, and the bearing performance is optimized.

Referring to fig. 40 and 41, in some embodiments, the second through holes J-13 are uniformly disposed with respect to the circumferential direction of the bearing support J-1.

Referring to fig. 40 and 41, in some embodiments, the outer edge dimension of the side of bearing support J-1 facing thrust bearing J-3 is smaller than the outer edge dimension of the side of bearing support J-1 facing away from thrust bearing J-3. Taking the direction shown in fig. 40 as an example, the outer edge of the bearing support J-1 on the right side has a large size and the outer edge on the left side has a small size. This structure makes the bearing support J-1 easy to install in the compressor.

Referring to fig. 40 and 41, in some embodiments, the outer edge of the bearing support J-1 is substantially gradually changed in size, and an annular boss is provided at the wide mouth end of the bearing support J-1, and the boss is provided with a mounting hole J-15, through which the bearing support J-1 is positioned when mounted on the cylinder J-5. The mounting hole J-15 is, for example, a pin hole.

Above-mentioned technical scheme adopts integration bearing support, and structural strength is high, and is convenient for cast. The bearing support J-1 adopts a V-shaped structure, so that the transmission of axial force to the motor cylinder J-5 is effectively realized, and the strength and the service life of the bearing support J-1 are improved;

referring to FIG. 40, in some embodiments, bearing support J-1 is provided with a spigot J-14 for positioning with compressor barrel J-5.

Specifically, on the side of the boss away from the bearing support J-1, the bearing support J-1 is further provided with a spigot J-14, and positioning of the bearing support J-1 relative to the compressor cylinder J-5 is achieved through the spigot J-14.

In the technical scheme, the bearing support J-1 adopts the double positioning of the mounting hole J-15 and the spigot J-14, the coaxiality of the assembled bearing is ensured by the spigot J-14, and then the pin penetrates through the mounting hole J-15 for accurate positioning. The structure meets the requirement that two radial bearings J-2 at two ends of the main shaft J-4 reach the coaxiality of micron level, so that the radial bearings J-2 have reliable performance, and the rotor works normally.

In some embodiments, bearing support J-1 is provided with a lightening hole J-16 to achieve a lightweight compressor.

The shape of the lightening hole J-16 matches the shape of the bearing support J-1, the lightening hole J-16 is annular, and the contour lines of the lightening hole J-16 located on each side of the central axis of the bearing support J-1 are also approximately horn-shaped in a cross-sectional view. The weight-reducing holes J-16 of the above construction make the wall thickness of the bearing support J-1 substantially uniform. The middle of the bearing support J-1 is hollowed into a V shape, so that the wall thickness of the casting is relatively uniform, the dead weight of the support is reduced, and casting molding is facilitated.

Diffuser structural variation

Referring to fig. 42-45, in some embodiments, the present disclosure provides a compressor including an impeller K-1, a thrust bearing K-2, and a diffuser K-3. One side surface K-31 of the diffuser K-3 is abutted against the impeller K-1, the other side is provided with an axial concave part K-32, and the bottom surface of the axial concave part K-32 is abutted against the thrust bearing K-2. The other side of the thrust bearing K-2 is provided with a thrust disk K-7.

The diffuser K-3 integrates the function of a thrust bearing fixing plate, and the bottom surface of the axial concave part K-32 of the diffuser K-3 directly abuts against the thrust bearing K-2 to play a role in positioning the thrust bearing K-2. The thrust bearing K-2 is directly locked by a screw and bears the axial force of the rotor. The bottom surface of the axial concave part K-32 of the diffuser K-3 is used as a fixing surface of the thrust bearing K-2, and the verticality precision of the fixing surface is high, so that the air film of the matching surface of the thrust disc K-7 and the thrust bearing K-2 is uniform, the thrust bearing K-2 is uniformly stressed, the abrasion of the thrust bearing K-2 is slowed down, and the service life of the thrust bearing K-2 is prolonged.

According to the compressor provided by the technical scheme, due to the adoption of the diffuser K-3 with the structure, the number of parts is reduced, the quality control is improved, and the thickness of the thrust bearing fixing plate is reduced under the condition of meeting the functional requirement, so that the length of the rotor is reduced, the rigidity of the rotor is improved, the critical rotating speed of the bending mode of the bearing rotor system is improved, the weight of the rotor is reduced, the bearing load is lightened, and the stability of the bearing rotor system is improved.

In some embodiments, the inner wall of the through hole of the diffuser K-3 is provided with a seal K-4.

The diffuser K-3 converts the speed energy of the outlet medium of the impeller K-1 into pressure energy, the inner wall of the through hole of the diffuser K-3 is provided with a sealing piece K-4, and the sealing piece K-4 is matched with the rotor to form a shaft seal so as to prevent the exhaust of the impeller K-1 from entering the motor cavity.

In some embodiments, seal K-4 includes sealing comb teeth.

In some embodiments, the diffuser K-3 is integral with the seal K-4. The structure integrates the sealing element K-4, the thrust bearing fixing plate and the existing diffuser into one part, has high integration degree, reduces the number of parts, improves the quality control, reduces the length of the part under the condition of meeting the functional requirement, thereby reducing the length of the rotor, improving the rigidity of the rotor, improving the critical rotation speed of the bending mode of the bearing rotor system, reducing the weight of the rotor, lightening the bearing load, and jointly improving the stability of the bearing rotor system.

In some embodiments, the compressor further includes a bowl K-5, the bowl K-5 being coupled to the diffuser K-3 and positioned by a positioning spigot K-33 of the diffuser K-3.

During assembly, the thrust bearing K-2 is fixed on the diffuser K-3 through a screw, then the diffuser K-3 is positioned on the motor cylinder K-5 through a spigot, and then the positioning is accurately performed through a pin. The structure realizes the accurate positioning and assembly of the diffuser and the cylinder K-5.

The coaxiality of the diffuser K-3 shaft seal part and the perpendicularity of the thrust bearing K-2 fixing surface are guaranteed on one part, so that the machining and assembling difficulty is reduced, and meanwhile, the machining and assembling accumulated dimensional tolerance and shape and position errors are greatly reduced.

In addition, one part has more parts, and only one assembly reference is used, so that the assembly precision and the assembly efficiency are improved. Because the coaxiality precision of the comb teeth seal is high, the probability of abrasion in the working process of the comb teeth seal and the rotor is reduced, the phenomenon of increasing the sealing gap is reduced, the leakage loss is reduced, and the compressor energy efficiency is improved.

In some embodiments, the diffuser K-3 is cast. The diffuser K-3 and the sealing piece K-4 are integrally cast and formed, so that the production efficiency is improved.

In some embodiments, the through hole of the diffuser K-3 is provided with a main shaft K-6, and the diffuser K-3 is made of a material softer than the main shaft K-6.

During operation, when wear occurs, the diffuser K-3 is worn and the main shaft K-6 is not or less worn. The structure plays a role in protecting the main shaft K-6.

In some embodiments, the thickness of the diffuser K-3 is less than 14mm. The thickness of the diffuser K-3 is obviously reduced compared with the total thickness of the thrust bearing fixing plate of the existing diffuser K-3, and the weight reduction of the compressor is realized.

Diffuser, thrust disc and related mating structure modification example one

Referring to fig. 46, in some embodiments, the present disclosure provides a centrifugal compressor. In order to make the improvement point of the present invention more clearly understood by those skilled in the art, the overall structure of the centrifugal compressor will be described with reference to fig. 46.

As shown in FIG. 46, taking a two-stage centrifugal compressor as an example, the two-stage centrifugal compressor comprises a first volute L-61, a second volute L-63 and a middle housing L-62, wherein the first volute L-61 and the second volute L-63 are respectively arranged at two ends of the middle housing L-62 along the axial direction to jointly form a compressor housing L-6. The main shaft L-1 is arranged at the center of the compressor shell, two ends of the main shaft L-1 are respectively provided with an impeller L-2, the inner end of the impeller L-2 is provided with a diffuser L-3, when the impeller L-2 rotates at a high speed, gas is rotated along with the rotation, and is thrown into the rear diffuser L-3 to be diffused under the action of centrifugal force, so that the speed energy of an outlet medium of the impeller L-2 is converted into pressure energy, and the gas with the increased pressure is discharged from the volute.

In order to support the main shaft L-1, radial bearings L-8 are respectively arranged at two ends of the main shaft L-1, the radial bearings L-8 are supported by bearing supports L-52, and the bearing supports L-52 are connected to the middle shell L-62. A stator assembly L-7 is arranged between the main shaft L-1 and the middle shell L-62. Because the impeller L-2 generates axial force in the working process, a thrust bearing is arranged at one end of the main shaft L-1 to balance the axial force generated by the impeller L-2.

The working principle of the compressor is that a main shaft L-1 rotates at a high speed in the working process of the compressor, gas enters a diffuser L-3 through a left impeller L-2, the gas enters a first volute L-61 after being compressed at one stage, a gas exhaust channel on the first volute L-61 guides compressed gas into a right impeller L-2, the compressed gas enters the right diffuser L-3 after being centrifuged by the right impeller L-2, the gas enters a second volute L-63 after being compressed at two stages, and the gas is discharged out of the compressor through a gas exhaust channel on the second volute L-63.

The bearing support assembly in a centrifugal compressor, which in some embodiments includes a main shaft L-1, an impeller L-2, a diffuser L-3, a thrust disc L-4, and a support assembly L-5, as shown in FIG. 47, will be described in detail.

The middle of the main shaft L-1 can be provided with magnetic steel L-13, the diffuser L-3 is fixed on the shell L-6, one end of the diffuser L-3, which is far away from the diffuser surface, is provided with a first thrust bearing L-10, and the diffuser surface is an end surface close to the impeller L-2. The supporting component L-5 is arranged at one end of the diffuser L-3 far away from the diffusion surface, one end of the supporting component L-5 is fixed with the shell L-6 of the compressor, the other end of the supporting component is propped against the end surface of the diffuser L-3, and a second thrust bearing L-10' is arranged at one side of the supporting component L-5 facing the diffuser L-3. The thrust plate L-4 is configured to be rotatable with the main shaft L-1, the thrust plate L-4 has a thrust portion L-41, for example, in a disk-like structure, and a gap between both sides of the thrust portion L-41 and the first thrust bearing L-10 and the second thrust bearing L-10' is defined by the diffuser L-3 abutting against the support assembly L-5. The left and right surfaces of the thrust part L-41 and the thrust bearings on the two sides form working surfaces, which can bear bidirectional axial force and ensure the running stability and reliability of the compressor during full-working-condition running and reversing.

For example, the first thrust bearing L-10 and the second thrust bearing L-10' may be hydrostatic or hydrodynamic gas thrust bearings, or may be magnetic bearings.

Taking fig. 47 as an example, because a gap is formed between the thrust bearing and the thrust disc L-4, gas can form a gas film with pressure in the gap to play a role in thrust and lubrication, and because the thrust bearing is arranged in the cavity of the compressor, the gas can enter the cavity environment, and during the rotation process of the rotor, the gas can be brought into the gap to form the dynamic pressure gas thrust bearing.

Moreover, since the diffuser L-3 and the supporting component L-5 are fixed on the shell L-6 of the compressor, the self-position is fixed, the supporting component L-5 and the diffuser L-3 are mutually abutted to be combined and limited, and the position of the thrust disc L-4 and the gap between the supporting component L-5 and the thrust bearings on two sides are limited, so that the gap between the thrust bearings can be accurately ensured, the assembly difficulty is reduced, the assembly efficiency and the assembly precision are improved, the working performance of the thrust bearings is ensured, and the running stability of the compressor is improved.

As shown in FIG. 47, a first groove L-31 is formed at one end of the diffuser L-3, which is far away from the diffuser surface, a first thrust bearing L-10 is arranged at the bottom of the first groove L-31 along the axial direction, a thrust part L-41 is positioned in the first groove L-31, and gaps are formed between two sides of the thrust part L-41 and the first thrust bearing L-10 and the second thrust bearing L-10'.

Because diffuser L-3 and supporting component L-5 support each other, can guarantee the clearance of both sides thrust bearing through the axial degree of depth of first recess L-31 accurately, can improve the assembly precision to reduce the assembly degree of difficulty, improve assembly efficiency, can also guarantee thrust bearing's performance simultaneously, prevent that the clearance control inaccuracy from causing thrust bearing performance to reduce even inefficacy, thereby improve compressor's operating stability.

As shown in FIG. 47, the depth of the first groove L-31 includes the thickness of the thrust portion L-41, the thickness of the both side thrust bearings and the gap of the both side thrust bearings, and thus, in order to secure the gap of the both side thrust bearings, the gap can be controlled by increasing the depth of the first groove L-31, the thickness of the thrust portion L-41 and the thickness of the both side thrust bearings. The design depth and the tolerance range of the first groove L-31 are reversely pushed according to the clearance range, the thickness tolerance range of the thrust part L-41 and the thickness tolerance range of the thrust bearing which are required to be achieved by the thrust bearing. Therefore, the thrust bearing clearance can be ensured by improving the machining precision of the depth of the first groove L-31, the assembly precision can be improved, the assembly difficulty is reduced, and the assembly efficiency is improved.

In some embodiments, as shown in FIGS. 47 and 48, the centrifugal compressor further includes a housing L-6 and radial bearings L-8 for carrying the radial forces of the rotor, primarily from the weight of the rotor itself. For example, the radial bearing L-8 may be a hydrostatic or hydrodynamic gas radial bearing, or may be a magnetic bearing.

The support assembly L-5 includes a fixed plate L-51 and a bearing support L-52. The fixed plate L-51 is abutted against the diffuser L-3, the second thrust bearing L-10' is arranged on one side of the fixed plate L-51, which faces the diffuser L-3, the bearing support L-52 is arranged on one side of the fixed plate L-51, which is far away from the diffuser L-3, and the first end of the bearing support L-52 is connected with the fixed plate L-51, and the second end of the bearing support L-52 is connected with the shell L-6 and used for supporting the main shaft L-1 through the radial bearing L-8.

The support assembly L-5 in the embodiment adopts a split structure, the second thrust bearing L-10' is installed through the fixing plate L-51, the radial bearing L-8 is installed on the bearing support L-52, the accuracy of the radial bearings L-8 at the two ends of the main shaft L-1 and the installation position of the thrust bearings are improved, the coaxiality of the two radial bearings L-8 and the verticality of the thrust bearings are included, and the working stability of a rotor system can be improved.

Specifically, as shown in fig. 50, this can be achieved as follows. The second end of the bearing support L-52 is provided with a flange L-52L-5, the outer end of the flange L-52L-5 is provided with a spigot L-52L-7, the bearing support L-52 is arranged in the middle shell L-62 through the flange L-52L-5 and is fixed through a fastener, and meanwhile, the bearing support L-52 is radially positioned by means of the spigot L-52L-7.

During machining, the two bearing supports L-52 are first repositioned through the spigot L-52L-7 to be matched with the middle shell L-62, then the flange L-52L-5 is fixed with the middle shell L-62 through a fastener, and then the flange L-52L-5 is pinned and fixed. Then, the middle shell L-62 and the two bearing supports L-52 are used as an integral assembly to be positioned on processing equipment, the end faces of the two bearing supports L-52 matched with the fixing plate L-51 are processed to ensure the perpendicularity of the thrust bearing and the radial bearing L-8, and then the mounting holes L-52 of the two bearing supports L-52 are processed sequentially from one side to ensure the coaxiality of the two radial bearings L-8.

After the machining is completed, the bearing support L-52 is disassembled, the radial bearing L-8 is installed in the installation hole L-52 of the bearing support L-52 in a hot-set mode, and then the fixing plate L-51 is installed at the first end of the bearing support L-52. The bearing support L-52 may be fixedly mounted to the housing L-6 by pin positions determined during machining.

Because each key positioning part is processed in one clamping process, the coaxiality of the two radial bearings L-8 and the verticality of the thrust bearing can be ensured, and therefore, the working stability of the rotor system is improved.

As shown in FIG. 48, the fixing plate L-51 is further used for limiting the radial bearing L-8 to move towards one side of the diffuser L-3 along the axial direction, so that the fixing plate L-51 can be used for mounting the second thrust bearing L-10 'and limiting the radial bearing L-8 along the axial direction, the structure of the bearing support assembly can be more compact, the parallelism between the mounting surface of the second thrust bearing L-10' and the axial limiting surface of the radial bearing L-8 can be guaranteed through the processing parallelism on two sides of the fixing plate L-51, and the mounting precision of the thrust bearing and the radial bearing L-8 can be improved.

Further, one end of the fixing plate L-51 facing the bearing support L-52 is provided with a locating ring L-51, the bearing support L-52 is provided with a second annular groove L-52, and the locating ring L-51 is embedded into the second groove L-52 to radially locate the fixing plate L-51, and a gap is reserved between the fixing plate L-51 and the main shaft L-1. Moreover, the inner wall of the positioning ring L-51 is matched with the outer wall of a part of the length section of the radial bearing L-8, and is used for supporting the part of the length section of the radial bearing L-8 and simultaneously playing a role in axially thrust the radial bearing L-8.

In a specific construction, as shown in FIG. 47, a first thrust bearing L-10 is secured to a diffuser L-3 by a fastener L-32, a second thrust bearing L-10' is secured to a securing plate L-51 by a fastener L-32, the securing plate L-51 and the diffuser L-3 are abutted against each other, and a positioning spigot L-33 is provided on the outer periphery of the diffuser L-3 for positioning and mounting with a housing L-6.

In some embodiments, as shown in FIG. 49, the securing plate L-51 forms a unitary structure with the bearing support L-52. The support component L-5 adopts an integrated structure, so that the structure can be simplified, the assembly difficulty is reduced, and the perpendicularity of the radial bearing L-8 and the thrust bearing is easily ensured through the machining precision of the support component L-5.

In some embodiments, not shown in the figures, the centrifugal compressor further comprises a casing L-6 and a radial bearing L-8, wherein the bearing assembly L-5 comprises a bearing support L-52, a first end of the bearing support L-52 being abutted against the diffuser L-3, a second end being connected to the casing L-6, a second thrust bearing L-10' being provided on the side of the bearing support L-52 facing the diffuser L-3, the bearing support L-52 further serving to support the main shaft L-1 via the radial bearing L-8. The bearing support L-52 reserves a thrust platform when the mounting hole L-52 is machined so as to axially limit the radial bearing L-8.

Compared with the embodiment shown in fig. 49, the axial dimension of the bearing support assembly can be further reduced by omitting the fixing plate L-51, the structure can be simplified, the assembly difficulty can be reduced, and the perpendicularity of the radial bearing L-8 and the thrust bearing can be easily ensured through the machining precision of the support assembly L-5.

As shown in FIGS. 48 and 49, the centrifugal compressor further includes a housing L-6 and a radial bearing L-8, and the bearing assembly L-5 includes a bearing support L-52, the bearing support L-52 having a first end abutting against the diffuser L-3 and a second end coupled to the housing L-6 for supporting the main shaft L-1 via the radial bearing L-8. Since the outer diameter of the thrust bearing is smaller than the inner diameter of the housing L-6, the bearing support L-52 correspondingly increases in cross-sectional profile from the first end to the second end. For weight reduction, as shown in FIG. 50, a weight reduction groove L-52L-4 may be provided on a side of the bearing support L-52 away from the thrust bearing, for example, the weight reduction groove L-52L-4 may be provided in a ring shape, with an inner wall parallel to the axis, and an outer wall conforming to the contour shape of the bearing support L-52.

The V-shaped bearing support L-52 can improve the overall structural strength of the bearing support L-52 by adopting a structure with gradually changed sectional areas, the stress distribution is uniform everywhere, the bearing capacity can be optimized, the outer side wall is an inclined surface which is easy to realize through casting, and the die draft angle is realized when casting is carried out through a die.

Further, as shown in FIG. 50, the bearing support L-52 is provided with a vent hole L-52L-6 for conforming the working environment of the radial bearing L-8 to the first thrust bearing L-10 and the second thrust bearing L-10', for example, for conforming the working back pressure of the radial bearing L-8 to the first thrust bearing L-10 and the second thrust bearing L-10'. The motor cavity is internally provided with a refrigerant inlet and outlet for cooling the motor, when the compressor normally operates, the pressure and the temperature of the whole motor cavity are stable, the working environment of the thrust bearing and the radial bearing is the same as that of the motor cavity, namely gas circulation is ensured, the back pressure is relatively stable, and if the back pressure fluctuation is too large, the bearing air film fluctuation can be caused, so that the bearing performance is influenced.

As shown in FIG. 48, the bearing support L-52 is provided with an operation hole L-52 in a radial direction so that a vibration sensor or a temperature sensor is mounted on the outer wall of the radial bearing L-8 through the operation hole L-52 to monitor the operation state of the radial bearing L-8. The radial outer hole section of the operation hole L-52 can be used as a bypass hole, so that the thrust bearing is guaranteed to be the same as the radial bearing L-8 and the motor cavity in pressure and temperature, and the radial inner hole section of the operation hole L-52 plays a role in radiating heat for the radial bearing L-8.

In some embodiments, as shown in FIG. 48, the first thrust bearing L-10 is directly secured to the bottom of the first groove L-31 of the diffuser L-3. For example, the first thrust bearing L-10 adopts a dynamic pressure thrust bearing which is a thin plate structure and can be directly fixed at the bottom of the first groove L-31. The diffuser L-3 and the thrust bearing fixing plate are integrated into one part, the bottom of the first groove L-31 can be used as the fixing plate of the first thrust bearing L-10, and the axial size of the bearing supporting assembly can be further reduced without arranging the thrust bearing fixing plate additionally, so that the structure is more compact.

In some embodiments, as shown in FIG. 46, the centrifugal compressor further includes an impeller L-2 and a locking member L-9, a cavity L-11 is provided in the main shaft L-1 and a shaft core L-12 is provided at the center, an end of the shaft core L-12 extends out of an end of the main shaft L-1, the impeller L-2 is sleeved on an outer end of the shaft core L-12, the impeller L-2 is locked on the shaft core L-12 by the locking member L-9, and the impeller L-2 is positioned outside the diffuser L-3.

The embodiment enables the impeller L-2 to be detachably arranged relative to the main shaft L-1, can reduce the difficulty of disassembling and assembling the impeller, simplifies the assembly process and required equipment of the impeller, and improves the assembly efficiency and the operability of disassembling and inspection work and maintenance. Moreover, the installation mode can prevent the main shaft or the impeller from deforming, also can ensure the installation strength of the impeller, and avoid stress concentration, thereby improving the compression capacity of the compressor. In addition, by arranging the cavity on the main shaft, the weight of the main shaft can be reduced, so that the critical rotation speed of the rotor is improved, and the limit working capacity of the compressor is further improved.

Still referring to FIG. 46, the shaft core L-12 is directly formed during the processing of the cavity L-11, so that the shaft core L-12 and the rest of the main shaft L-1 are integrally processed, the shaft core L-12 is not required to be additionally installed in the cavity of the main shaft L-1, the assembly difficulty can be further reduced, the connection strength between the shaft core L-12 and the main shaft L-1 is increased, the position accuracy of the shaft core L-12 can be ensured, the jumping problem of the front end of a rotor is effectively solved, the length of a cantilever end is reduced, and the working stability and reliability of the compressor are improved. For example, the cavity L-11 may be a ring groove, or a plurality of holes that are centrally symmetrical about an axis.

As shown in FIG. 48, the thrust disk L-4 further comprises a connecting part L-42, the thrust disk L-4 is connected with the thrust part L-41 and sleeved on the main shaft L-1, a through hole L-34 is arranged at the bottom of the first groove L-31, and the connecting part L-42 is embedded into the through hole L-34. The connection portion L-42 may be an interference fit with the main shaft L-1 such that the thrust disc L-4 may rotate with the main shaft L-1. The diffuser L-3 and the fixing plate L-51 are fixedly arranged, and a gap is reserved between the diffuser L-3 and the main shaft L-1. For example, thrust disc L-4 may be a cylindrical stepped structure.

As shown in FIG. 51, the centrifugal compressor further comprises an impeller L-2 arranged at the end part of the main shaft L-1, the impeller L-2 is positioned at the outer side of the diffuser L-3, a first axial comb tooth sealing structure L-35 is arranged on the side wall of the through hole L-34, and a shaft seal is formed between the impeller L-2 and the thrust disc L-4, so that the phenomenon that refrigerant enters a motor cavity along with the exhaust of the impeller through a gap between the diffuser L-3 and the thrust disc L-4 can be reduced. And/or the end of the impeller L-2 facing the diffuser L-3 is provided with a radial comb tooth sealing structure L-21, so that the refrigerant can be reduced from flowing to the periphery along the gap between the impeller L-2 and the diffuser L-3. And/or the impeller L-2 has an embedded portion L-22 embedded in the diffuser L-3, for example, the embedded portion L-22 may be an elongated strip-like structure extending in the axial direction, and a second axial comb-tooth sealing structure L-23 is provided on the embedded portion L-22 radially inward in the longitudinal direction so as to reduce the flow of refrigerant to the outer periphery along the gap between the impeller L-2 and the diffuser L-3.

Specifically, the inclined surfaces of the comb teeth incline from the high pressure side to the low pressure side, and the tips of the comb teeth may have a trapezoidal shape.

The embodiment can reduce the leakage amount of the refrigerant between the impeller L-2 and the diffuser L-3 and between the diffuser L-3 and the thrust disc L-4, not only can ensure the gap required by the operation of the main shaft L-1 and the impeller L-2, but also can prevent the leakage of the refrigerant caused by overlarge gap, effectively solve the sealing problem of the compressor, and is beneficial to improving the energy efficiency of the compressor.

In addition, the structure integrates the diffuser L-3, the thrust bearing fixing plate and the shaft seal piece into one part, so that the installation structure can be simplified, the structure is more compact, and the assembly efficiency is improved. As shown in FIG. 47, the outer periphery of the diffuser L-3 is provided with a locating spigot L-33 for locating and mounting with the housing L-6 and then precisely locating by matching with a pin. Therefore, the coaxiality of the shaft seal part on the diffuser and the perpendicularity of the thrust bearing fixing surface are guaranteed on one part, so that the processing difficulty is reduced, meanwhile, the assembly accumulated error is greatly reduced, the shaft seal with high coaxiality and the thrust bearing with high perpendicularity are required to be positioned by sharing the positioning spigot L-33 and the pin, the assembly standard is unified, the assembly difficulty is reduced, the assembly precision is improved, the perpendicularity of the thrust bearing fixing surface is improved, the working performance of the thrust bearing is guaranteed, the coaxiality of the first axial comb tooth sealing structure L-35 is improved, and the abrasion of comb teeth is prevented from influencing the sealing performance.

The diffuser L-3 is made of a material having lower hardness than the thrust disk L-4 in terms of material selection, and the diffuser L-3 is generally selected from aluminum, L-45 steel, L-40Cr, and the like. Thus, if the first axial comb tooth sealing structure L-35 on the diffuser L-3 is worn with the main shaft L-1, the comb teeth are worn first so as to prevent the main shaft L-1 from being worn.

Still referring to FIG. 51, the first axial comb seal structure L-35, the radial comb seal structure L-21, and the second axial comb seal structure L-23 are provided simultaneously, and the radial comb seal structure L-21 is located radially between the first axial comb seal structure L-35 and the second axial comb seal structure L-23. The arrangement mode can enable the airflow to form a roundabout flow path, optimize the effect of reducing the speed and the pressure of the airflow and improve the sealing performance.

Specifically, one end of the impeller L-2 facing the diffuser L-3 is provided with a boss, the boss stretches into a groove of the diffuser L-3, and the radial comb tooth sealing structure L-21 is arranged at the end of the boss, so that the radial sealing is realized, the gas flow path is further prolonged, the air flow speed reduction and depressurization effect is optimized, and the sealing performance is improved.

In addition, the invention also provides air conditioning equipment, which comprises the centrifugal compressor of the embodiment. The centrifugal compressor can bear axial forces in two directions, ensure the running stability of the compressor during full-working-condition running and reversing, accurately ensure the assembly clearance of the thrust bearing and ensure the performance of the thrust bearing, thereby improving the running stability of the compressor. Both of these factors can improve the stability and reliability of operation of the air conditioning apparatus.

Diffuser, thrust disc and related matching structure modification II

Referring to fig. 30, in some embodiments, the present disclosure provides a rotor assembly including a housing H-1. A housing H-1 is formed therein with a receiving chamber.

In some embodiments, the rotor assembly includes a shaft H-8, the shaft H-8 rotatably disposed within the receiving cavity of the housing H-1. The rotary shaft H-8 corresponds to a rotor of the compressor.

Further, the rotating shaft H-8 is arranged along the central axis direction of the accommodating cavity in the shell H-1.

In some embodiments, the rotor assembly employs an electric machine (but is not limited thereto) with the housing of the electric machine being the same housing as housing H-1 of the rotor assembly.

In some embodiments, the motor includes a stator H-9, the stator H-9 is disposed between an inner wall of the housing H-1 and the rotating shaft H-8, and the stator H-9 is fixedly disposed on the inner wall of the housing H-1.

In some embodiments, the rotor assembly includes a thrust disc H-6, the thrust disc H-6 is disposed in the housing H-1, and the thrust disc H-6 is fixedly disposed at an end of the rotating shaft H-8, and the thrust disc H-6 rotates along with the rotating shaft H-8.

In some embodiments, the rotor assembly includes first and second fixtures that are disposed on opposite sides of the thrust disc H-6, respectively. The first fixing member and the second fixing member do not rotate with the rotating shaft H-8 and the thrust disc H-6.

In some embodiments, the rotor assembly includes a first thrust bearing H-4, the first thrust bearing H-4 being disposed between the thrust disc H-6 and the first stationary member. And the first thrust bearing H-4 is fixed to the first mount.

In some embodiments, the rotor assembly includes a second thrust bearing H-4, the second thrust bearing H-4 being disposed between the thrust disc H-6 and the second stationary member. And the second thrust bearing H-4 is fixedly arranged on the second fixing piece.

In some embodiments, thrust bearings are arranged on two sides of the thrust disc H-6, the thrust disc H-6 bears bidirectional axial force, the performance of the thrust bearings can be improved, the structure is simple to assemble and compact, the length of a rotor can be reduced to the greatest extent, the load of the bearing is reduced, the rigidity of the rotor is improved, the critical rotation speed of bending modes is improved, and the stability of a bearing rotor system is improved.

In some embodiments, the first thrust bearing H-4 and the second thrust bearing H-4 comprise gas bearings. Further, the first thrust bearing H-4 and the second thrust bearing H-4 are dynamic pressure gas bearings.

In some embodiments, the first thrust bearing H-4 and the second thrust bearing H-4 are lamellar structures.

In some embodiments, the first mount includes a diffuser H-7, the diffuser H-7 being coupled to an end of the housing H-1. The first thrust bearing H-4 is fixed to the diffuser H-7. The diffuser H-7 also acts as a thrust bearing mount. The diffuser H-7 is provided with a shaft hole, and the rotating shaft H-8 passes through the shaft hole arranged on the diffuser H-7.

Further, the first thrust bearing H-4 is secured to the diffuser H-7 by a screw lock.

In some embodiments, thrust disc H-6 is L-shaped in cross-section and includes a first portion and a second portion. The first part is arranged in a gap between the inner wall of the shaft hole of the diffuser H-7 and the rotating shaft H-8. The second part is arranged between the first thrust bearing H-4 and the second thrust bearing H-4.

In some embodiments, the shaft hole of the diffuser H-7 comprises a first shaft hole and a second shaft hole, the aperture of the first shaft hole is smaller than that of the second shaft hole, the end part of the rotating shaft H-8 and the first part of the thrust disc H-6 are both positioned in the first shaft hole, the first thrust bearing H-4 is positioned in the second shaft hole and fixedly connected with the inner wall surface of the second shaft hole, the second part of the thrust disc H-6 is positioned in the second shaft hole, and the second thrust bearing H-4 is positioned in the second shaft hole.

The clearance of the thrust bearing is related to the thickness of the thrust disk H-6, the depth of the second shaft hole of the diffuser H-7 and the thrust bearing, and the purpose of controlling the clearance is achieved by improving the precision of the diffuser H-7.

In some embodiments, the depth of the second shaft hole of the diffuser H-7, namely, the length tolerance range of the boss forming the second shaft hole, is reversely pushed through the known clearance range of the thrust bearing, the thickness tolerance range of the thrust disc and the thickness tolerance range of the thrust bearing, the clearance of the thrust bearing is ensured by improving the processing precision of the boss length of the diffuser H-7, the inaccurate clearance control is prevented, the performance reduction or failure of the thrust bearing is caused, the assembly difficulty is reduced, and the assembly efficiency and the assembly precision are improved.

By improving the machining precision of the diffuser H-7, the clearance of the thrust bearing is accurately ensured, the reduction of the bearing performance or the failure of the bearing caused by improper clearance of the thrust bearing is prevented, and meanwhile, the structure is compact, and the length of the rotor is reduced to the greatest extent.

Further, the inner wall of the shaft hole of the diffuser H-7 is provided with a shaft seal structure, and the shaft seal structure is used for forming dynamic seal with the thrust disc H-6, so that the shaft seal structure has a shaft seal effect and can prevent external gas from entering the shell H-1. In the case where the diffuser H-7 is a primary diffuser, the shaft seal structure is used to prevent the exhaust of the primary impeller from entering the housing H-1, i.e., the motor cavity.

Optionally, the shaft seal structure comprises a comb seal structure.

In some embodiments, the diffuser H-7 has a shaft seal function and a function of coupling the first thrust bearing H-4. The shaft seal structure and the fixed plate of the first thrust bearing H-4 are integrally arranged on the diffuser H-7, so that the structure is compact.

In some embodiments, the second mount includes a bearing support H-2, the bearing support H-2 being disposed within the housing H-1. The first end of the bearing support H-2 is fixedly connected with the second thrust bearing H-4, and the second end of the bearing support H-2 is connected with the inner wall of the shell H-1.

The first end and the second end of the bearing support H-2 are two opposite ends along the axial direction of the rotating shaft H-8.

In the above embodiment, the bearing support H-2 also has the function of a fixed plate of the second thrust bearing H-4.

In other embodiments, the second mount includes a mounting plate H-5 and a bearing support H-2 disposed within the housing H-1.

The first end of the fixing plate H-5 is fixedly connected with the second thrust bearing H-4, and the second end of the fixing plate H-5 is fixedly connected with the bearing support H-2.

The fixed plate H-5 is arranged between the second thrust bearing H-4 and the bearing support H-2.

The first end of the bearing support H-2 is fixedly connected with the second end of the fixed plate H-5, and the second end of the bearing support H-2 is connected with the inner wall of the shell H-1.

The first end and the second end of the bearing support H-2 are opposite ends.

In the above embodiment, the bearing support H-2 and the fixing plate H-5 are provided separately.

In some embodiments, the fixed plate H-5 is provided with an engagement portion that extends outwardly for engagement with a bearing hole H-21 provided in the first end of the bearing support H-2.

Further, the bearing hole H-21 formed in the bearing support H-2 comprises a first hole and a second hole, the first hole is close to the first end of the bearing support H-2 relative to the second hole, the aperture of the first hole is larger than that of the second hole, the radial bearing H-3 is arranged in the bearing hole H-21, and a gap between the radial bearing H-3 and the first hole is used for accommodating a matching part formed in the fixing plate H-5.

One side of the thrust disc H-6 is provided with a first thrust bearing H-4, and the other side of the thrust disc H-6 is provided with a second thrust bearing H-4. The first thrust bearing H-4 is fixed to the diffuser H-7. The second thrust bearing H-4 is fixed to the fixed plate H-5.

Further, the first thrust bearing H-4 is fastened to the diffuser H-7 by a screw lock. The second thrust bearing H-4 is locked on the fixed plate H-5 through a screw, and the fixed plate H-5 is locked on the bearing support H-2 through a screw.

Further, the inner wall of the housing H-1 extends toward the central axis direction of the housing H-1 to form a mounting part, and the mounting part is used for being fixedly connected with the second end of the bearing support H-2.

In some embodiments, as shown in FIG. 33, the radial dimension of the second end of bearing support H-2 is greater than the radial dimension of the first end of bearing support H-2.

The radial dimension of at least a portion between the first end and the second end of the bearing support H-2 gradually increases in the direction from the first end to the second end of the bearing support H-2.

The inventor also finds that the axial load borne by the bearing support H-2 is larger than the radial load, and the axial load is transmitted to the bearing support H-2 through the thrust bearing and the thrust bearing fixing plate, so that the first end of the bearing support H-2 provided by the disclosure is matched with the thrust bearing fixing plate and the thrust bearing, the radial dimension of the first end of the bearing support H-2 is smaller than that of the second end of the bearing support H-2 connected with the shell H-1, and the radial dimension of at least part of the bearing support H-2 is gradually increased along the direction from the first end to the second end of the bearing support H-2, so that the axial force can be well transmitted to the shell H-1 of the rotor assembly motor, the strength of the bearing support H-2 is improved, and the service life of the bearing support H-2 is prolonged.

In some embodiments, bearing support H-2 is V-shaped, and has high structural strength and is convenient for casting. The dynamic pressure bearing high-precision assembly can be guaranteed, and the stability of a bearing rotor system can be improved.

In some embodiments, the radial dimension of the first end of bearing support H-2 is less than the radial dimension of the second end of bearing support H-2.

In some embodiments, as shown in FIG. 33, bearing support H-2 includes bearing holes H-21, bearing holes H-21 for mounting bearings.

In some embodiments, bearing support H-2 includes an annular groove H-22, with annular groove H-22 disposed about bearing aperture H-21.

Optionally, the cross section of the annular groove H-22 is V-shaped and is matched with the V-shaped structure of the bearing support H-2.

In some embodiments, the inner wall of the housing H-1 is provided with a mounting portion extending towards the center of the housing H-1 for connection with the second end of the bearing support H-2.

In some embodiments, the second end of the bearing support H-2 includes a stop H-23, the stop H-23 abutting against the inside of the mounting portion.

The second end of the bearing support H-2 further includes a connecting portion H-24, the connecting portion H-24 extending outwardly relative to the limiting portion H-23 for connection with the mounting portion.

And a spigot is formed between the limiting part H-23 and the connecting part H-24 and is used for being matched and positioned with the mounting part.

Further, the connecting portion H-24 is connected with the mounting portion arranged on the inner wall of the shell H-1 through the pin, and the bearing support H-2 can be assembled with high precision through the mode that the pin and the mounting spigot are positioned together.

In some embodiments, the connecting portion H-24 is annular and disposed circumferentially about the spacing portion H-23.

In some embodiments, bearing support H-2 includes bearing hole H-21, bearing hole H-21 for mounting a bearing.

In some embodiments, bearing support H-2 includes vent H-25, vent H-25 being disposed radially of bearing support H-2, a first end of vent H-25 being in communication with bearing hole H-21, and a second end of vent H-25 being in communication with an exterior of bearing support H-2.

In some embodiments, the rotor assembly includes a radial bearing H-3, the radial bearing H-3 being disposed at an end of the shaft H-8. And the radial bearing H-3 is positioned in the bearing hole H-21 of the bearing support H-2.

In other embodiments, the rotor assembly includes a radial bearing H-3, the radial bearing H-3 being disposed at an end of the shaft H-8 and within a bearing bore H-21 of the bearing support H-2. The radial bearing H-3 and the second thrust bearing H-4 are respectively positioned at two sides of the fixed plate H-5.

In some embodiments, radial bearing H-3 is positioned within bearing bore H-21 of bearing support H-2 by a shrink fit.

In some embodiments, radial bearing H-3 comprises a gas bearing. Further, the radial bearing H-3 includes a dynamic pressure gas bearing.

In some embodiments, thrust disc H-6 is disposed at a first end of shaft H-8.

In some embodiments, the second end of the shaft H-8 is provided with a radial bearing H-3 and a bearing support H-2 that mates with the radial bearing H-3.

In some embodiments, the first end of the rotating shaft H-8 is provided with a thrust disk H-6, a first thrust bearing H-4, a second thrust bearing H-4, a radial bearing H-3, a bearing support H-2 and other structures, the second end of the rotating shaft H-8 is provided with the radial bearing H-3 and the bearing support H-2, the first end and the second end of the rotating shaft H-8 are in an asymmetric assembly mode, the assembly mode ensures bidirectional bearing, simultaneously reduces the length and the weight of the rotating shaft H-8 to the greatest extent, reduces the radial bearing load, improves the rigidity of a rotor, improves the critical rotation speed of a rotor bending mode, is convenient for gap adjustment, and can ensure the coaxiality of the two radial bearings H-3 and the verticality of the thrust bearing with high precision, and improves the assembly efficiency and the assembly precision.

On the other hand, if the symmetrical assembly mode is adopted, on one hand, the assembly difficulty is increased, and meanwhile, the length and the weight of the whole rotor are also increased, and on the other hand, because the clearance of the thrust bearing is small, if the symmetrical structure is adopted, the clearance adjustment can be difficult.

In some embodiments, radial bearings H-3 are arranged at two ends of a rotating shaft H-8 to bear radial force, thrust bearings are arranged at two sides of a thrust disc H-6 to bear bidirectional axial force, and the structure is simple to assemble and compact, can reduce the length of a rotor to the greatest extent, reduce the load of the bearings, improve the rigidity of the rotor, improve the critical rotating speed of bending modes and improve the stability of a bearing rotor system.

In some embodiments, bearing supports H-2 are arranged at two ends of the rotating shaft H-8, and the two bearing supports H-2 bore the bearing holes H-21 in a matched boring mode, so that coaxiality of the two bearing holes H-21 and perpendicularity of the matching surfaces of the fixing pieces can be well guaranteed.

Furthermore, the radial bearing H-3 is in interference fit with the bearing hole H-21 of the bearing support H-2, so that assembly errors can be reduced better, coaxiality of the two bearing holes H-21 is guaranteed, and coaxiality of the radial bearing holes H-21 is guaranteed jointly through two means of machining and hot sleeve assembly processes.

In addition, the perpendicularity of thrust surfaces on two sides of the thrust disc H-6 can be well guaranteed in a machining mode, so that the coaxiality and the perpendicularity precision can be guaranteed, bearing performance reduction caused by low precision is prevented, bearing failure is prevented when the precision is serious, and the rotor cannot float.

Some embodiments provide a compressor that includes the rotor assembly of the above embodiments.

In some embodiments, the motor housing of the compressor is the same housing as the housing H-1 of the rotor assembly.

In some embodiments, the compressor comprises a centrifugal compressor.

The assembling form of the end part of the inner rotating shaft H-8 in the compressor can 1) reduce bearing load, improve rotor rigidity, improve critical rotation speed of bending modes and improve stability of a bearing rotor system, 2) ensure coaxiality of two radial bearings and perpendicularity of a thrust bearing with high precision, improve assembling efficiency and assembling precision, 3) ensure a bidirectional bearing thrust bearing gap with high precision, and prevent the performance of the thrust bearing from being reduced or even losing efficacy due to inaccurate gap control.

The assembling form of the end part of the inner shaft H-8 of the compressor is compact in structure, the length of the rotor and the load of the bearing can be reduced, and the rigidity of the rotor and the critical rotating speed of bending modes are improved.

The radial bearing coaxiality and the thrust surface perpendicularity can be improved through machining and assembly processes, and the assembly efficiency and the assembly precision are improved.

The method and the device accurately ensure the clearance of the thrust bearing by controlling the machining precision of the diffuser H-7, and prevent the inaccurate clearance control from causing the performance reduction or failure of the thrust bearing.

The embodiments of the compressor and the compressor inner part or the assembly structure are applicable to various refrigerant circulation systems and refrigeration equipment, so the present disclosure also provides the refrigerant circulation system comprising any one embodiment of the compressor and the compressor inner part or the assembly structure, and the refrigeration equipment comprising any one embodiment of the compressor and the compressor inner part or the assembly structure.

Thus, various embodiments of the present disclosure have been described in detail. In order to avoid obscuring the concepts of the present disclosure, some details known in the art are not described. How to implement the solutions disclosed herein will be fully apparent to those skilled in the art from the above description.

Although some specific embodiments of the present disclosure have been described in detail by way of example, it should be understood by those skilled in the art that the above examples are for illustration only and are not intended to limit the scope of the present disclosure. It will be understood by those skilled in the art that the foregoing embodiments may be modified and equivalents substituted for elements thereof without departing from the scope and spirit of the disclosure. The scope of the present disclosure is defined by the appended claims.

Claims

1. The compressor is characterized by comprising a shell and a motor driving system, wherein the motor driving system comprises a compressor rotor and a motor stator, the shell is provided with a motor accommodating cavity and a compression cavity, the motor stator is fixedly arranged in the motor accommodating cavity and is provided with a rotor mounting hole, and the compressor rotor is rotatably arranged in the shell;

a reflux through hole extending along the axial direction of the compressor rotor is arranged in the motor stator, and part of fluid in the motor accommodating cavity flows from one end of the motor stator to the other end of the motor stator through the reflux through hole;

the compressor rotor includes:

The compression unit rotating part is positioned in the compression cavity, is fixedly connected to the end part of the motor rotor and forms an air inlet passage communicated with the hollow part with the motor rotor, and fluid in the compression cavity enters the hollow part through the air inlet passage and enters the motor accommodating cavity through the vent hole;

Wherein the end of the motor rotor is provided with an axial notch for matching with the rotating part of the compression unit, the side wall of the axial notch is provided with a first leakage groove which is concave towards the radial outside, the air inlet passage comprises the first leakage groove, and/or

2. The compressor of claim 1, wherein the return through hole comprises:

A return air hole above the compressor rotor for circulating air and/or,

3. The compressor of claim 1, further comprising a compression system including a volute having at least two volute lines over different angular ranges.

4. A compressor according to claim 3, wherein the at least two volute profiles comprise a first volute profile and a second volute profile distributed along the direction of airflow within the volute, the parting interface of the first and second volute profiles being 80-100 ° relative to a direction perpendicular from the center of the volute to the airflow outlet of the volute.

5. The compressor of claim 4, wherein the first volute line is D-shaped, trapezoidal, or oval, and the second volute line is circular greater than 180 °.

6. The compressor of claim 1, wherein the compressor rotor includes a motor rotor positioned in the motor housing cavity and disposed through the rotor mounting hole, having a hollow portion and a vent hole, the vent hole communicating with both the hollow portion and the motor housing cavity, the motor rotor including:

A permanent magnet;

7. The compressor of claim 1, wherein the compressor is a centrifugal compressor and the compression unit rotating portion is an impeller.

8. The compressor of claim 1, further comprising a gas bearing by which the compressor rotor is rotatably supported within the housing.

9. The compressor of claim 6, wherein,

The first end shaft section comprises a first axial bore and a plurality of first perforations communicating the first axial bore with the motor receiving cavity, the hollow comprises the first axial bore, the vent comprises the first perforations, and/or,

10. The compressor of claim 1, wherein the housing is provided with:

A cooling fluid inlet;

11. A refrigerant circulation system comprising the compressor of any one of claims 1 to 10.

12. A refrigeration device comprising a compressor as claimed in any one of claims 1 to 10.