CN111365254B - Compressors for optimizing interior space - Google Patents
Compressors for optimizing interior space Download PDFInfo
- Publication number
- CN111365254B CN111365254B CN201811593234.6A CN201811593234A CN111365254B CN 111365254 B CN111365254 B CN 111365254B CN 201811593234 A CN201811593234 A CN 201811593234A CN 111365254 B CN111365254 B CN 111365254B
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- Prior art keywords
- gas
- bearing
- housing
- air
- compressor
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- 239000007789 gas Substances 0.000 claims description 178
- 239000000112 cooling gas Substances 0.000 claims description 18
- 238000009423 ventilation Methods 0.000 claims description 18
- 230000008093 supporting effect Effects 0.000 claims description 16
- 238000007789 sealing Methods 0.000 claims description 10
- 230000002706 hydrostatic effect Effects 0.000 claims description 7
- 238000007599 discharging Methods 0.000 claims description 3
- 239000003921 oil Substances 0.000 description 4
- 244000126211 Hericium coralloides Species 0.000 description 3
- 239000003507 refrigerant Substances 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000011148 porous material Substances 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 1
- 239000012466 permeate Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
- F04D29/057—Bearings hydrostatic; hydrodynamic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/06—Lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
- F04D29/5846—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling by injection
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Thermal Sciences (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
本公开涉及一种压缩机，包括：壳体(2)；电机定子(3)和电机转子(8)，均设置在壳体(2)内；和第一气体轴承，设置在壳体(2)内，并支撑电机转子(8)；压缩机还包括：供气流道，设置在壳体(2)内，用于连接外部气源，并将外部气源提供的工作气体供应给第一气体轴承；和排气装置，其吸气口位于壳体(2)内，用于将从第一气体轴承和电机转子(8)的间隙流出，并经由电机定子(3)和电机转子(8)的间隙流动到电机定子(3)的第一侧的工作气体排出到壳体(2)外；其中，电机定子(3)的第一侧为电机定子(3)在轴向上远离第一气体轴承的一侧。本公开实施例能够优化压缩机内部空间。
The present disclosure relates to a compressor, comprising: a housing (2); a motor stator (3) and a motor rotor (8), both of which are arranged in the housing (2); and a first gas bearing, which is arranged in the housing (2) and supports the motor rotor (8); the compressor also comprises: a gas supply channel, which is arranged in the housing (2) and is used to connect an external gas source and supply working gas provided by the external gas source to the first gas bearing; and an exhaust device, whose air intake is located in the housing (2) and is used to discharge the working gas that flows out of the gap between the first gas bearing and the motor rotor (8) and flows to the first side of the motor stator (3) through the gap between the motor stator (3) and the motor rotor (8) to the outside of the housing (2); wherein the first side of the motor stator (3) is the side of the motor stator (3) that is far away from the first gas bearing in the axial direction. The embodiment of the present disclosure can optimize the internal space of the compressor.
Description
Technical Field
The present disclosure relates to a compressor for optimizing an inner space.
Background
A centrifugal compressor is a compressor that compresses gas by generating centrifugal force by rotation of a high-speed impeller. At present, a centrifugal compressor mainly adopts two bearings, namely an oil lubrication bearing and an electromagnetic bearing, to support a rotor. Wherein, the oil lubrication bearing needs to be matched with an additional oil supply system, which leads to the complex structure of the centrifugal compressor. But also friction between the oil and the rotor, which can lead to energy losses. In addition, the lubricating oil may leak into the refrigerant, causing pollution of the refrigerant. The electromagnetic bearing has higher control requirement and poorer system impact resistance, and an additional power-off protection system is also needed.
The hydrostatic gas bearing is a bearing for supporting a rotor by using gas pressure, and belongs to an oilless bearing. The bearing has simple structure, small friction between the gas and the rotor and no need of complex control system. The static pressure gas bearing adopts external gas supply, the gas pressure is easy to adjust, and the gas can be continuously supplied in the start-stop stage of the compressor, so that the contact friction between the rotor and the bearing caused by insufficient gas supply in the start-stop stage is avoided, and the stability of the system is improved.
Disclosure of Invention
The present inventors have found that it is difficult for the related art compressor to introduce external gas into the gas bearing accurately and with less loss, and that an additional gas collecting device is often required to occupy the internal space of the compressor.
In view of the above, the embodiments of the present disclosure provide a compressor capable of optimizing an internal space of the compressor.
In one aspect of the present disclosure, there is provided a compressor including:
A housing;
a motor stator and a motor rotor both disposed within the housing, and
A first gas bearing disposed within the housing and supporting the motor rotor;
Characterized in that the compressor further comprises:
a gas supply flow passage provided in the housing for connecting an external gas source and supplying a working gas supplied from the external gas source to the first gas bearing, and
An exhaust device having an air inlet located in the housing for exhausting working gas flowing out of a gap between the first gas bearing and the motor rotor and flowing to a first side of the motor stator through the gap between the motor stator and the motor rotor to the outside of the housing;
Wherein the first side of the motor stator is a side of the motor stator axially remote from the first gas bearing.
In some embodiments, a cooling gas flow passage is provided between the housing and the motor stator, an outlet of the cooling gas flow passage being located on a second side of the motor stator such that cooling gas flowing from the outlet of the cooling gas flow passage can be mixed with working gas flowing from a gap between the first gas bearing and the motor rotor on the second side of the motor stator and then flows to the first side of the motor stator via the gap between the motor stator and the motor rotor;
Wherein the second side of the motor stator is a side of the motor stator axially adjacent to the first gas bearing.
In some embodiments, the first gas bearing comprises a first thrust gas bearing axially supporting the motor rotor and a first radial gas bearing radially supporting the motor rotor;
The air supply flow passage includes:
the first air supply flow passage is arranged in the shell and is used for connecting an external air source and supplying working air provided by the external air source to the first radial air bearing;
And the second air supply flow passage is arranged in the shell and is used for connecting an external air source and supplying working air provided by the external air source to the first thrust air bearing.
In some embodiments, the first air supply flow passage and the second air supply flow passage are disposed apart from each other within the housing.
In some embodiments, the inlet of the first air supply flow passage on the housing and the inlet of the second air supply flow passage on the housing are located in opposite directions of the housing.
In some embodiments, the compressor further comprises a second gas bearing disposed within the housing and supporting the motor rotor;
The air supply flow passage further includes:
And the third air supply flow passage is arranged in the shell and is used for connecting an external air source and supplying working air provided by the external air source to the second air bearing.
In some embodiments, the third air supply flow passage is in communication with the first air supply flow passage and shares the same air inlet on the housing.
In some embodiments, the compressor further comprises:
the first-stage impeller and the second-stage impeller are respectively fixedly connected with two ends of the motor rotor;
A second gas bearing provided adjacent to the secondary impeller and radially supporting the motor rotor, and
The bearing seat is arranged in the shell and supports the second gas bearing;
the air supply runner is also communicated with the second air bearing and is used for supplying working air supplied by an external air source to the second air bearing, the bearing seat is provided with a bearing mounting hole for supporting the second air bearing, a vent hole group is arranged between the bearing mounting hole and the surface of the bearing seat, which is close to one side of the motor stator, and the vent hole group is used for guiding the working air flowing out from a gap between the second air bearing and the motor rotor to flow to one side of the bearing seat, which is close to the motor stator.
In some embodiments, the compressor further comprises an axial sealing mechanism disposed between the motor rotor and the bearing housing for forming a seal on one side of the second gas bearing in an axial direction.
In some embodiments, the axial sealing mechanism comprises a comb tooth sealing piece, wherein the comb tooth sealing piece is sleeved on the motor rotor and fixedly connected with the bearing seat, a ventilation groove group is arranged on a flange of one side, close to the second gas bearing, of the comb tooth sealing piece, and the ventilation groove group is at least partially communicated with the ventilation hole group.
In some embodiments, the set of vent holes includes at least one vent hole distributed along a circumferential direction of the bearing housing, the set of vent grooves includes at least one vent groove distributed along a circumferential direction of the comb seal, the number of vent holes is the same as the number of vent grooves, and each vent groove is aligned with each vent hole, respectively.
In some embodiments, the compressor is a centrifugal compressor.
In some embodiments, the first gas bearing is a hydrostatic gas bearing.
In some embodiments, the second gas bearing is a hydrostatic gas bearing.
Therefore, according to the embodiment of the disclosure, by providing the gas supply flow passage for supplying the working gas outside the housing to the first gas bearing in the housing and discharging the working gas flowing from the gap between the first gas bearing and the motor rotor through the gap between the motor stator and the motor rotor to the other side of the motor stator to the outside of the housing through the gas discharge device, the external working gas can be accurately supplied to the first gas bearing and absorbed by the gas discharge device after passing through the gap between the motor stator and the motor rotor, thereby eliminating the need for providing an additional gas collecting device and further optimizing the internal space of the compressor.
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 cross-sectional view of some embodiments of a compressor according to the present disclosure;
FIG. 2 is a schematic structural view of a bearing housing in some embodiments of a compressor according to the present disclosure;
FIG. 3 is a schematic view of section A-A of FIG. 2;
FIG. 4 is a schematic illustration of the structure of a comb seal in some embodiments of compressors according to the present disclosure;
fig. 5 is a schematic view of section B-B of fig. 4.
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 the components and steps set forth in these embodiments should be construed as merely illustrative, and not limiting unless specifically stated otherwise.
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, is a schematic cross-sectional view of some embodiments of a compressor according to the present disclosure. Referring to fig. 1, in some embodiments, the compressor includes a housing 2, a motor stator 3, a motor rotor 8, and a first gas bearing. The compressor may be a centrifugal compressor. In other embodiments, the compressor may be other types of compressors, such as screw compressors or sliding vane compressors. A motor stator 3 and a motor rotor 8 are both arranged in the housing 2. A gap is formed between the motor stator 3 and the motor rotor 8. At least one stage of impeller may be included within the housing 2. At least one stage of impeller is fixedly connected with the motor rotor 8 and can rotate along with the rotation of the motor rotor 8. A first gas bearing is arranged in the housing 2 and supports the motor rotor 8. The first gas bearing is preferably a hydrostatic gas bearing.
In some embodiments, the compressor further comprises a supply air flow passage. The air supply flow passage is arranged in the housing 2 and is used for connecting an external air source and supplying working air provided by the external air source to the first air bearing. An external gas source can enter the first gas bearing accurately and with little loss through the gas supply flow path.
Referring to FIG. 1, in some embodiments, the first gas bearing may include a first thrust gas bearing 12, 14 and a first radial gas bearing 11. The first thrust gas bearings 12 and 14 are located on the right and left sides, respectively, of a thrust disk 18 fixedly connected to the motor rotor, so that the motor rotor 8 is supported in the axial direction. The first radial gas bearing 11 is fitted over the motor rotor 8 and radially supports the motor rotor 8.
For the first gas bearing described above, the gas supply flow passages may include a first gas supply flow passage 10 and a second gas supply flow passage 16. A first gas supply flow passage 10 is provided in the housing 2 for connecting an external gas source and supplying working gas supplied from the external gas source to the first radial gas bearing 11. In fig. 1, the first air supply flow passage 10 may be opened inside a wall of the housing 2, and may include a plurality of sub flow passages in horizontal and vertical directions. These linear sub-channels can further reduce the gas along-path pressure loss. The end of the first gas supply flow passage 10 may be directly aligned with the outer ring of the first radial gas bearing 11, thereby enabling the working gas of the external gas source to be introduced into the first radial gas bearing 11 accurately and with less loss. The working gas introduced into the first radial gas bearing 11 can permeate into the gap between the first radial gas bearing 11 and the motor rotor 8 through the porous material of the bearing, thereby forming a static pressure gas supporting effect.
A second air supply flow passage 16 is provided in the housing 2 for connecting an external air supply and supplying working air supplied from the external air supply to the first thrust gas bearings 12, 14. A part of the second supply flow channel 16 may be opened inside the wall of the casing 2, and its tip end is aligned with the right end face of the first thrust gas bearing 12, while another part may be opened inside the diffuser 13 that is disposed in close contact with the first thrust gas bearing 14, and its tip end is aligned with the left end face of the first thrust gas bearing 14, so that the working gas of the external gas source can be introduced into the first thrust gas bearings 12, 14 accurately with less loss. The second gas supply flow passage 16 may include a plurality of sub-flow passages in horizontal and vertical directions, and these sub-flow passages are linear in shape, which may further reduce the along-path pressure loss of the gas. The working gas introduced into the first thrust gas bearings 12 and 14 can penetrate into the gaps between the first thrust gas bearings 12 and 14 and the thrust disk 18 respectively through the porous material of the bearings, thereby forming a static pressure gas supporting effect.
Considering that the gas pressures required for the thrust gas bearing and the radial gas bearing may be different, in some embodiments the first gas supply flow passage 10 and the second gas supply flow passage 16 are arranged spaced apart from each other within the housing 2. In other words, the first air supply flow passage 10 and the second air supply flow passage 16 are independent from each other and do not directly communicate in the inner flow passage of the housing. For example, the air inlet 9 of the first air supply flow passage 10 outside the housing and the air inlet 1 of the second air supply flow passage 16 outside the housing are provided at different positions of the housing 2, respectively, and the first air supply flow passage 10 is not directly communicated with the second air supply flow passage 16. Thus, the air inlet 9 can be connected with external air sources with different pressures with the air inlet 1, thereby meeting the working gas supply of the gas bearing which accords with working conditions, and leading the structure of the air supply flow passage to be simpler.
In order to facilitate connection of an external air source to the air inlet and to reduce interference problems when connecting external pipes, it is preferred that the air inlet 9 of the first air supply flow passage 10 on the housing 2 and the air inlet 1 of the second air supply flow passage 16 on the housing 2 are arranged in opposite directions of the housing 2, for example below and above the housing 2.
In some embodiments, the compressor further comprises an exhaust. With reference to the indication of the flow direction of the air flow indicated by the arrows in fig. 1, the suction opening of the exhaust device is located in the housing 2, which is capable of discharging the working air flowing from the gap between the first air bearing and the motor rotor 8, and via the gap between the motor stator 3 and the motor rotor 8 to the first side of the motor stator 3 (i.e. the side of the motor stator 3 axially remote from the first air bearing, corresponding to the region B in fig. 1), out of the housing 2. Thus, the working gas externally input into the compressor can be more easily discharged from the inside of the compressor to ensure the stability of the supplied gas, and a special device for collecting the working gas is not needed, so that the internal space of the compressor is optimized. In addition, the cooling effect of the motor stator and the motor rotor can be realized through the flowing of the working gas in the gap between the stator and the rotor.
In fig. 1, a cooling gas flow passage 15 may be provided between the housing 2 and the motor stator 3. The outlet of the cooling gas flow channel 15 is located at the second side of the motor stator 3 (i.e. the side of the motor stator 3 axially close to the first gas bearing). In this way, the cooling gas entering the cooling gas flow passage 15 can flow out from the outlet of the cooling gas flow passage 15 and be mixed with the working gas flowing out from the gap between the first gas bearing and the motor rotor 8 at the second side of the motor stator (corresponding to the region a in fig. 1), and the mixed gas medium flows to the first side of the motor stator 3 (corresponding to the region B in fig. 1) via the gap between the motor stator 3 and the motor rotor 8.
After the cooling gas and the working gas are mixed, the cooling effect of the motor stator 3 and the motor rotor 8 can be realized when the cooling gas passes through between the motor stator 3 and the motor rotor 8, and the cooling gas can be absorbed by the exhaust device and exhausted outside the shell, so that the gas circulation inside and outside the compressor is smoother, and the stability of the operation inside the compressor is ensured. The cooling gas and the working gas may be the same medium or different mediums. Preferably, the cooling gas and the working gas are both refrigerants compressed by the compressor.
Referring to fig. 1, in some embodiments, the compressor includes two stages of impellers fixedly connected to both ends of the motor rotor 8, respectively, and the first thrust gas bearings 12, 14 and the first radial gas bearing 11 of the first gas bearings are disposed on a side of the motor rotor 8 adjacent to the second stage impeller 20 with respect to the first stage impeller 19. The compressor further comprises a second gas bearing 6, which second gas bearing 6 supports said motor rotor 8 at a position of the secondary impeller 20 on the side of the first impeller 19. The second gas bearing is preferably a hydrostatic gas bearing.
For mounting the second gas bearing 6, the second gas bearing 6 may be supported by a bearing housing 5 arranged in the housing 2. The air supply flow passage may further comprise a third air supply flow passage 17 provided in said housing 2. The third gas supply flow passage 17 is used for connecting an external gas source and supplying working gas supplied from the external gas source to the second gas bearing 6.
In view of the fact that the conditions of the first radial gas bearing and the second gas bearing 6, which are also radial gas bearings, are relatively close, the third gas supply flow channel 17 and the second gas supply flow channel 16 can be made to communicate with each other and share the same gas inlet on the housing 2, so as to simplify the gas supply flow channels.
Referring to fig. 1-3, in some embodiments, a gas supply flow passage 10 may be in communication with the second gas bearing 6 (either directly or via a flow passage 53 provided in the bearing housing 5) for supplying working gas provided by the external gas source to the second gas bearing 6. The bearing housing 5 has a bearing mounting hole 52 for supporting the second gas bearing 6, and a vent hole group is provided between the bearing mounting hole 52 and a surface of the bearing housing 5 on a side close to the motor stator 3. The set of ventilation holes may comprise at least one ventilation hole 51 distributed along the circumference of the bearing housing 5. The set of ventilation holes is capable of guiding the working gas flowing out of the gap between the second gas bearing 6 and the motor rotor 8 to the region B of the bearing housing 5 on the side close to the motor stator 3. The working gas entering the region B can be absorbed by the exhaust means to be discharged outside the housing.
Referring to fig. 1, in some embodiments, the compressor further comprises an axial sealing mechanism provided between the motor rotor 8 and the bearing housing 5 for forming a seal on one side of the second gas bearing 6 in the axial direction. Referring to fig. 4-5, in some embodiments, the axial sealing mechanism includes a comb seal 7. The comb seal 7 is sleeved on the motor rotor 8 and fixedly connected with the bearing seat 5, and a ventilation groove group is arranged on a flange 74 of one side of the comb seal 7, which is close to the second gas bearing 6, and is at least partially communicated with the ventilation groove group. The comb teeth seal 7 is further provided with comb teeth 71 arranged in the axial direction and assembly holes 72 for assembly with the bearing housing 5.
The vent groove group may include at least one vent groove group distributed in the circumferential direction of the comb seal 7, and in order to smoothly discharge the working gas flowing out of the gap between the second gas bearing 6 and the motor rotor 8, it is preferable that the number of vent holes 51 is the same as the number of vent grooves 71, for example, 5 (or 3 or 7, etc.), and each vent groove 71 is aligned with each vent hole 51, respectively.
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 (13)
1. A compressor, comprising:
A housing (2);
A motor stator (3) and a motor rotor (8), both arranged in the housing (2), and
A first gas bearing arranged in the housing (2) and supporting the motor rotor (8);
Characterized in that the compressor further comprises:
a gas supply flow passage provided in the housing (2) for connecting an external gas source and supplying a working gas supplied from the external gas source to the first gas bearing, and
An exhaust device, the air suction port of which is positioned in the shell (2) and is used for discharging working gas flowing out from the gap between the first gas bearing and the motor rotor (8) and flowing to the first side of the motor stator (3) through the gap between the motor stator (3) and the motor rotor (8) to the outside of the shell (2);
Wherein a first side of the motor stator (3) is a side of the motor stator (3) axially remote from the first gas bearing, the first gas bearing comprises first thrust gas bearings (12, 14) axially supporting the motor rotor (8) and first radial gas bearings (11) radially supporting the motor rotor (8), the gas supply flow path comprises a first gas supply flow path (10) which is arranged in the housing (2) and is used for connecting an external gas source and supplying working gas provided by the external gas source to the first radial gas bearings (11), and a second gas supply flow path (16) which is arranged in the housing (2) and is used for connecting an external gas source and supplying working gas provided by the external gas source to the first thrust gas bearings (12, 14).
2. Compressor according to claim 1, characterized in that a cooling gas flow channel (15) is provided between the housing (2) and the motor stator (3), the outlet of the cooling gas flow channel (15) being located at the second side of the motor stator (3) so that the cooling gas flowing out of the outlet of the cooling gas flow channel (15) can be mixed with the working gas flowing out of the gap of the first gas bearing and the motor rotor (8) at the second side of the motor stator (3) and then flows to the first side of the motor stator (3) via the gap of the motor stator (3) and the motor rotor (8);
Wherein the second side of the motor stator (3) is the side of the motor stator (3) axially close to the first gas bearing.
3. The compressor according to claim 1, characterized in that the first air supply flow channel (10) and the second air supply flow channel (16) are arranged separately from each other within the housing (2).
4. A compressor according to claim 3, characterized in that the inlet opening of the first supply flow channel (10) on the housing (2) and the inlet opening of the second supply flow channel (16) on the housing (2) are located in opposite directions of the housing (2).
5. The compressor according to claim 1, further comprising a second gas bearing (6) disposed within the housing and supporting the motor rotor (8);
The air supply flow passage further includes:
and a third air supply flow passage (17) is arranged in the shell (2) and is used for connecting an external air source and supplying working air provided by the external air source to the second air bearing (6).
6. Compressor according to claim 5, characterized in that said third air supply flow channel (17) is in communication with said first air supply flow channel (10) and shares the same air inlet on the housing (2).
7. The compressor of claim 1, further comprising:
The primary impeller (19) and the secondary impeller (20) are fixedly connected with two ends of the motor rotor respectively;
A second gas bearing (6) provided adjacent to the secondary impeller (20) and supporting the motor rotor (8) in a radial direction, and
A bearing seat (5) which is arranged in the shell (2) and supports the second gas bearing (6);
The air supply flow channel is also communicated with the second air bearing (6) and is used for supplying working air supplied by an external air source to the second air bearing (6), the bearing seat (5) is provided with a bearing mounting hole (52) for supporting the second air bearing (6), a vent hole group is arranged between the bearing mounting hole (52) and the surface of the bearing seat (5) close to one side of the motor stator (3) and is used for guiding working air flowing out of a gap between the second air bearing (6) and the motor rotor (8) to flow to one side of the bearing seat (5) close to the motor stator (3).
8. The compressor according to claim 7, further comprising an axial sealing mechanism provided between the motor rotor (8) and the bearing housing (5) for forming a sealing action on one side in the axial direction of the second gas bearing (6).
9. The compressor of claim 8, wherein the axial sealing mechanism comprises a comb seal (7), the comb seal (7) is sleeved on the motor rotor (8) and fixedly connected with the bearing seat (5), and a ventilation groove group is arranged on a flange (74) of one side of the comb seal (7) close to the second gas bearing (6), and is at least partially communicated with the ventilation groove group.
10. The compressor according to claim 9, characterized in that the set of ventilation holes comprises at least one ventilation hole (51) distributed along the circumference of the bearing housing (5), the set of ventilation grooves comprises at least one ventilation groove (71) distributed along the circumference of the comb seal (7), the number of ventilation holes (51) is the same as the number of ventilation grooves (71), and each ventilation groove (71) is aligned with each ventilation hole (51) respectively.
11. The compressor of claim 1, wherein the compressor is a centrifugal compressor.
12. The compressor of claim 1, wherein the first gas bearing is a hydrostatic gas bearing.
13. The compressor of claim 7, wherein the second gas bearing is a hydrostatic gas bearing.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811593234.6A CN111365254B (en) | 2018-12-25 | 2018-12-25 | Compressors for optimizing interior space |
| PCT/CN2019/113991 WO2020134517A1 (en) | 2018-12-25 | 2019-10-29 | Compressor |
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| CN201811593234.6A CN111365254B (en) | 2018-12-25 | 2018-12-25 | Compressors for optimizing interior space |
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| CN111365254B true CN111365254B (en) | 2025-03-07 |
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| CN113123983A (en) * | 2021-04-07 | 2021-07-16 | 西安交通大学 | Two-stage high-speed centrifugal air compressor with double cooling systems for fuel cell |
| CN114483611B (en) * | 2022-01-21 | 2024-02-13 | 扬州大学 | Main shaft structure of dynamic pressure floating ring and magnetic bearing supporting fuel cell air compressor |
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| CN209340163U (en) * | 2018-12-25 | 2019-09-03 | 珠海格力电器股份有限公司 | Compressor for optimizing internal space |
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| FR2602834A1 (en) * | 1986-08-13 | 1988-02-19 | Cit Alcatel | Turbomolecular pump on gas bearings |
| KR100356506B1 (en) * | 2000-09-27 | 2002-10-18 | 엘지전자 주식회사 | Turbo compressor |
| JP5125684B2 (en) * | 2008-03-28 | 2013-01-23 | 株式会社Ｉｈｉ | Turbocharger |
| SG11201403813TA (en) * | 2012-01-03 | 2014-09-26 | New Way Machine Components Inc | Air bearing for use as seal |
| US10598222B2 (en) * | 2012-01-03 | 2020-03-24 | New Way Machine Components, Inc. | Air bearing for use as seal |
| CN103326512B (en) * | 2013-05-16 | 2015-04-15 | 西安交通大学 | Centrifugal air compressor cooling structure driven by ultra-high-speed permanent magnet motor |
| US9732766B2 (en) * | 2014-02-19 | 2017-08-15 | Honeywell International Inc. | Electric motor-driven compressor having a heat shield forming a wall of a diffuser |
| CN106015032B (en) * | 2016-06-28 | 2018-05-22 | 杭州万辰机电科技有限公司 | Centrifugal compressor |
| JP6200127B1 (en) * | 2016-12-09 | 2017-09-20 | 三菱重工コンプレッサ株式会社 | Compressor system with gas bearing and method for supplying gas to a compressor with gas bearing |
| US11274679B2 (en) * | 2017-02-14 | 2022-03-15 | Danfoss A/S | Oil free centrifugal compressor for use in low capacity applications |
| CN107634611A (en) * | 2017-10-18 | 2018-01-26 | 李记东 | Motor with novel cooling structure and fluid machine including it |
| CN108775289B (en) * | 2018-05-23 | 2020-03-17 | 北京石油化工学院 | Self-cooling air suspension compressor with air storage function |
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