CN111365290A - Shaft seal components, compressors and refrigerant circulation systems - Google Patents

Abstract

The present disclosure provides a shaft seal component, a compressor and a refrigerant circulation system. The shaft seal component includes: a shaft seal disc body, the center of the shaft seal disc body has a shaft hole, and a shaft seal structure is arranged on the hole wall of the shaft hole; the shaft seal positioning stop is coaxially and integrally arranged on the On the axial end of the shaft seal disc body, the shaft seal positioning stop is provided with a first fluid channel which communicates with the radial inner side and the radial outer side of the shaft seal positioning stop. The shaft seal component provided by the present disclosure has the functions of shaft sealing, positioning and fluid discharge. The shaft seal positioning stopper is beneficial to improve the matching accuracy between the shaft seal component and the sealed rotating shaft, and can more effectively prevent fluid leakage. The first fluid The passage is beneficial to prevent fluid retention in the components adjacent to the shaft seal components, and is beneficial to stabilize the back pressure of the relevant components, thereby improving the stability of the bearing rotor system.

Description

Shaft seal components, compressors and refrigerant circulation systems

technical field

The present disclosure relates to a compressor and a refrigerant circulation system, in particular to a shaft seal component, a compressor and a refrigerant circulation system.

Background technique

Hydrostatic gas bearing has the advantages of ultra-high precision, ultra-low friction, ultra-low vibration, ultra-low noise, long life, no pollution, etc. It is suitable for high-speed and high-precision occasions, especially in centrifugal compressors, especially miniaturized centrifugal compressors. It has broad application prospects.

The static pressure gas bearing needs air supply from an external air source, and requires stable working back pressure of the bearing to prevent the gas film from being damaged due to fluctuations in the bearing back pressure, which will make the bearing rotor system unstable and damaged.

SUMMARY OF THE INVENTION

The purpose of the present disclosure is to provide a shaft seal component, a compressor and a refrigerant circulation system.

A first aspect of the present disclosure provides a shaft seal component, comprising:

A shaft seal disc body, the center of the shaft seal disc body has a shaft hole, and a shaft seal structure is arranged on the hole wall of the shaft hole;

The shaft seal positioning stop is coaxially and integrally arranged at one axial end of the shaft seal disc body, and the shaft seal positioning stop is provided with a connection between the radial inner side and the radial outer side of the shaft seal positioning stop. first fluid channel.

In some embodiments, the shaft seal structure includes a comb structure.

In some embodiments, one end of the shaft seal positioning stop which is away from the shaft seal disc body has a bearing positioning end surface for axially positioning the radial bearing.

In some embodiments, the first fluid channel includes:

at least one through hole provided on the side wall of the shaft seal positioning stop; and/or

A groove is recessed from the end of the shaft seal positioning stop that is far away from the shaft seal disc body to the end close to the shaft seal disc body.

In some embodiments, the shaft seal member includes a plurality of the first fluid passages.

In some embodiments, the plurality of first fluid passages are uniformly arranged along the circumference of the shaft seal positioning stop.

In some embodiments, the plurality of first fluid passages are evenly arranged at angular intervals of 360°/(n+1) along the circumference of the shaft seal positioning stop, where n is the plurality of first fluid passages The number of fluid channels.

In some embodiments, the shaft seal component includes a shaft seal connection hole and/or a shaft seal positioning hole provided on the shaft seal disc body.

In some embodiments, the diameter of the inner peripheral surface of the shaft seal positioning stop is larger than the diameter of the shaft hole.

A second aspect of the present disclosure provides a compressor, comprising:

Compressor rotors, including main shafts;

radial bearings for carrying the main shaft; and

A shaft sealing member is the shaft sealing member according to the first aspect of the present disclosure, the main shaft is inserted into the shaft hole of the shaft sealing member, and the shaft sealing structure of the shaft sealing member is connected to the main shaft. In cooperation, the first fluid passage of the shaft seal member communicates with the gap between the radial bearing and the main shaft.

In some embodiments, the compressor further includes a bearing carrier including:

The diffuser has a shaft seal installation hole, an axial end of the diffuser is provided with a diffuser structure, and the shaft seal component is arranged in the shaft seal installation hole;

The bearing seat is integrally arranged at the other axial end of the diffuser, the bearing seat is provided with a bearing chamber that is coaxial with the shaft seal mounting hole and communicated, and the radial bearing is arranged in the bearing chamber.

In some embodiments, the bearing carrier member includes a fluid inlet channel that communicates the bearing chamber with an exterior of the bearing carrier member.

In some embodiments, the bearing carrier member includes a fluid outflow passage that communicates the shaft seal mounting hole with the outside of the bearing carrier member, and the first fluid passageway communicates with the fluid outflow passage.

In some embodiments, one end of the shaft seal positioning stop which is away from the shaft seal disc body has a bearing positioning end surface for axially positioning the radial bearing.

In some embodiments, the shaft seal mounting hole is a stepped hole, comprising a large-diameter section located at an end close to the diffuser structure and a small-diameter section located at an end away from the diffuser structure, and the large-diameter section is connected to the diffuser structure. A stepped positioning surface is formed between the small diameter sections, the shaft seal disc body is located in the large diameter section, the shaft seal positioning stop is located in the small diameter section, and the shaft seal disc body is close to the shaft seal The end face of the positioning stop is in contact with the step positioning face.

In some embodiments, the radial bearing is a gas bearing.

A third aspect of the present disclosure provides a refrigerant circulation system, including the compressor described in the second aspect of the present disclosure.

Based on the shaft seal component provided by the present disclosure, which has the functions of shaft sealing, positioning and fluid discharge, the shaft seal positioning stop is beneficial to improve the matching accuracy between the shaft seal component and the sealed rotating shaft, and can more effectively prevent fluid leakage. The fluid passage is beneficial to prevent fluid retention in the components adjacent to the shaft seal components, and is beneficial to stabilize the back pressure of the relevant components, thereby improving the stability of the bearing rotor system.

The compressor and the refrigerant circulation system provided by the present disclosure have the same advantages as the shaft seal components provided by the present disclosure.

Other features of the present disclosure and advantages thereof will become apparent from the following detailed description of exemplary embodiments of the present disclosure with reference to the accompanying drawings.

Description of drawings

The accompanying drawings described herein are used to provide a further understanding of the present disclosure and constitute a part of the present application. The exemplary embodiments of the present disclosure and their descriptions are used to explain the present disclosure and do not constitute an improper limitation of the present disclosure. In the attached image:

FIG. 1 is a schematic structural diagram of a compressor according to an embodiment of the disclosure.

FIG. 2 is a schematic three-dimensional structural diagram of a shaft seal component according to an embodiment of the disclosure.

FIG. 3 is a schematic side view of the structure of FIG. 2 .

FIG. 4 is a schematic cross-sectional structure diagram of FIG. 2 .

FIG. 5 is a partial structural schematic diagram of a compressor according to an embodiment of the disclosure.

6 is a schematic structural diagram of a bearing bearing structure of a compressor according to an embodiment of the disclosure.

Detailed ways

The technical solutions in the embodiments of the present disclosure will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present disclosure. Obviously, the described embodiments are only a part of the embodiments of the present disclosure, but not all of the embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the disclosure, its application or uses in any way. Based on the embodiments in the present disclosure, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present disclosure.

The relative arrangement of the components and steps, the numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present disclosure unless specifically stated otherwise. Meanwhile, it should be understood that, for the convenience of description, the dimensions of various parts shown in the accompanying drawings are not drawn in an actual proportional relationship. Techniques, methods, and devices known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the authorized description. In all examples shown and discussed herein, any specific value should be construed as illustrative only and not as limiting. Accordingly, other examples of exemplary embodiments may have different values. It should be noted that like numerals and letters refer to like items in the following figures, so once an item is defined in one figure, it does not require further discussion in subsequent figures.

In the description of the present disclosure, it should be understood that the use of words such as "first" and "second" to define components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above words have no special Therefore, it cannot be construed as a limitation on the protection scope of the present disclosure.

In the description of the present disclosure, it should be understood that directional words such as "front, rear, top, bottom, left, right", "horizontal, vertical, vertical, horizontal" and "top, bottom" etc. are only for the purpose of For the convenience of describing the present disclosure and simplifying the description, unless stated to the contrary, these directional words do not indicate or imply that the referred device or element must have a particular orientation or be constructed and operated in a particular orientation, and therefore should not be construed as a Disclosure of limitations of the scope of protection; the directional words "inside and outside" refer to inside and outside relative to the contours of each component itself.

As shown in FIGS. 1 to 5 , an embodiment of the present disclosure provides a shaft seal component 70 . The shaft seal component 70 includes a shaft seal disc body 71 and a shaft seal positioning stop 72 . The shaft seal disc body 71 has a shaft hole in the center, and a shaft seal structure is provided on the hole wall of the shaft hole. The shaft seal positioning stop 72 is coaxially and integrally provided at one end of the shaft seal disc body 71 in the axial direction. fluid channel.

The shaft seal member 70 of the embodiment of the present disclosure has both the functions of shaft seal, positioning and fluid discharge, and the shaft seal positioning stop 72 is beneficial to improve the matching accuracy between the shaft seal member 70 and the sealed rotating shaft (such as the main shaft 21 of the compressor). , which can more effectively prevent fluid leakage. The first fluid passage is beneficial to prevent fluid retention in the components (such as radial bearings) that cooperate with the shaft seal component 70, stabilize the back pressure of the relevant components, and improve the stability of the bearing rotor system.

As shown in FIGS. 1 to 5 , in some embodiments, the shaft seal structure includes a comb-tooth structure 711 . The comb-tooth structure 711 is more suitable for sealing gas, suitable for use in compressors, and can effectively prevent leakage of pressurized gas.

As shown in FIGS. 1 to 5 , in some embodiments, one end of the shaft seal positioning stop 72 away from the shaft seal disc body 71 has a bearing positioning end surface 721 for axially positioning the radial bearing. The bearing locating end surface 721 enables the shaft seal component 70 to have both the axial locating function of the radial bearing, which is beneficial to simplify the structure of the device where it is located and shorten the length of the rotor of the device where it is located.

The structure of the first fluid channel can be various. For example, as shown in FIG. 1 to FIG. 5 , in some embodiments, the first fluid channel includes a direction from an end away from the shaft seal disc body 71 to a direction close to the shaft seal disc body 71 . One end of the groove 722 is concave. In a not-shown embodiment, the first fluid passage may include at least one through hole provided on the side wall of the shaft seal positioning stop 72 . It is also possible to provide both grooves and through holes as the first fluid passage.

As shown in FIGS. 3 and 4 , in some embodiments, the shaft seal component 70 includes a plurality of first fluid passages. The provision of a plurality of first fluid passages facilitates the rapid and uniform discharge of the fluid in the vicinity of the relevant components such as the radial bearing, and is beneficial to prevent the fluid from stagnant in the vicinity of the relevant components.

As shown in FIGS. 3 and 4 , in some embodiments, the plurality of first fluid passages are uniformly arranged along the circumference of the shaft seal positioning stop 72 . This arrangement facilitates the rapid and uniform discharge of the fluid in the vicinity of the relevant parts such as the radial bearing, and is beneficial to prevent the fluid from stagnant in the vicinity of the relevant parts.

In some embodiments, the plurality of first fluid passages are evenly arranged at angular intervals of 360°/n+1 along the circumferential direction of the shaft seal positioning stop 72 , where n is the number of the plurality of first fluid passages. The number of n can be 2, 3, 4, 5, 6 or more. In the embodiments shown in Figures 3 and 4, n=5. The number and distribution of the first fluid passages advantageously correspond to the number and distribution of the fluid outflow passages 64 provided on the bearing carrier 60 . This arrangement facilitates the formation of a fluid discharge passage in cooperation with related components such as the bearing bearing component 60 described later, and facilitates reserving a setting position for the setting of the fluid inlet passage of the related components.

The shaft seal component 70 includes a shaft seal connection hole 712 and/or a shaft seal positioning hole 713 provided on the shaft seal disc body 71 . The shaft seal positioning hole 713 can accurately determine the connection position between the shaft seal member 70 and the related parts such as the bearing bearing member 60 described later, which is conducive to the rapid and accurate realization of the first fluid channel and the corresponding fluid channel (such as the bearing bearing member 60). The fluid outflow channel 64) communicates. The shaft seal connection hole 712 facilitates the detachable connection with the relevant components through the screw connection.

As shown in FIGS. 1 to 5 , in some embodiments, the diameter of the inner peripheral surface of the shaft seal positioning stop 72 is larger than the diameter of the shaft hole of the shaft seal disc body 71 . This arrangement facilitates the communication between the first fluid passage and the gap between the radial bearing and the main shaft 21, and facilitates the uniform distribution of fluid among the first fluid passages.

Embodiments of the present disclosure also provide a compressor including a compressor rotor 20 , a radial bearing and a shaft seal member 70 . The compressor rotor 20 includes a main shaft 21 . Radial bearings are used to carry the main shaft 21 . The shaft seal member 70 is the aforementioned shaft seal member 70 . The main shaft 21 is inserted through the shaft hole of the shaft seal member 70 . The shaft sealing structure of the shaft sealing member 70 is matched with the main shaft 21 . The first fluid passage communicates with the gap between the radial bearing and the main shaft 21 . The arrangement is beneficial to prevent the fluid from stagnant near the radial bearing, to keep the back pressure of the radial bearing stable, and to ensure the stable operation of the compressor.

As shown in FIGS. 1 , 5 and 6 , in some embodiments, the compressor further includes a bearing carrying part 60 , and the bearing carrying part 60 includes a diffuser and a bearing seat. The diffuser has a shaft seal mounting hole 67 , and one axial end of the diffuser (the right end in FIGS. 1 , 5 and 6 ) is provided with a diffuser structure. The diffuser structure can be, for example, a diffuser surface or a diffuser vane. The shaft seal member 70 is provided in the shaft seal mounting hole 67 . The bearing seat is integrally arranged at the other axial end of the diffuser. The bearing housing is provided with a bearing chamber 62 that is coaxial with and communicated with the shaft seal mounting hole 67 . The radial bearing is arranged in the bearing chamber 62 . The bearing bearing member 60 also undertakes the functions of installing the diffuser, the bearing seat and the shaft seal member. The shaft seal member 70 cooperates with the radial bearing to be installed in the bearing bearing member 60, which is beneficial for the compressor to shorten the length of the compressor rotor and lighten the compressor rotor. The weight is beneficial to increase the critical speed of the compressor rotor.

As shown in FIGS. 1 , 5 and 6 , in some embodiments, the bearing carrier 60 includes a fluid inlet channel 63 that communicates the bearing chamber 62 with the outside of the bearing carrier 60 . The fluid inlet channel 63 may supply the radial bearing with the fluid required to carry the main shaft 21, such as suspending gas. The fluid inlet channel 63 can be, for example, a hole provided inside the bearing carrier member 60 .

As shown in FIG. 1 , FIG. 5 , and FIG. 6 , in some embodiments, the bearing carrier 60 includes a fluid outflow channel 64 that communicates with the shaft seal mounting hole 67 and the outside of the bearing carrier 60 , and the first fluid channel and the fluid outflow channel 64 Connected. The arrangement is beneficial to prevent fluid from stagnant near the radial bearing, and is beneficial to keep the back pressure of the radial bearing stable, thereby facilitating the stable operation of the compressor.

As shown in FIGS. 1 to 5 , the first fluid passage of the shaft seal component 70 is a plurality of grooves 722 provided on the shaft seal positioning stop 72 . The number of grooves 722 is not limited, for example, it can be 3-12. The number of fluid outflow passages 64 and grooves 722 of the bearing carrier structure 60 is the same. The fluid outflow channel 64 is a hole disposed inside the bearing support structure 60 .

As shown in FIG. 1 and FIG. 5 , in some embodiments, one end of the shaft seal positioning stop 72 away from the shaft seal disc body 71 has a bearing positioning end surface 721 for axially positioning the radial bearing. This arrangement enables the shaft seal component 70 to simultaneously undertake the axial positioning function of the radial bearing, which is beneficial to shorten the length of the compressor rotor, reduce the weight of the compressor rotor and the whole machine, and simplify the compressor structure. The bearing locating end face 721 and the corresponding end face of the radial bearing can, for example, be clearance fit.

As shown in FIG. 1 , FIG. 5 and FIG. 6 , in some embodiments, the shaft seal mounting hole 67 is a stepped hole, including a large diameter section at one end close to the diffuser structure and a small diameter section at an end away from the diffuser structure. The shaft seal disc body 71 is installed in the large diameter section to cooperate with the large diameter section, and the shaft seal positioning stop 72 is installed in the small diameter section to cooperate with the small diameter section. A stepped positioning surface 65 is formed between the large diameter section and the small diameter section, and the end surface 714 of the shaft seal disc body 71 close to the positioning ring is in clearance fit with the stepped positioning surface 65 . This arrangement facilitates the axial positioning of the bearing member 70 . At the same time, because the shaft seal component undertakes the axial positioning function of the radial bearing, it is also beneficial to the axial positioning of the radial bearing.

As shown in FIG. 6 , the fluid inlet of the fluid inlet passage 63 is provided on the end face of the other axial end of the diffuser. This arrangement facilitates the introduction of fluid from within the compressor housing into the fluid inlet passage 63 .

Bearing carrier member 60 includes a plurality of fluid outflow passages 64 . The plurality of fluid outflow channels 64 are evenly distributed along the circumferential direction of the bearing carrier member 60 . The plurality of fluid outflow channels 64 are evenly distributed along the circumferential interval of the bearing carrier 60 at 360°/m+1, where m is the number of the plurality of fluid outflow channels 64 . The number of m can be 2, 3, 4, 5, 6 or more. In the embodiments shown in Figures 1 to 6, m=5. The number and distribution of the first fluid passages correspond to the quantity and distribution of the fluid outflow passages 64 provided on the bearing support member 60 . In the circumferential direction of the bearing carrier part 60 where the fluid outflow channel 64 is not arranged, the fluid inlet channel 63 is arranged. This arrangement can make all the fluid channels of the bearing carrier part 60 roughly evenly distributed, which is beneficial to the processing of the fluid channel and the assembly of the bearing carrier part 60 Positioning accuracy.

As shown in FIGS. 1 , 5 and 6 , the fluid outlet of the fluid outflow channel 64 is provided on the end face of the second axial end of the diffuser and/or on the outer peripheral face of the bearing seat.

The bearing bearing member 60 includes a bearing positioning structure disposed at the other end in the axial direction for positioning the radial bearing in the axial direction. The bearing locating structure includes an annular groove 66 . The annular groove 66 is provided on the side wall of the bearing chamber 62 . The snap ring 81 is installed in the ring groove 66 , and the inner diameter of the snap ring 81 is smaller than the diameter of the bearing chamber 62 .

The bearing bearing member 60 further includes a bearing member positioning stop 68 disposed at the other axial end of the diffuser, and a diffuser positioning hole 69 and a diffuser mounting hole disposed on the diffuser. The bearing member positioning stop 68 is matched with the inner wall of the right end of the motor cylinder 11 of the casing 10 of the compressor to determine the radial position and the axial position of the bearing bearing member 60 . The bearing support member 60 is circumferentially positioned between the housing 10 through the positioning member passing through the diffuser positioning hole 69 , and is fixedly connected to the housing 10 through the threaded connection member passing through the diffuser mounting hole.

Embodiments of the present disclosure also provide a refrigerant circulation system, including the aforementioned compressor.

The compressor and the refrigerant circulation system of the embodiment of the present disclosure have the corresponding advantages of the shaft seal component 70 of the embodiment of the present disclosure.

Some embodiments of the present disclosure will be described in more detail below with reference to FIGS. 1 to 6 .

As shown in FIG. 1 , the compressor mainly includes a casing 10 , a compressor rotor 20 , a motor stator 30 , a bearing assembly, a first-stage diffuser 50 , a bearing bearing part 60 and a shaft sealing part 70 .

The housing 10 includes a motor cylinder 11 and a primary volute 12 and a secondary volute 13 respectively connected to the left and right ends of the motor cylinder 11 . The left end of the motor cylinder 11 has an end wall, and the right end is open.

The first-stage diffuser 50 and the bearing carrying member 60 and the shaft sealing member 70 installed in the shaft seal mounting hole 67 of the bearing carrying member 60 are respectively disposed on the left and right ends of the motor cylinder 11, and the inner space of the casing 10 is separated. It is divided into a motor accommodating cavity 14 located in the middle of the casing 10 , a primary compression cavity 15 located at the left end of the casing 10 , and a secondary compression cavity 16 located at the right end of the casing 10 .

The compressor rotor 20 mainly includes a main shaft 21 , a primary impeller 22 , a secondary impeller 23 and a thrust disc member 24 .

The motor stator 30 is fixed on the inner wall of the motor cylinder 11 and has a rotor installation hole. Spiral grooves may be provided on the inner wall of the motor cylinder 11 for passing the cooling fluid for cooling the motor stator 30 .

The main shaft 21 is disposed in the motor stator 30 and penetrates through the rotor mounting hole of the motor stator 30 . A permanent magnet for generating a magnetic field is provided in the middle of the main shaft 21 , and a first end shaft segment and a second end shaft segment are respectively provided at the left and right ends of the permanent magnet. Therefore, in this embodiment, the main shaft 21 is also the motor rotor of the motor of the compressor. The motor stator 30 and the main shaft 21 constitute the motor of the compressor. After the winding of the motor stator 30 is energized, the main shaft 21 is driven to rotate, thereby driving the entire compressor rotor to rotate.

The primary impeller 22 and the secondary impeller 23 are fixedly connected to the left and right ends of the main shaft 21 respectively. The diffusing structures of the first-stage impeller 22 and the first-stage diffuser 50 are located in the first-stage compression chamber 15 . The diffuser structures on the secondary impeller 23 and the bearing carrier member 60 are located within the secondary compression chamber 16 .

The thrust disc component 24 is disposed adjacent to the first stage impeller 22 and includes a thrust disc and an integrally provided mounting sleeve. The thrust plate member 24 is fixedly sleeved on the outer circumference of the first end shaft section of the main shaft 21 . The mounting sleeve is located between the first stage impeller 22 and the thrust disc. The thrust disc component 24 can be fitted on the first end shaft section of the main shaft 21 by shrinking.

The bearing assembly includes a thrust bearing assembly 41 , a first radial bearing 42 and a second radial bearing.

As shown in FIG. 1 , the thrust bearing assembly 41 includes a first thrust bearing 411 , a second thrust bearing 412 and a thrust bearing locating ring 413 . In the embodiments shown in FIGS. 1 to 6 , the first thrust bearing 411 , the second thrust bearing 412 , the first radial bearing 42 and the second radial bearing are all static pressure gas bearings.

The left end of the primary diffuser 50 has a diffusing structure, such as a diffusing surface or a diffusing vane. The center of the first-stage diffuser 50 is provided with a shaft hole, and the shaft hole is provided with a shaft seal structure, such as a comb-tooth structure. The mounting sleeve of the thrust disc component 24 is located in the shaft hole of the first-stage diffuser 50, and cooperates with the shaft seal structure provided in the shaft hole. The radial outer end of the primary diffuser 50 is sealedly fixed on the end wall of the motor cylinder 11 , so that the primary diffuser 50 isolates the primary compression chamber 15 at the left end of the housing 10 from the motor housing in the middle of the housing 10 . Cavity 14.

As shown in FIG. 1 , the right end of the first-stage diffuser 50 has a diffuser positioning stop, the left end of the end wall of the motor cylinder 11 has a diffuser installation opening, and the diffuser positioning stop of the first-stage diffuser 50 It is installed in the diffuser installation port and cooperates with the diffuser installation port, so as to realize the axial and radial positioning of the primary diffuser 50 . The inside of the diffuser positioning stop of the first-stage diffuser 50 and the bottom wall of the diffuser installation opening of the motor cylinder 11 enclose a thrust bearing assembly installation chamber.

The thrust bearing assembly 41 is disposed in the thrust bearing assembly installation chamber. The left and right end surfaces of the thrust plate of the thrust plate member 24 are matched with the first thrust surface of the first thrust bearing 411 and the second thrust surface of the second thrust bearing 412 respectively, so that the thrust plate is connected to the first thrust bearing 411 and the second thrust bearing. 412 collectively define the axial position of the compressor rotor 21 .

The radially outer end of the first thrust surface of the first thrust bearing 411 is also provided with a first positioning surface, the radially outer end of the second thrust surface of the second thrust bearing 412 is also provided with a second positioning surface, and the thrust bearing positioning ring The left and right end surfaces of the thrust bearing locating ring 413 are in clearance fit with the first positioning surface and the second positioning surface respectively, so that the distance between the left and right end surfaces of the thrust bearing positioning ring 413 can define the distance between the first thrust surface and the second thrust surface, The sum of the clearance between the thrust disc and the first thrust surface and the clearance between the thrust disc and the second thrust surface may be defined. The thrust bearing positioning ring 413 is fixedly connected to the second thrust bearing 42 and the end wall of the motor cylinder 11 through a screw connection.

The thrust bearing locating ring 413 is provided with a second fluid channel for connecting the radially inner side and the radially outer side thereof. The second fluid passage is beneficial to ensure the stability of the back pressure of the thrust bearing assembly, thereby facilitating the stable operation of the compressor.

An end wall bearing chamber is arranged in the radial middle portion of the end wall of the motor cylinder 10 , and the first radial bearing 42 is arranged in the end wall bearing chamber. The left end of the first radial bearing 42 is in clearance fit with the side of the second thrust bearing 412 away from the second thrust surface, and the right end of the first radial bearing 42 is in clearance with the snap ring 82 installed in the snap groove of the end wall bearing chamber Fits so that the axial position of the first radial bearing 42 is jointly determined by the second thrust bearing 412 and the snap ring 82 .

The bearing carrying part 60 integrates a diffuser (in the embodiment shown in FIG. 1 , it is a secondary diffuser) and a bearing seat, and the second radial bearing 43 is installed in the bearing chamber 62 of the bearing carrying part 60 . The second radial bearing 43 is sleeved on the outer circumference of the second end shaft section of the main shaft 21 .

The shaft seal member 70 is fixedly installed in the shaft seal installation hole 67 of the bearing carrying member 60 . As described above, the bearing support member 60 is fixedly mounted on the right end of the motor cylinder 11 . Moreover, the bearing carrying member 60 and the motor cylinder 11 are in a sealed connection. After the shaft sealing member 70 is installed on the bearing bearing member 60 and is sleeved outside the main shaft 21, a seal is formed between the shaft sealing structure in the shaft hole of the bearing member 70 and the shaft section of the second end of the main shaft 21, and the bearing member 70 is radially outward. The end is sealingly connected to the radially inner end of the bearing carrier member 60 , so that the shaft seal member 70 and the bearing carrier member 60 isolate the second compression chamber 16 of the housing 10 from the motor housing chamber 14 .

After the bearing carrying part 60 , the shaft seal part 70 and the second radial bearing 43 are assembled, the bearing positioning end face 721 of the shaft seal part 70 is in clearance fit with the right end face of the second radial bearing 43 , and the left end of the second radial bearing 43 is in clearance fit. Clearly fit with the snap ring 81 , so that the axial position of the second radial bearing 43 is jointly determined by the shaft seal member 70 and the snap ring 81 . At the same time, each of the first fluid passages of the shaft sealing member 70 is in corresponding communication with each of the fluid outflow passages 64 of the bearing carrying member 60 .

As shown in FIG. 1 , the motor cylinder 11 is provided with a first gas inlet channel 17 for supplying suspended gas to the first radial bearing 42 and the second radial bearing 43 . The fluid inflow channel 63 of the bearing carrying part 60 communicates with the first gas inlet channel 17 through the fluid inlet provided on the end face of the diffuser, so that the suspended gas can be introduced into the bearing chamber of the bearing carrying part 60 and pass through the second diameter. The porous medium to the bearing 43 enters the gap between the second radial bearing 43 and the second end shaft section of the main shaft 21, and then enters the inner cavity of the positioning ring 72 of the shaft seal member 70, and then enters each of the first fluid passages. The fluid of the corresponding bearing bearing member 60 flows out of the channel 64 , then enters the motor accommodating cavity 14 , and then flows out of the housing 10 through the outlet (not shown) provided on the motor cylinder 11 .

In this embodiment, the housing 10 is further provided with a second gas inlet channel for supplying suspended gas to the thrust bearing assembly 41 , and the second gas inlet channel is independent from the first gas inlet channel. The suspended gas in the second gas inlet channel is supplied to the inside of the first thrust bearing 411 and the second thrust bearing 412 respectively, and enters the first thrust surface and the thrust through the porous medium of the first thrust bearing 411 and the porous medium of the second thrust bearing 412 The gap between the disks and the gap between the second thrust surface and the thrust disk then flow to the motor accommodating cavity 14 through the second fluid channel on the thrust bearing positioning ring 413 . The second fluid channel on the thrust bearing locating ring 413 facilitates the timely discharge of suspended gas and ensures stable back pressure of the thrust bearing assembly 41 .

In some not-shown embodiments, the second gas inlet channel may communicate with the first gas inlet channel, so that each branch flow channel and the corresponding branch flow channel can be formed through the same housing air inlet and the same main channel. Suspended gas is supplied to each gas bearing.

As shown in FIG. 5 , the arrows therein indicate the flow paths of the suspended gas supplied to the second radial bearing 43 . The suspended gas enters the fluid inlet channel 63 and the bearing chamber 62 of the bearing bearing member 60 from the first gas inlet channel 17 at the bottom of the motor cylinder 11, and then supplies the second radial bearing 43, and the suspended gas enters the inside of the second radial bearing 43, Through the throttling of the porous medium of the second radial bearing 43, it enters the gap between the second radial bearing 43 and the main shaft 21, and the suspended gas forms a gas film in the gap between the second radial bearing 43 and the main shaft 21, so that the The main shaft 21 is floated and then discharged from both ends of the gap. The suspended gas discharged from the left end enters the motor accommodating cavity 14 and is then discharged from the housing 10 together with the cooling gas for cooling the motor. The suspended gas discharged from the right end enters each fluid outflow channel 64 of the bearing support structure 60 through each first fluid channel on the shaft seal member 70, and then enters the motor accommodating cavity 14, and together with the cooling gas for cooling the motor, flows out of the housing 10 from the housing 10. discharge.

Hydrostatic gas bearings require high precision, and the bearing clearance is generally below 10μm. The sealing gap of the shaft sealing structure of the shaft sealing component 70 should also be as small as possible under the condition of ensuring relative rotation. For example, the sealing gap can be as low as 0.02mm. The requirements are very high. The shaft seal component 70 can be positioned with the compressor-related components such as the bearing bearing component 70 and the housing 10 through the shaft seal positioning stop 72 , which is beneficial to ensure the coaxiality of the shaft seal structure and the main shaft 21 .

The shaft seal structure is set as a comb structure, which cooperates with the main shaft 21 to prevent the exhaust gas from the secondary impeller 23 of the compressor from entering the bearing chamber 62 of the bearing bearing member 60, which is beneficial to reduce the leakage loss of the compressor, improve the energy efficiency of the compressor, and at the same time It is also beneficial to prevent the back pressure of the bearing chamber 62 from increasing due to too much leakage.

The back pressure of the bearing chamber 62 affects the air film pressure distribution between the second radial bearing 43 and the main shaft 21, which in turn affects the bearing stiffness and damping, which in turn affect the rotor dynamic stability. On the other hand, the bearing Fluctuations in back pressure can also cause bearing whirl. Therefore, when a hydrostatic gas bearing is in use, ensuring the stability of the back pressure is conducive to ensuring the stability of the bearing rotor system. The first fluid passage of the shaft seal member 70 and the fluid outflow passage 64 of the bearing support structure 60 prevent the gas discharged from the left end from remaining in the shaft seal member 70 and the bearing support member 60, thus effectively preventing the bearing of the second radial bearing 43 Unstable back pressure.

The bearing positioning end face 721 of the shaft seal member 70 is in clearance fit with the right end face of the second radial bearing 43 , and together with the snap ring 81 restricts the axial position of the second radial bearing 43 , which can prevent the second radial bearing 43 from moving left and right cause bearing instability.

It can be seen that the shaft seal component 70 in the embodiment of the present disclosure is beneficial to reduce leakage loss and at the same time to ensure stable working back pressure of the radial bearing adjacent to the shaft seal component 70, thereby improving the energy efficiency of the compressor and improving the bearing rotor. System stability.

The bearing bearing component 60 of the embodiment of the present disclosure designs the diffuser and the bearing seat as one part, and sets the shaft seal installation hole at the same time, and integrates the functions of the diffuser, the bearing seat and the shaft seal installation seat, which is beneficial to reduce the number of parts and improve the Assembly efficiency, but also can reduce the length of the compressor rotor, improve the stability of the bearing rotor system.

Because the bearing carrying member 60 has the fluid inflow channel 63 and the fluid outflow channel 64, it is beneficial to ensure the normal operation of the second radial bearing 43 and the stable working back pressure, and is beneficial to improve the stability of the bearing rotor system, and also acts as a diffuser, reducing the The number of parts is reduced, the length of the compressor rotor is reduced, and the stability of the bearing rotor system is improved.

The bearing bearing member 60 adopts the bearing member positioning stop 68 and the diffuser positioning hole 69 for double positioning together with the positioning pins. The bearing member positioning stop 68 and the right end face and inner wall surface of the motor cylinder 11 can ensure the bearing bearing member 60 and the coaxiality between the bearing chamber 62 and the main shaft 21, thereby ensuring the coaxiality between the second radial bearing 43 and the main shaft 21 after assembly, through the pin and the diffuser positioning hole 69, the circumference of the bearing bearing member 60 can be adjusted. to precise positioning. Therefore, the bearing carrying member 60 can improve assembly efficiency and accuracy.

Since the bearing clearance of the static pressure gas bearing is generally several microns to tens of microns, the rotating machinery supported by the static pressure gas bearing has extremely high requirements on the same bearing of the two radial bearings. If the coaxiality is poor, the bearing performance will be reduced. In severe cases, the rotor cannot be floated. Therefore, the bearing supporting structure 60 and the bearing component 70 matched with the bearing supporting structure 60 of the embodiment of the present disclosure are suitable for the compressor which adopts the static pressure gas bearing bearing. Of course, although the shaft seal member 70 of the embodiment of the present disclosure is suitable for a compressor using a gas bearing, such as a centrifugal compressor, it is not excluded that the shaft seal member 70 of the embodiment of the present disclosure is used in other rotating systems.

Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present disclosure and not to limit them; although the present disclosure has been described in detail with reference to the preferred embodiments, those of ordinary skill in the art should understand: Modifications to the disclosed specific embodiments or equivalent replacement of some technical features shall all be included in the scope of the technical solutions claimed in the present disclosure.

Claims (16)

1. A shaft seal component (70), comprising:

the shaft seal device comprises a shaft seal disc body (71), wherein a shaft hole is formed in the center of the shaft seal disc body (71), and a shaft seal structure is arranged on the hole wall of the shaft hole;

the shaft seal positioning spigot (72) is coaxially and integrally arranged at one axial end of the shaft seal disc body (71), and a first fluid channel communicated with the radial inner side and the radial outer side of the shaft seal positioning spigot (72) is arranged on the shaft seal positioning spigot (72).

2. Shaft seal component (70) according to claim 1, characterized in that the shaft seal structure comprises a comb structure (711).

3. Shaft seal component (70) according to claim 1, characterized in that the end of the shaft seal positioning spigot (72) remote from the shaft seal disc (71) has a bearing positioning end face (721) for axially positioning a radial bearing.

4. The shaft seal member (70) of claim 1 wherein said first fluid passage comprises:

at least one through hole arranged on the side wall of the shaft seal positioning spigot (72); and/or

The groove (722) is recessed from one end, far away from the shaft seal disc body (71), of the shaft seal positioning spigot (72) to one end, close to the shaft seal disc body (71).

5. The shaft seal member (70) of claim 1 wherein said shaft seal member (70) includes a plurality of said first fluid passages uniformly disposed along a circumference of said shaft seal positioning spigot (72).

6. The shaft seal member (70) of claim 5 wherein said plurality of first fluid passages are uniformly disposed at angular intervals of 360 °/(n +1) in a circumferential direction of said shaft seal positioning seam allowance (72), where n is the number of said plurality of first fluid passages.

7. The shaft seal member (70) of claim 1 wherein the shaft seal member (70) includes a shaft seal attachment hole (712) and/or a shaft seal positioning hole (713) provided on the shaft seal disc (71).

8. The shaft seal member (70) of claim 1 wherein the diameter of the inner peripheral surface of said shaft seal retaining spigot (72) is greater than the diameter of said shaft bore.

9. A compressor, comprising:

a compressor rotor (20) comprising a main shaft (21);

a radial bearing for carrying the main shaft (21); and

the shaft seal part (70) is the shaft seal part (70) according to any one of claims 1 to 9, the main shaft (21) is inserted into the shaft hole of the shaft seal part (70), the shaft seal structure of the shaft seal part (70) is matched with the main shaft (21), and the first fluid passage of the shaft seal part (70) is communicated with a gap between the radial bearing and the main shaft (21).

10. The compressor of claim 9, further comprising a bearing carrier (60), the bearing carrier (60) comprising:

the diffuser is provided with a shaft seal mounting hole (67), a diffusion structure is arranged at one axial end of the diffuser, and the shaft seal part (70) is arranged in the shaft seal mounting hole (67);

the bearing seat is integrally arranged at the other axial end of the diffuser, a bearing chamber (62) which is coaxial and communicated with the shaft seal mounting hole (67) is arranged on the bearing seat, and the radial bearing is arranged in the bearing chamber (62).

11. The compressor of claim 10, wherein the bearing carrier (60) includes a fluid inlet passage (63), the fluid inlet passage (63) communicating the bearing chamber (62) with an exterior of the bearing carrier (60).

12. The compressor of claim 10, wherein the bearing carrier (60) includes a fluid outflow channel (64), the fluid outflow channel (64) communicating the shaft seal mounting hole (67) with an exterior of the bearing carrier (60), the first fluid channel communicating with the fluid outflow channel (64).

13. The compressor of claim 10 wherein an end of the shaft seal locating spigot (72) remote from the shaft seal disc (71) has a bearing locating end face (721) for axially locating a radial bearing.

14. The compressor of claim 10, wherein the shaft seal mounting hole (67) is a stepped hole and comprises a large diameter section located at one end close to the diffuser structure and a small diameter section located at one end far away from the diffuser structure, a step positioning surface (65) is formed between the large diameter section and the small diameter section, the shaft seal disc body (71) is located in the large diameter section, the shaft seal positioning spigot (72) is located in the small diameter section, and an end surface (714) of the shaft seal disc body (71) close to the shaft seal positioning spigot (72) abuts against the step positioning surface (65).

15. The compressor of claim 10, wherein the radial bearing is a gas bearing.

16. A refrigerant circulation system comprising the compressor of any one of claims 10 to 15.

Images