CN219119403U - Compressor and refrigerant circulation system - Google Patents

Abstract

The application provides a compressor and refrigerant circulation system. The compressor of this application includes: the compressor comprises a shell, a stator, a rotor, a radial hydrostatic bearing, a bearing seat and a diffuser, wherein the shell is provided with an air outlet, the radial hydrostatic bearing is sleeved on the rotor in an axially movable mode, a first gap is formed between the radial hydrostatic bearing and the outer surface of the rotor, and the compressor further comprises at least one of the following: the first exhaust cavity is positioned between the first end face of the radial hydrostatic bearing and the first surface of the bearing seat, and the first groove is positioned on the first end face and/or the first surface and communicated with the first exhaust cavity and the air outlet hole; the second exhaust cavity is positioned between the second end face of the radial hydrostatic bearing and the second surface of the diffuser, and the second groove is positioned on the second end face and/or the second surface and communicated with the second exhaust cavity and the air outlet hole. Based on this, can promote the exhaust smoothness nature, improve the operational reliability of compressor.

Description

Compressor and refrigerant circulation system

Technical Field

The application relates to the technical field of compressors, in particular to a compressor and a refrigerant circulation system.

Background

The static pressure gas bearing is widely applied to compressors due to the characteristics of small running resistance, high mechanical precision, strong bearing capacity, no dry friction in the start-stop stage and the like. For example, in some compressors, radial hydrostatic bearings are provided to support the rotor, and in order to reduce the risk of seizing the shaft, radial hydrostatic bearings are also provided to be axially movable.

However, in practice it has been found that in the case of a radial hydrostatic bearing which is axially movable, the gas of the radial hydrostatic bearing for forming the gas film has the problem of a poor evacuation, which affects the bearing capacity of the radial hydrostatic bearing, resulting in a reduced operational reliability of the compressor.

Disclosure of Invention

One technical problem to be solved by the present application is: and the exhaust smoothness of the radial hydrostatic bearing capable of axially moving is improved, and the operation reliability of the compressor is improved.

In order to solve the above technical problem, the present application provides a compressor, which includes:

a housing;

the stator is fixedly arranged in the shell;

the rotor is rotatably arranged in the stator in a penetrating way;

the bearing assembly comprises a radial hydrostatic bearing, a bearing seat and a diffuser, wherein the radial hydrostatic bearing is sleeved on the rotor in an axially movable manner, a first gap is formed between the radial hydrostatic bearing and the outer surface of the rotor so as to allow gas to enter the rotor to form a gas film, the bearing seat is sleeved outside the radial hydrostatic bearing, and the diffuser is sleeved on the rotor and is positioned at one side of the radial hydrostatic bearing far away from the stator; and

The exhaust gas circuit is used for discharging the gas in the first gap to the outside of the shell, and comprises a gas outlet hole, wherein the gas outlet hole is arranged on the shell and is communicated with the outside of the shell, and the exhaust gas circuit further comprises at least one of the following components:

the first exhaust cavity is positioned between the first end face of the radial hydrostatic bearing facing the stator and the first surface opposite to the first end face of the bearing seat, and the first groove is positioned on the first end face and/or the first surface and communicated with the first exhaust cavity and the air outlet;

the second exhaust cavity is positioned between a second end face of the radial hydrostatic bearing facing the diffuser and a second surface of the diffuser opposite to the second end face, and the second groove is positioned on the second end face and/or the second surface and communicated with the second exhaust cavity and the air outlet.

In some embodiments, the exhaust gas path includes at least two first grooves spaced apart along the circumference of the rotor; and/or the exhaust gas path comprises at least two second grooves which are arranged at intervals along the circumferential direction of the rotor.

In some embodiments, the exhaust gas path includes a first exhaust gas chamber, a first recess, a second exhaust gas chamber, and a second recess, and the exhaust gas path further includes a communication hole that communicates the first recess and the second exhaust gas chamber or the second recess, and the second recess communicates the second exhaust gas chamber and the gas outlet.

In some embodiments, the radial hydrostatic bearing includes a sleeve and a carrier, the sleeve is sleeved outside the carrier, the first gap is located between the carrier and the rotor, and the communication hole is located on the sleeve.

In some embodiments, the air outlet is located on a side of the bearing housing remote from the diffuser, and the exhaust gas path further includes a bleed hole disposed on the bearing housing and/or on the housing and communicating the first and/or second exhaust chambers with the air outlet.

In some embodiments, the compressor includes a first gas supply path that communicates with the first gap and supplies gas to the first gap to form a gas film.

In some embodiments, the first air supply path includes an air inlet hole, a first air supply channel and a first air intake channel, the air inlet hole is disposed on the housing and communicates with the exterior of the housing, the first air supply channel is disposed on the bearing seat and communicates with the air inlet hole, and the first air intake channel is disposed on the radial hydrostatic bearing and communicates with the first air supply channel and the first gap.

In some embodiments, the radial hydrostatic bearing comprises a sleeve and a carrier, the sleeve is sleeved outside the carrier, the first gap is located between the carrier and the outer surface of the rotor, the first air inlet channel comprises a first channel section and a second channel section, the first channel section is arranged on the sleeve and communicated with the first air inlet channel, and the second channel section is arranged on the carrier and communicated with the first channel section and the first gap.

In some embodiments, the first channel section includes a first annular groove disposed on an outer surface of the sleeve in communication with the first air supply channel and a vent disposed at a bottom of the first annular groove in communication with the first annular groove and the second channel section; and/or the second channel section comprises a second annular groove and a first throttling hole, the second annular groove is arranged on the outer surface of the carrier and is communicated with the first channel section, and the first throttling hole is arranged at the bottom of the second annular groove and is communicated with the second annular groove and the first gap.

In some embodiments, the first channel segment comprises at least two vent holes spaced apart along the circumference of the first annular groove; and/or the second channel section comprises at least two first orifices, which are arranged at intervals along the axial direction and/or the circumferential direction of the second annular groove.

In some embodiments, the compressor includes two bearing assemblies disposed at axial ends of the rotor.

In some embodiments, the air supply air circuit includes two first air supply air circuits that respectively supply air for the first gaps of the radial hydrostatic bearings of the two bearing assemblies.

In some embodiments, a thrust disc is provided on the rotor, the thrust disc being located on a side of the radial hydrostatic bearing remote from the diffuser, and the compressor further comprises at least one of:

the first hydrostatic thrust bearing is sleeved on the rotor and arranged on one side of the thrust disk, which is close to the radial hydrostatic bearing, a second gap is arranged between the first hydrostatic thrust bearing and the adjacent axial end face of the thrust disk, the compressor comprises a second air supply channel, the second air supply channel is communicated with the second gap so as to supply air to the second gap to form an air film, and the second gap is communicated with a first exhaust cavity of the exhaust channel;

the second hydrostatic thrust bearing is sleeved on the rotor and arranged on one side of the thrust disc far away from the radial hydrostatic bearing, a third gap is arranged between the second hydrostatic thrust bearing and the adjacent axial end face of the thrust disc, the compressor comprises a third air supply air passage, the third air supply air passage is communicated with the third gap to supply air to the third gap to form an air film, and the third gap is communicated with the air outlet hole.

In some embodiments, the second air supply path includes a second air supply channel disposed on the bearing seat and communicating the first air supply channel of the first air supply path of the compressor with the second gap; and/or the third air supply channel comprises a third air supply channel which is arranged on the bearing seat and is communicated with the first air supply channel and the third gap of the first air supply channel of the compressor.

In some embodiments, the second air supply channel further comprises a first air supply cavity and a second orifice, the first air supply cavity is positioned between the first hydrostatic thrust bearing and the adjacent axial end face of the bearing seat and is communicated with the second air supply channel, and the second orifice is arranged on the first hydrostatic thrust bearing and is communicated with the first air supply cavity and the second gap; and/or the third air supply channel comprises a second air supply cavity and a third throttling hole, the second air supply cavity is positioned between the second hydrostatic thrust bearing and the adjacent axial end face of the sealing cover and is communicated with the third air supply channel, the third throttling hole is arranged on the second hydrostatic thrust bearing and is communicated with the second air supply cavity and the third gap, and the sealing cover is sleeved on the rotor and is positioned on one side of the second hydrostatic thrust bearing far away from the radial hydrostatic bearing.

In addition, the application also provides a refrigerant circulation system, which comprises the compressor of any embodiment of the application.

In some embodiments, the refrigerant circulation system is an air conditioning system.

By arranging at least one of the first exhaust cavity, the first groove, the second exhaust cavity and the second groove, the exhaust smoothness can be effectively improved, the bearing capacity and the bearing stability can be improved, and the operation reliability of the compressor can be improved.

Other features of the present application and its advantages will become apparent from the following detailed description of exemplary embodiments of the present application, which proceeds with reference to the accompanying drawings.

Drawings

In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described below, it being obvious that the drawings in the following description are only some embodiments of the present application, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

Fig. 1 is a schematic structural diagram of a compressor according to an embodiment of the present application.

Fig. 2 is an enlarged partial schematic view of fig. 1 at a left radial hydrostatic bearing, a first hydrostatic thrust bearing, and a second hydrostatic thrust bearing.

Fig. 3 is a schematic perspective view of a left radial hydrostatic bearing in an embodiment of the present application.

Fig. 4 is a cut-away perspective view of a left radial hydrostatic bearing in an embodiment of the present application.

Fig. 5 is a schematic structural view of a sleeve of a left radial hydrostatic bearing in an embodiment of the present application.

Fig. 6 is a schematic structural view of a carrier of the left radial hydrostatic bearing in the embodiment of the present application.

Fig. 7 is a schematic perspective view of a left bearing seat in an embodiment of the present application.

Fig. 8 is a right side view of a left diffuser in the practice of the present application.

Reference numerals illustrate:

10. a compressor;

1. a housing;

2. a stator;

3. a rotor; 31. a thrust plate;

4. a bearing assembly; 41. a radial hydrostatic bearing; 411. a sleeve; 412. a carrier; 413. a cylinder; 414. a limit flange; 415. a main body; 416. a stop ring; 417. a first end face; 418. a second end face; 419. a first gap; 42. a bearing seat; 421. a base; 422. a first boss; 423. a second boss; 424. a first mounting groove; 425. a second mounting groove; 426. a first surface; 43. a diffuser; 431. a second surface;

5. a first hydrostatic thrust bearing; 51. A second gap; 52. A first slit;

6. a second hydrostatic thrust bearing; 61. A third gap; 62. A second slit;

7. an air supply path; 71. a first air supply path; 711. an air inlet hole; 712. a first air supply channel; 713. a first air intake passage; 714. a first channel segment; 715. a second channel segment; 716. a first annular groove; 717. a vent hole; 718. a second annular groove; 719. a first orifice; 72. a second air supply path; 721. a second air supply channel; 722. a first air supply chamber; 723. a third annular groove; 724. a second orifice; 73. a third air supply path; 731. a third air supply channel; 732. a second air supply chamber; 733. a fourth annular groove; 734. a third orifice;

8. An exhaust gas path; 81. a first exhaust chamber; 82. a second exhaust chamber; 83. a communication hole; 84. an air outlet hole; 85. a first groove; 86. a second groove; 87. an air vent;

91. a seal; 92. an impeller; 93. a volute; 94. a locking member; 95. a bearing cavity; 96. a motor cavity; 97. and (5) sealing the cover.

Detailed Description

The following description of the embodiments of the present application will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all, of the embodiments of the present application. The following description of at least one exemplary embodiment is merely exemplary in nature and is in no way intended to limit the application, its application, or uses. All other embodiments, which can be made by one of ordinary skill in the art without undue burden from the inventors, are within the scope of the present application, based on the embodiments 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.

In the description of the present application, it should be understood that, the terms "first," "second," etc. are used for defining the components, and are merely for convenience in distinguishing the corresponding components, and if not otherwise stated, the terms are not to be construed as limiting the scope of the present application.

In addition, the technical features described below in the different embodiments of the present application may be combined with each other as long as they do not collide with each other.

The compressor is an important component of a refrigerant circulation system of an air conditioner and the like, and is connected with the condenser, the evaporator, the throttling element and the like to form a refrigerant circulation loop. When the refrigerating device works, the compressor sucks working medium steam with lower pressure from the evaporator, the working medium steam is sent to the condenser after the pressure of the working medium steam is increased, the working medium steam is condensed into liquid with higher pressure in the condenser, the liquid is sent to the evaporator after being throttled by the throttling element to become liquid with lower pressure, the liquid is absorbed in the evaporator and evaporated to become steam with lower pressure, and then the steam is sent to the inlet of the compressor, so that the refrigerating cycle is completed.

Referring to fig. 1, a compressor 10 generally includes a housing 1, a stator 2, a rotor 3, and the like.

The interior of the shell 1 is provided with a cavity, and a mounting space is provided for other structural components such as the stator 2, the rotor 3 and the like.

The stator 2 and the rotor 3 are both mounted in the housing 1. Wherein the stator 2 is fixedly arranged in the housing 1. For example, the stator 2 may be shrink-fit to the inner surface of the housing 1. The rotor 3 is rotatably disposed in the housing 1 and penetrates the stator 2, i.e., the rotor 3 is rotatably disposed in the stator 2.

The rotor 3 rotates at a high speed in the working process, and is matched with the stator 2 to realize the conversion from electric energy to mechanical energy.

For a reliable support of the rotors 3, some of the rotors 3 are provided with gas bearings.

A gas bearing is a bearing that receives a load using a gas film formed by gas. Compared with other types of bearings, the gas bearing has the advantages of no oil, no pollution, small running resistance, simple structure, high mechanical precision, low heat productivity, long service life and the like, and can make up the defects of the traditional liquid bearing, the sliding bearing and the rolling bearing, so that the gas bearing is widely applied to high-speed rotating machinery and precision machining machinery.

The gas bearing can be divided into a plurality of types such as a static pressure gas bearing, a dynamic and static pressure hybrid bearing and the like according to the different working principles of the bearing. The dynamic pressure gas bearing utilizes the high-speed moving rotor to drive fluid to move, a dynamic pressure gas film is formed, the bearing capacity of the gas film is relatively small, and meanwhile, dry friction is easy to occur at the low-speed stage of starting and stopping due to insufficient bearing capacity. The static pressure gas bearing forms a static pressure gas film by utilizing external high-pressure gas through the restrictor, the dry friction phenomenon can not occur in the start-stop stage, and meanwhile, the static pressure gas film has strong bearing capacity. The hydrostatic gas bearing has remarkable characteristics compared with the hydrodynamic gas bearing, and is widely applied to the compressor such as a centrifugal compressor.

In addition, depending on the direction in which the bearing is loaded, the hydrostatic gas bearing may be classified into a radial hydrostatic bearing, an axial hydrostatic bearing, and the like. Wherein, radial hydrostatic bearing mainly bears radial load. The axial hydrostatic bearing is mainly subjected to axial loads, also called hydrostatic thrust bearings.

In the conventional scheme, the radial hydrostatic bearing in the compressor is usually of an integral structure, and a gap between the radial hydrostatic bearing and the outer surface of the rotor 3 is usually small, so that the radial hydrostatic bearing cannot move axially on the rotor 3, and in this case, the assembly difficulty is high, and the shaft clamping phenomenon easily occurs in the assembly and operation processes.

In order to reduce the difficulty of assembly and the risk of seizing, in some related art, a radial hydrostatic bearing is provided so as to be axially movable on the rotor 3.

However, it has been found that the radial hydrostatic bearings are axially movable, while indeed reducing assembly difficulties and the risk of seizing, and at the same time presenting problems of unsmooth exhaust.

As mentioned above, the radial hydrostatic bearing requires external air supply to form an air film, and the corresponding air needs to be exhausted after forming the air film, and if the exhaust is not smooth, the differential pressure distribution is affected, the bearing load is affected, and the operation reliability of the compressor is reduced. And when the radial hydrostatic bearing axially moves to two limit positions, the radial hydrostatic bearing axially abuts against the bearing seat and the diffuser which are positioned on two axial sides of the radial hydrostatic bearing, so that an exhaust gas path is blocked, and the exhaust gas is not smooth.

Therefore, the scheme that the radial hydrostatic bearing can axially move can influence the operation reliability of the compressor by influencing the smoothness of exhaust.

Based on the discovery, the application provides a compressor to solve the problem that the exhaust is unsmooth and the operational reliability is lower under the condition that radial hydrostatic bearings can axially move.

Fig. 1 to 8 exemplarily show the structure of a compressor in the present application.

Referring to fig. 1-8, in the present application, a compressor 10 includes a housing 1, a stator 2, a rotor 3, a bearing assembly 4, and an exhaust gas path 8. Wherein the stator 2 is fixedly arranged in the housing 1. The rotor 3 is rotatably provided through the stator 2. The bearing assembly 4 includes a radial hydrostatic bearing 41, a bearing housing 42, and a diffuser 43. The radial hydrostatic bearing 41 is axially movably sleeved on the rotor 3, and a first gap 419 is arranged between the radial hydrostatic bearing and the outer surface of the rotor 3 so as to allow gas to pass in to form a gas film. The bearing seat 42 is sleeved outside the radial hydrostatic bearing 41. The diffuser 43 is sleeved on the rotor 3 and is positioned on the side of the radial hydrostatic bearing 41 away from the stator 2. The exhaust gas path 8 is used for exhausting the gas in the first gap 419 to the outside of the casing 1, and includes an air outlet 84, the air outlet 84 is disposed on the casing 1 and is communicated with the outside of the casing 1, and the exhaust gas path 8 further includes at least one of the following:

A first exhaust chamber 81 and a first groove 85, the first exhaust chamber 81 being located between a first end face 417 of the radial hydrostatic bearing 41 facing the stator 2 and a first surface 426 of the bearing housing 42 opposite the first end face 417, the first groove 85 being located on the first end face 417 and/or the first surface 426 and communicating the first exhaust chamber 81 with the air outlet 84;

a second exhaust chamber 82 and a second groove 86, the second exhaust chamber 82 being located between a second end surface 418 of the radial hydrostatic bearing 41 facing the diffuser 43 and a second surface 431 of the diffuser 43 opposite the second end surface 418, the second groove 86 being located on the second end surface 418 and/or the second surface 431 and communicating the second exhaust chamber 82 with the exhaust aperture 84.

Based on the first groove 85 and/or the second groove 86, the exhaust smoothness can be effectively improved, so that the bearing capacity and the bearing stability are improved, and the operation reliability of the compressor 10 is improved.

Wherein, based on the first groove 85 provided, when the radial hydrostatic bearing 41 moves to the first end face 417 thereof in the axial direction to abut against the first surface 426 of the bearing seat 42, the gas in the first exhaust chamber 81 is not blocked, but can still flow outwards through the recessed first groove 85, thereby effectively preventing the radial hydrostatic bearing 41 from abutting against the bearing seat 42 to cause unsmooth exhaust, so that even if the radial hydrostatic bearing 41 moves to the limit position towards the side of the stator 2, the gas in the first gap 419 can still be smoothly and timely exhausted, thus being beneficial to improving the exhaust smoothness, bearing capacity and bearing stability and improving the operation reliability of the compressor 10.

In addition, based on the second groove 86, when the radial hydrostatic bearing 41 moves axially until the second end surface 418 thereof abuts against the second surface 431 of the diffuser 43, the gas in the second exhaust chamber 82 is not blocked, but can still flow outwards through the recessed second groove 86, so that the radial hydrostatic bearing 41 is effectively prevented from abutting against the diffuser 43 to cause unsmooth exhaust, and even if the radial hydrostatic bearing 41 moves to the limit position towards the diffuser 43, the gas in the first gap 419 can still be smoothly and timely exhausted, thereby being beneficial to improving the exhaust smoothness, bearing capacity and bearing stability and operation reliability of the compressor 10.

It can be seen that by providing at least one of the first exhaust chamber 81 and the first groove 85 and the second exhaust chamber 82 and the second groove 86, the exhaust smoothness can be effectively improved, the bearing capacity and the bearing stability can be improved, and the operation reliability of the compressor 10 can be improved.

Wherein, only the first exhaust chamber 81 and the first groove 85 may be provided, only the second exhaust chamber 82 and the second groove 86 may be provided, or the first exhaust chamber 81 and the first groove 85 and the second exhaust chamber 82 and the second groove 86 may be provided at the same time. When only the first exhaust chamber 81 and the first groove 85 or the second exhaust chamber 82 and the second groove 86 are provided, the gas in the first gap 419 is discharged from only one of the axial both sides of the radial hydrostatic bearing 41. When the first exhaust chamber 81 and the first groove 85 and the second exhaust chamber 82 and the second groove 86 are provided at the same time, the gas in the first gap 419 can be exhausted from both sides of the radial hydrostatic bearing 41 in the axial direction at the same time, so that the exhaust efficiency is higher, the exhaust smoothness is better, and the operation reliability of the compressor 10 is more improved.

In the case that the exhaust gas path 8 includes the first exhaust gas chamber 81, the first groove 85, the second exhaust gas chamber 82, and the second groove 86 at the same time, the first exhaust gas chamber 81 and the first groove 85 located at two axial sides of the radial hydrostatic bearing 41 and the second exhaust gas chamber 82 and the second groove 86 may be two exhaust gas paths that are independent of each other and respectively communicate with the air outlet hole 84, or the two exhaust gas paths may also communicate with each other, where one path communicates with the air outlet hole 84 through the other path.

For example, referring to fig. 1 and 2, in some embodiments, the exhaust gas path 8 includes a first exhaust gas chamber 81, a first groove 85, a second exhaust gas chamber 82, and a second groove 86, and the exhaust gas path 8 further includes a communication hole 83, the communication hole 83 communicating the first groove 85 and the second exhaust gas chamber 82 or the second groove 86, the second groove 86 communicating the second exhaust gas chamber 82 and the gas outlet 84.

In the above-described configuration, the first exhaust gas path (the first exhaust gas chamber 81 and the first groove 85) and the second exhaust gas path (the second exhaust gas chamber 82 and the second groove 86) located on both sides in the axial direction of the radial hydrostatic bearing 41 are not independent of each other, but are communicated with each other, specifically, the first exhaust gas path is communicated with the second exhaust gas path and is communicated with the gas outlet 84 through the second exhaust gas path, at this time, the first groove 85 is communicated with the gas outlet 84 through the communication hole 83 and the second exhaust gas path, so that, referring to the arrow in fig. 2, the gas after entering the first gap 419 to form the gas film flows in two paths, one of which flows toward the stator 2 side, flows toward the first exhaust gas path, enters the first exhaust gas chamber 81, the other of which flows toward the diffuser 43 side, flows toward the second exhaust gas path, enters the second exhaust gas chamber 82, and the gas entering the first exhaust gas chamber 81 flows out through the second groove 86 together via the first groove 85 and the communication hole 83, and is discharged to the outside of the casing 1 through the second groove 86.

In the above-described exhaust process, since the first exhaust gas path and the second exhaust gas path include the first groove 85 and the second groove 86, respectively, the first exhaust gas path and the second exhaust gas path are not blocked by the movement of the radial hydrostatic bearing, and therefore smooth exhaust in the axial movement process of the radial hydrostatic bearing 41 can be achieved. Further, since the first exhaust gas passage and the second exhaust gas passage are communicated by the communication hole 83, the first exhaust gas passage and the second exhaust gas passage do not need to be respectively communicated with the gas outlet holes 84, and therefore the structure of the entire exhaust gas passage 8 can be effectively simplified.

Therefore, the above scheme can improve the exhaust smoothness and the operation reliability of the compressor 10 based on a simpler structure.

Here, the communication hole 83 may be provided on the radial hydrostatic bearing 41. As an example, referring to fig. 1 and 2, in some embodiments, the radial hydrostatic bearing 41 includes a sleeve 411 and a carrier 412, the sleeve 411 is sleeved outside the carrier 412, the first gap 419 is located between the carrier 412 and the rotor 3, and the communication hole 83 is located on the sleeve 411. At this time, the radial hydrostatic bearing 41 is not an integral structure, but a split structure, so that axial movement is more convenient to realize, and the risk of shaft clamping is reduced. The communication hole 83 is arranged on the sleeve 411 of the split type radial hydrostatic bearing 41, which is positioned outside, so that the communication hole 83 is more convenient for communicating the first groove 85 with the second exhaust gas path.

In the foregoing embodiments, the air outlet 84 may be located on the side of the bearing housing 42 near the diffuser 43, or may be located on the side of the bearing housing 42 away from the diffuser 43. Wherein, referring to fig. 1 and 2, when the air outlet 84 is located on the side of the bearing seat 42 away from the diffuser 43, the air outlet path 8 may further include an air bleed hole 87, where the air bleed hole 87 is disposed on the bearing seat 42 and/or on the housing 1, and communicates the first air outlet cavity 81 and/or the second air outlet cavity 82 with the air outlet 84. At this time, the gas flowing out of the bearing assembly 4 can smoothly flow to the gas outlet 84 on the side of the bearing housing 42 away from the diffuser 43 via the gas outlet 87, thereby realizing the exhaust.

In the foregoing embodiments, the number of the first grooves 85 and/or the second grooves 86 is not limited to one, but may be two or more.

For example, referring to fig. 7, in some embodiments, the exhaust gas path 8 includes at least two first grooves 85, the at least two first grooves 85 being spaced apart along the circumference of the rotor 3. In this way, a faster and more reliable discharge of air is facilitated, so that the operational reliability of the compressor 10 can be more effectively improved.

For another example, referring to fig. 8, in some embodiments, the exhaust gas path 8 includes at least two second grooves 86, the at least two second grooves 86 being spaced apart along the circumference of the rotor 3. In this way, a faster and more reliable discharge of air is facilitated, so that the operational reliability of the compressor 10 can be more effectively improved.

In order to achieve the air supply to the radial hydrostatic bearing 41 in the foregoing embodiments, referring to fig. 1 and 2, the compressor 10 includes a first air supply path 71, and the first air supply path 71 communicates with the first gap 419 and supplies air to the first gap 419 to form an air film.

Specifically, referring to fig. 2, in some embodiments, the first air supply path 71 includes an air intake hole 711, a first air supply passage 712, and a first air intake passage 713, the air intake hole 711 is provided on the housing 1 and communicates with the outside of the housing 1, the first air supply passage 712 is provided on the bearing housing 42 and communicates with the air intake hole 711, and the first air intake passage 713 is provided on the radial hydrostatic bearing 41 and communicates with the first air supply passage 712 and the first gap 419. In this way, the gas can enter the first gap 419 between the radial hydrostatic bearing 41 and the rotor 3 through the gas inlet hole 711 on the housing 1, the first gas supply channel 712 on the bearing seat 42 and the first gas supply channel 712 on the radial hydrostatic bearing 41 in sequence, so as to form a gas film, support the rotor 3, and realize the supporting function of the radial hydrostatic bearing 41 on the rotor 3. In this case, since only the casing 1, the bearing seat 42 and the radial hydrostatic bearing 41 are provided with the duct, the air supply to the radial hydrostatic bearing 41 can be realized without providing a complicated air path, thereby being beneficial to simplifying the structure of the air supply air path and also being beneficial to preventing the risk of gas leakage from being increased due to the excessively complicated air supply air path.

Where the radial hydrostatic bearing 41 is a split bearing comprising the sleeve 411 and the carrier 412 as previously described, referring to fig. 2, in some embodiments the first air intake passage 713 comprises a first passage segment 714 and a second passage segment 715, the first passage segment 714 being disposed on the sleeve 411 and in communication with the first air supply passage 712, the second passage segment 715 being disposed on the carrier 412 and in communication with the first passage segment 714 and the first gap 419. At this time, the first air inlet channel 713 penetrates through the sleeve 411 and the carrier 412, and includes a first channel segment 714 located on the sleeve 411 and a second channel segment 715 located on the carrier 412, and the first air inlet channel 712 is communicated with the first gap 419 through the first channel segment 714 located on the sleeve 411 and the second channel segment 715 located on the carrier 412 in sequence, so that the whole air path is relatively simple.

Specifically, with continued reference to fig. 2, as an example of the first channel segment 714, the first channel segment 714 includes a first annular groove 716 and a vent 717, the first annular groove 716 is disposed on an outer surface of the sleeve 411 in communication with the first air supply channel 712, and the vent 717 is disposed at a bottom of the first annular groove 716 and in communication with the first annular groove 716 and the second channel segment 715. At this time, the first passage section 714 includes a first annular groove 716 and a vent hole 717 which are communicated with each other, and is communicated with the first gas supply passage 712 and the second passage section 715 through the first annular groove 716 and the vent hole 717, respectively, so that the gas flowing out from the first gas supply passage 712 can flow through the first annular groove 716 and the vent hole 717 in sequence, then flow into the second passage section 715, and finally reach the first gap 419. Due to the arrangement of the first annular groove 716, the first annular groove 716 can guide the gas flowing out of the first gas supply channel 712 to flow along the circumferential direction of the sleeve 411, so that circumferential uniform distribution of the gas is realized, and the gas supply uniformity is improved, and a more uniform gas film is formed in the first gap 419.

The number of vent holes 717 may be one, two, or more. For example, referring to fig. 5, in some embodiments, the first channel segment 714 includes at least two vent holes 717, the at least two vent holes 717 being spaced along the circumference of the first annular groove 716. Thus, the uniformity of air supply is further improved.

In addition, returning to fig. 2, as an example of the second channel section 715, the second channel section 715 includes a second annular groove 718 and a first orifice 719, the second annular groove 718 is provided on an outer surface of the carrier 412 and communicates with the first channel section 714, and the first orifice 719 is provided at a bottom of the second annular groove 718 and communicates with the second annular groove 718 and the first gap 419. At this time, the second passage section 715 includes the second annular groove 718 and the first orifice 719 which communicate with each other, and communicates with the first passage section 714 and the first gap 419 through the second annular groove 718 and the first orifice 719, respectively, so that the gas flowing out of the first passage section 714 can flow through the second annular groove 718 and the first orifice 719 in order and then flow into the first gap 419. Due to the provision of the second annular groove 718, the second annular groove 718 is capable of guiding the gas flowing out of the first channel segment 714 to flow along the circumferential direction of the carrier 412, so that circumferential uniform distribution of the gas is achieved, and therefore, the gas supply uniformity is improved, and a more uniform gas film is formed in the first gap 419. Further, since the first orifice 719 can perform a throttle function, it is convenient for the gas to flow into the first gap 419 through the first orifice 719, and then a gas film is formed to support the rotor 3.

The number of the first throttle 719 may be one, two, or more. For example, referring to fig. 6, in some embodiments, the second channel segment 715 includes at least two first orifices 719 that are spaced apart along the axial and/or circumferential direction of the second annular groove 718. Thus, the uniformity of air supply is further improved, and the pressure difference is more quickly established to form an air film.

In the foregoing embodiments, the number of bearing assemblies 4 may be one, or may be more than one. For example, returning to fig. 1, in some embodiments, the compressor 10 includes two bearing assemblies 4, the two bearing assemblies 4 being disposed at axial ends of the rotor 3. At this time, both axial ends of the rotor 3 can be effectively supported by the two radial hydrostatic bearings 41, and both the radial hydrostatic bearings 41 can smoothly exhaust, and therefore, the operation reliability of the compressor 10 is higher.

When the compressor 10 includes two bearing assemblies 4, the two bearing assemblies 4 may be supplied by the same supply gas path, or may be supplied by different supply gas paths. For example, referring to fig. 1, in some embodiments, the compressor 10 includes two first air supply passages 71, the two first air supply passages 71 supplying air to the first gaps 419 of the radial hydrostatic bearings 41 of the two bearing assemblies 4, respectively. At this time, the two bearing assemblies 4 are supplied with air by the different first air supply paths 71, and the reliability of the air supply is higher.

As a further improvement to the previous embodiments, in some embodiments, the compressor 10 includes not only the radial hydrostatic bearings 41, but also hydrostatic thrust bearings. Specifically, referring to fig. 1 and 2, the rotor 3 is provided with a thrust disk 31, the thrust disk 31 is located on a side of the radial hydrostatic bearing 41 remote from the diffuser 43, and the compressor 10 further includes at least one of the first hydrostatic thrust bearing 5 and the second hydrostatic thrust bearing 6.

The first hydrostatic thrust bearing 5 is sleeved on the rotor 3, and is disposed on one side of the thrust disc 31 near the radial hydrostatic bearing 41, and a second gap 51 is disposed between the first hydrostatic thrust bearing 5 and an adjacent axial end surface of the thrust disc 31, see fig. 1 and 2. The compressor 10 includes a second air supply path 72, and the second air supply path 72 communicates with the second gap 51 to supply air to the second gap 51 to form an air film. The second gap 51 communicates with the first exhaust chamber 81.

In the above-described arrangement, the first hydrostatic thrust bearing 5 may support the rotor 3 together with the radial hydrostatic bearing 41, making the rotor 3 operate more smoothly. Further, since the second gap 51 for inflating and forming a gas film between the first hydrostatic thrust bearing 5 and the thrust disk 31 communicates with the first exhaust chamber 81, the gas in the second gap 51 can flow into the first exhaust chamber 81, and flow outward via the first groove 85 together with the gas flowing into the first exhaust chamber 81 from the first gap 419, thereby exhausting. Since the first hydrostatic thrust bearing 5 and the radial hydrostatic bearing 41 can share part of the exhaust gas path, it is advantageous to simplify the structure of the exhaust gas path 8. Further, since the first groove 85 can improve the exhaust smoothness, the first hydrostatic thrust bearing 5 can exhaust gas via the first groove 85, and the exhaust smoothness of the first hydrostatic thrust bearing 5 can also be improved. In particular, the first hydrostatic thrust bearing 5 and the exhaust gas of the radial hydrostatic bearing 41 flow together into the first exhaust chamber 81, so that the gas quantity is large, and in this case, the effect of the first groove 85 is more prominent, which can realize timely exhaust of two parts of gas, effectively prevent the accumulation of two parts of gas, and affect the bearing load and the operation reliability of the compressor.

The second air supply path 72 for supplying air to the first hydrostatic thrust bearing 5 may be independent of, or in communication with, the first air supply path 71 for supplying air to the radial hydrostatic bearing 41. For example, referring to fig. 1 and 2, in some embodiments, the second air supply channel 72 includes a second air supply channel 721, the second air supply channel 721 being disposed on the bearing housing 42 and communicating the first air supply channel 712 of the first air supply channel 71 with the second gap 51. At this time, the second air supply path 72 is communicated with the first air supply path 71, and the second air supply path 72 may share a portion of the first air supply path 712 and the air intake hole 711 with the first air supply path 71, and thus, the structure is simpler.

With continued reference to fig. 1 and 2, in some embodiments, the second air supply passage 72 includes not only a second air supply channel 721, but also a first air supply chamber 722 and a second orifice 724, the first air supply chamber 722 being located between the first hydrostatic thrust bearing 5 and an adjacent axial end face of the bearing housing 42 and in communication with the second air supply channel 721, the second orifice 724 being disposed on the first hydrostatic thrust bearing 5 and in communication with the first air supply chamber 722 and the second gap 51. In this way, the air outside the casing 1 can flow into the second gap 51 through the air inlet 711, the first air supply channel 712, the second air supply channel 721, the first air supply chamber 722 and the second orifice 724 in sequence, so as to form an air film required by the first hydrostatic thrust bearing 5, realize the supporting effect of the first hydrostatic thrust bearing 5 on the rotor 3, and have simple air path and convenient air supply.

In addition, referring to fig. 1 and 2, the second hydrostatic thrust bearing 6 is fitted over the rotor 3 and is disposed on the side of the thrust disc 31 remote from the radial hydrostatic bearing 41. A third gap 61 is provided between the second hydrostatic thrust bearing 6 and the adjacent axial end face of the thrust disc 31. The compressor 10 includes a third air supply path 73, the third air supply path 73 being in communication with the third gap 61 to supply air to the third gap 61 to form an air film, the third gap 61 being in communication with the air outlet hole 84.

In the above-described arrangement, the second hydrostatic thrust bearing 6 may support the rotor 3 together with the radial hydrostatic bearing 41, making the rotor 3 operate more smoothly. Since the third gap 61 for forming a gas film by inflation between the second hydrostatic thrust bearing 6 and the thrust disk 31 communicates with the gas outlet 84, the gas can flow out of the third gap 61 and flow to the gas outlet 84 after forming a gas film in the third gap 61, and is exhausted. Since the third gap 61 may not pass through the exhaust gas path of the radial hydrostatic bearing 41, i.e., may be in communication with the air outlet 84, the exhaust gas path of the second hydrostatic thrust bearing 6 is shorter, and the exhaust gas is smoother.

The third air supply path 73 for supplying air to the second hydrostatic thrust bearing 6 may be independent of, or in communication with, the first air supply path 71 for supplying air to the radial hydrostatic bearing 41. For example, referring to fig. 1 and 2, in some embodiments, the third air supply path 73 includes a third air supply passage 731, the third air supply passage 731 is disposed on the bearing housing 42 and communicates the first air supply passage 712 of the first air supply path 71 with the third gap 61. At this time, the third air supply path 73 communicates with the first air supply path 71, and the third air supply path 73 may share a portion of the first air supply channel 712 and the air intake hole 711 with the first air supply path 71, and thus, the structure is simpler.

With continued reference to fig. 1 and 2, in some embodiments, the third air supply passage 73 includes not only the third air supply passage 731, but also a second air supply chamber 732 and a third orifice 734, the second air supply chamber 732 being located between the second hydrostatic thrust bearing 6 and the adjacent axial end face of the cover 97 and communicating with the third air supply passage 731, the third orifice 734 being disposed on the second hydrostatic thrust bearing 6 and communicating the second air supply chamber 732 with the third gap 61. The cover 97 is sleeved on the rotor 3 and is positioned on the side of the second hydrostatic thrust bearing 6 away from the radial hydrostatic bearing 41. In this way, the air outside the casing 1 can flow into the third gap 61 through the air inlet 711, the first air supply channel 712, the third air supply channel 731, the second air supply cavity 732 and the third orifice 734 in sequence, so as to form an air film required by the second hydrostatic thrust bearing 6, realize the supporting effect of the second hydrostatic thrust bearing 6 on the rotor 3, and have simple air path and convenient air supply.

The embodiments shown in fig. 1-8 are further described below.

As shown in fig. 1-8, in this embodiment, the compressor 10 is a centrifugal compressor that includes a housing 1, a stator 2, a rotor 3, two bearing assemblies 4, a first hydrostatic thrust bearing 5, a second hydrostatic thrust bearing 6, an air supply air path 7, an air exhaust air path 8, a seal 91, an impeller 92, a volute 93, a lock 94, and a cover 97.

Wherein, the shell 1 is cylindrical, and the inside is provided with a cavity, which provides installation space for other components such as the stator 2, the rotor 3 and the like.

The stator 2 is fixedly disposed in the housing 1.

The rotor 3 is rotatably arranged in the shell 1, penetrates through the stator 2 and is matched with the stator 2, so that the conversion of electric energy into mechanical energy is realized. The axial both ends of the rotor 3 protrude from both sides of the housing 1, and the axial both ends of the rotor 3 are provided with impellers 92, respectively. The impeller 92 is locked to the rotor 3 by a locking member 94 (e.g., a lock nut) so that the impeller 92 can rotate with the rotor 3. The outer sides (the sides away from the stator 2) of both impellers 92 are provided with a volute 93. Two volutes 93 are connected to both axial ends of the housing 1.

Two bearing assemblies 4 are provided at both axial ends of the rotor 3, and are located inside (on the side close to the stator 2) the two impellers 92. Both bearing assemblies 4 comprise a radial hydrostatic bearing 41, a bearing housing 42 and a diffuser 43. The radial hydrostatic bearing 41 is fitted over the rotor 3. The bearing seat 42 is sleeved outside the radial hydrostatic bearing 41. The diffuser 43 is fitted over the rotor 3 and is located on the side of the radial hydrostatic bearing 41 remote from the stator 2.

The two bearing blocks 42 divide the interior space of the housing 1 such that the interior of the housing 1 is divided into a motor chamber 96 between the two bearing blocks 42 and a bearing chamber 95 between the two bearing blocks 42 and the corresponding diffuser 43.

For convenience of description, the axial direction of the rotor 3 is defined as the left-right direction, and is left-right with respect to fig. 1. As such, the volute 93, impeller 92, diffuser 43, radial hydrostatic bearing 41, and bearing housing 42 on the left side may be referred to as a left volute, a left impeller, a left diffuser, a left radial hydrostatic bearing, and a left bearing housing, respectively, while the volute 93, impeller 92, diffuser 43, radial hydrostatic bearing 41, and bearing housing 42 on the right side may be referred to as a right volute, a right impeller, a right diffuser, a right radial hydrostatic bearing, and a right bearing housing, respectively, and the two bearing assemblies 4 on the left and right sides may be referred to as a left bearing assembly and a right bearing assembly, respectively, for convenience of distinction.

In this embodiment, the left bearing assembly and the right bearing assembly have much similarity, and thus, for the sake of simplifying the description, only the left bearing assembly will be described with emphasis, while for the right bearing assembly, only the differences from the left bearing assembly will be mainly described, and where not described, it can be understood with reference to the description of the left bearing assembly.

Fig. 3-6 further illustrate the structure of the hydrostatic bearing 41 (i.e., left hydrostatic bearing) in the left bearing assembly. As can be seen in connection with fig. 3-6 and fig. 1 and 2, in this embodiment, the left hydrostatic bearing is of a split construction, comprising a carrier 412 and a sleeve 411. The carrier 412 is substantially hollow cylindrical and is fitted over the rotor 3 with a first gap 419 between the inner surface and the outer surface of the rotor 3 for ventilation to form a gas film. The sleeve 411 is generally hollow and cylindrical, and is fitted over the carrier 412, and a sealing member 91 (e.g., an O-ring, V-ring, or U-ring) is provided between the inner surface of the sleeve and the outer surface of the carrier 412 to seal against air leakage.

Specifically, as shown in fig. 3-6, in this embodiment, sleeve 411 includes a barrel 413 and a stop flange 414. The carrier 412 includes a body 415 and a stop ring 416. The stopper flange 414 is connected to one axial end of the cylinder 413 and protrudes radially outward from the cylinder 413. The body 415 is located in the sleeve 411. The stopper ring 416 is connected to an axial end of the main body 415, and projects radially outward from the main body 415. The stop flange 414 and the stop ring 416 are located on both axial sides of the barrel 413. The stop ring 416 abuts an axial end face of the cylinder 413 facing the stator 2 to limit the relative displacement of the sleeve 411 and the carrier 412. The limiting flange 414 faces the diffuser 43 of the left bearing assembly (i.e., the left diffuser) and is configured to extend between the left diffuser and the left bearing housing for stopping and limiting. Wherein the surface of the stop ring 416 facing the stator 2 and the surface of the limit flange 414 facing the left diffuser form two axial end faces of the radial hydrostatic bearing 41, i.e. a first end face 417 and a second end face 418, respectively.

Fig. 7 further illustrates the structure of the bearing housing 42 (i.e., left bearing housing) in the left bearing assembly. As can be seen in connection with fig. 7 and 2, in this embodiment the left bearing housing is used not only for supporting the radial hydrostatic bearing 41, but also for supporting the first hydrostatic thrust bearing 5 and the second hydrostatic thrust bearing 6.

Specifically, as shown in fig. 2 and 7, in this embodiment, the left bearing housing includes a housing 421, a first boss 422, and a second boss 423. The first boss 422 and the second boss 423 are connected to axial end surfaces of opposite sides of the seat 421, and each have an outer diameter smaller than the seat 421. Wherein, the first boss 422 is connected to the surface of the base 421 facing the left diffuser for cooperating with the limit flange 414 of the left radial hydrostatic bearing. The second boss 423 is connected to a surface of the base 421 facing the stator 2. The first boss 422 and the base 421 are provided with a first mounting groove 424 for accommodating the left radial hydrostatic bearing therein. The second boss 423 is provided therein with a second mounting groove 425 for accommodating the first hydrostatic thrust bearing 5 and the second hydrostatic thrust bearing 6. The first mounting groove 424 is smaller in size than the second mounting groove 425. The first mounting groove 424 and the second mounting groove 425 each have a groove bottom. The bottom of the first mounting groove 424 is a portion of the bottom of the second mounting groove 425. The surface of the groove bottom of the first mounting groove 424 facing the left radial hydrostatic bearing is an inner surface, which is opposite to the first end surface 417 of the left radial hydrostatic bearing, constituting a first surface 426 of the left bearing housing. The left radial hydrostatic bearing is disposed in the first mounting groove 424 with a first end face 417 opposite a first surface 426 of the left bearing housing. Further, a plurality of seals 91 are provided on the outer surface of the cylinder 413 of the left hydrostatic bearing for sealing the gap between the left hydrostatic bearing and the left bearing housing to prevent air leakage. Meanwhile, a sealing piece 91 is arranged between the outer surface of the left bearing seat and the inner surface of the shell 1 and is used for sealing a gap between the left bearing seat and the shell 1 to prevent air leakage.

Fig. 8 further shows the structure of the diffuser 43 (left diffuser) in the left bearing assembly. As can be seen from fig. 8 and 2, in this embodiment, the left diffuser is generally hollow and cylindrical, and has a shoulder thereon for being engaged with the housing 1 for limiting. The smaller diameter end of the diffuser 43 is inserted into the housing 1 with its surface facing the left hydrostatic bearing opposite the second end face 418 of the left hydrostatic bearing, constituting a second surface 431.

The first hydrostatic thrust bearing 5 and the second hydrostatic thrust bearing 6 are each disposed in the second mounting groove 425 of the left bearing housing, and supported by the left bearing housing. Specifically, as shown in fig. 1 and 2, in this embodiment, a thrust disk 31 is provided on the rotor 3. The thrust disc 31 is located between the left radial hydrostatic bearing and the stator 2 and extends into the second mounting groove 425. The first hydrostatic thrust bearing 5 and the second hydrostatic thrust bearing 6 are disposed on opposite sides of the thrust disc 31. The first hydrostatic thrust bearing 5 is provided on the side of the thrust disk 31 close to the left radial hydrostatic bearing, and serves as the left hydrostatic thrust bearing. The second hydrostatic thrust bearing 6 is provided on the side of the thrust disc 31 remote from the left radial hydrostatic bearing, and serves as a right hydrostatic thrust bearing. A second gap 51 for forming a gas film by introducing gas is provided between the first hydrostatic thrust bearing 5 and the left end surface of the thrust disk 31. A third gap 61 for forming a gas film by introducing gas is provided between the second hydrostatic thrust bearing 6 and the right end surface of the thrust disk 31. Further, a cover 97 is provided on the side of the second hydrostatic thrust bearing 6 remote from the left radial hydrostatic bearing. Seals 91 are provided between the first hydrostatic thrust bearing 5 and the left bearing block, between the second hydrostatic thrust bearing 6 and the cover 97, and between the first hydrostatic thrust bearing 5 and the second hydrostatic thrust bearing 6.

The left radial hydrostatic bearing, the first hydrostatic thrust bearing 5, and the second hydrostatic thrust bearing 6 together support the left end of the rotor 3.

In order to achieve the supporting effect of the left radial hydrostatic bearing, the first hydrostatic thrust bearing 5, and the second hydrostatic thrust bearing 6 on the rotor 3, as shown in fig. 1 and 2, in this embodiment, the compressor 10 includes an air supply path 7, and the air supply path 7 includes a first air supply path 71, a second air supply path 72, and a third air supply path 73 provided on the left side.

Wherein the first air supply path 71 is used for supplying air to the left radial hydrostatic bearing. Specifically, as shown in fig. 1 to 7, in this embodiment, the first air supply passage 71 includes an air intake hole 711, a first air supply passage 712, and a first air intake passage 713 that communicate in this order, and the first air intake passage 713 includes a first passage section 714 and a second passage section 715 that communicate in this order, the first passage section 714 includes a first annular groove 716 and an air vent 717 that communicate in this order, and the second passage section 715 includes a second annular groove 718 and a first orifice 719 that communicate in this order. Among them, an air intake hole 711 is provided on the housing 1 and extends in the radial direction, communicating the inside and outside of the housing 1. The first air supply channel 712 is disposed on the left bearing seat, specifically on the seat body 421 of the left bearing seat, and extends in the radial direction to communicate the air intake hole 711 with the first annular groove 716. The first annular groove 716 is disposed on the sleeve 411 of the left radial hydrostatic bearing, specifically disposed on the cylinder 413 of the sleeve 411, and is recessed inward from the outer surface of the cylinder 413 and surrounds the cylinder 413 for a complete circle, so as to uniformly distribute the airflow in a circumferential direction. The 3 vent holes 717 are uniformly arranged at the groove bottom of the first annular groove 716 in the circumferential direction, and each extend in the radial direction, communicating the first annular groove 716 with the second annular groove 718. The second annular groove 718 is disposed on the carrier 412 of the left radial hydrostatic bearing, specifically disposed on the main body 415 of the carrier 412, and is recessed inward from the outer surface of the main body 415, and surrounds the main body 415 for a whole circle, so as to store gas and uniformly distribute the gas in a circumferential direction. A plurality of first throttle holes 719 are provided in a row and column at the bottom of the second annular groove 718, and these first throttle holes 719 each extend in the radial direction, communicating the second annular groove 718 with the first gap 419 to throttle gas so that gas can enter the first gap 419 and form a gas film of the left radial hydrostatic bearing. Thus, the air supply to the left radial hydrostatic bearing can be realized.

The second air supply path 72 is used for supplying air to the first hydrostatic thrust bearing 5. Specifically, as shown in fig. 1 and 2, in this embodiment, the second air supply passage 72 includes a second air supply passage 721, a first air supply chamber 722, and a second orifice 724. The second air supply channel 721 is disposed on the left bearing seat, specifically, on the seat body 421 of the left bearing seat, and extends along the axial direction, and communicates the first air supply channel 712 with the first air supply chamber 722. At this time, the second air supply passage 721 forms a branch of the first air supply passage 712. The first air supply chamber 722 is located between the first hydrostatic thrust bearing 5 and the surface of the second mounting groove 425 facing the first hydrostatic thrust bearing 5, and is formed specifically by providing a third annular groove 723 on the left end surface of the first hydrostatic thrust bearing 5. A plurality of second orifices 724 are provided on the groove bottom of the third annular groove 723, and each penetrate the first hydrostatic thrust bearing 5 in the axial direction, communicating the third annular groove 723 with the second gap 51, so that gas can enter the second gap 51 after undergoing a throttling action, forming a gas film of the first hydrostatic thrust bearing 5. In this way, the air supply to the first hydrostatic thrust bearing 5 can be realized.

The third air supply path 73 is used for supplying air to the second hydrostatic thrust bearing 6. Specifically, as shown in fig. 1 and 2, in this embodiment, the third air supply passage 73 includes a third air supply passage 731, a second air supply chamber 732, and a third orifice 734. The third air supply passage 731 is disposed on the left bearing seat, specifically on the seat body 421 of the left bearing seat, and extends along the axial direction, and communicates the first air supply passage 712 with the second air supply chamber 732. At this time, the third air supply passage 731 forms another branch of the first air supply passage 712, is arranged side by side in the radial direction with the second air supply passage 721, and is located specifically radially outside the second air supply passage 721. The second air supply chamber 732 is located between the second hydrostatic thrust bearing 6 and the surface of the cover 97 facing the second hydrostatic thrust bearing 6, and is specifically formed by providing a fourth annular groove 733 on the right end face of the second hydrostatic thrust bearing 6. The plurality of third orifices 734 are disposed on the groove bottom of the fourth annular groove 733 and penetrate the second hydrostatic thrust bearing 6 along the axial direction, so that the fourth annular groove 733 and the third gap 61 are communicated, and gas can enter the third gap 61 after being throttled, thereby forming a gas film of the second hydrostatic thrust bearing 6. In this way, the air supply to the second hydrostatic thrust bearing 6 can be achieved.

It can be seen that in this embodiment, the left radial hydrostatic bearing, the first hydrostatic thrust bearing 5 and the second hydrostatic thrust bearing 6 share the same air intake hole 711, which is simple in structure, and this is advantageous in avoiding the risk of leakage caused by a complex air supply path.

In this embodiment, the left hydrostatic bearing is movable left and right, and when moved to the right to the extreme position, the first end face 417 abuts the first surface 426, and when moved to the left to the extreme position, the second end face 418 abuts the second surface 431. In order to prevent this from affecting the exhaust smoothness, this embodiment provides an exhaust gas path 8, and the exhaust gas path 8 is designed.

Next, the structure of the exhaust gas path 8 will be described.

As shown in fig. 1 and 2, in this embodiment, the exhaust gas path 8 includes a first exhaust gas chamber 81, a second exhaust gas chamber 82, a communication hole 83, an exhaust gas hole 84, a first groove 85, a second groove 86, and a bleed hole 87.

Wherein the air outlet 84 is provided on the casing 1, and particularly on a portion of the casing 1 between the stator 2 and the right bearing assembly, which extends in a radial direction, communicating the inside and the outside of the casing 1.

The air vent 87 is disposed on the left bearing seat, specifically on the seat 421 of the left bearing seat, and extends in the axial direction to communicate the bearing cavity 95 located on the left side of the left bearing seat with the motor cavity 96 located on the right side of the left bearing seat.

The first and second exhaust chambers 81 and 82 are disposed on the left and right sides of the left radial hydrostatic bearing, specifically between the first end face 417 of the left radial hydrostatic bearing and the first surface 426 of the left bearing housing, and between the second end face 418 of the left radial hydrostatic bearing and the second surface 431 of the left diffuser, respectively. The first exhaust chamber 81 and the second exhaust chamber 82 are both communicated with the first gap 419, so that the gas in the first gap 419 can be divided into two paths, and flows to the left and right sides, and flows into the second exhaust chamber 82 and the first exhaust chamber 81.

The first groove 85 is disposed on the first surface 426 of the left bearing housing, and is recessed from the first surface 426 toward a side remote from the first end surface 417. Also, the first groove 85 is located radially outside the first exhaust chamber 81. The plurality of first grooves 85 are uniformly arranged in the circumferential direction and each communicate with the first exhaust chamber 81.

The communication hole 83 is provided on the sleeve 411 of the left radial hydrostatic bearing. The plurality of communication holes 83 are uniformly arranged along the circumferential direction of the sleeve 411. Each communication hole 83 extends in the axial direction, penetrates through both axial ends of the sleeve 411, and communicates a first groove 85 located on the right side of the left hydrostatic bearing with a second exhaust chamber 82 located on the left side of the left hydrostatic bearing.

The second groove 86 is disposed on the second surface 431 of the left diffuser and is recessed from the second surface 431 toward a side away from the second end surface 418. Further, the second groove 86 is located radially outward of the second exhaust chamber 82. The plurality of second grooves 86 are uniformly arranged along the circumferential direction and each communicate the second exhaust chamber 82 with a bearing chamber 95 located between the left bearing housing and the left diffuser.

Since the bearing chamber 95 between the left bearing housing and the left diffuser communicates with the bleed hole 87 and the bleed hole 87 communicates with the air outlet 84, the second groove 86 communicating with the bearing chamber 95 between the left bearing housing and the left diffuser can communicate with the air outlet 84 through the bleed hole 87.

Further, since the second exhaust chamber 82 communicates with the second recess 86 and the first exhaust chamber 81 communicates with the second exhaust chamber 82 through the first recess 85 and the communication hole 83, the second exhaust chamber 82 and the first exhaust chamber 81 can both communicate with the air outlet 84, so that the gas in the first gap 419 can be divided into two flows into the first exhaust chamber 81 and the second exhaust chamber 82, and the gas flowing into the first exhaust chamber 81 can flow into the second exhaust chamber 82 via the first recess 85 and the communication hole 83, and the gas flowing into the second exhaust chamber 82 leftward from the first gap 419 merges with the gas flowing into the second exhaust chamber 82 through the second recess 86 and the air-entraining hole 87, and then flows out to the outside of the housing 1 via the air outlet 84 to be discharged, thereby realizing the exhaust of the left radial hydrostatic bearing.

In addition, in order to achieve the exhaust of the first hydrostatic thrust bearing 5, as shown in fig. 2, in this embodiment, the second gap 51 of the first hydrostatic thrust bearing 5 communicates with the first exhaust chamber 81 through the first gap 52 between the inner surface of the first hydrostatic thrust bearing 5 and the outer surface of the rotor 3. In this way, the gas in the second gap 51 can flow into the first exhaust chamber 81 through the first gap 52, and then, together with the gas flowing into the first exhaust chamber 81 from the first gap 419, flows into the gas outlet 84 through the first groove 85, the communication hole 83, the second exhaust chamber 82, the second groove 86, and the bleed hole 87 in this order, and is discharged through the gas outlet 84, thereby realizing the exhaust of the first hydrostatic thrust bearing 5.

Since the first groove 85 is provided, even if the left hydrostatic bearing moves rightward to the limit position, the first exhaust chamber 81 can still communicate with the communication hole 83 through the first groove 85, so that the gas collected in the first exhaust chamber 81 by the first gap 419 and by the second gap 51 is not blocked but can be discharged in time, and thus, it is possible to effectively prevent the pressure from rising here due to gas accumulation, affecting the pressure difference between the right side portion of the left hydrostatic bearing and the second annular groove 718, and the pressure distribution in the third annular groove 723 of the first hydrostatic thrust bearing 5, so as not to affect the load bearing of the left hydrostatic bearing and the first hydrostatic thrust bearing 5, resulting in a reduction in operational reliability.

Moreover, since the second groove 86 is provided, even if the left hydrostatic bearing moves to the left to the limit position, the second exhaust chamber 82 can still communicate with the air outlet hole 84 through the second groove 86, so that the air entering the second exhaust chamber 82 from the first gap 419 and the air converged into the second exhaust chamber 82 from the first gap 419 and the second gap 51 via the first exhaust chamber 81 are not blocked but can still be discharged in time, and thus, the pressure rise caused by the accumulation of the air can be effectively prevented from affecting the load of the left hydrostatic bearing and the first hydrostatic thrust bearing 5, resulting in a reduction in operational reliability.

It can be seen that by providing the first groove 85 and the second groove 86, the exhaust smoothness can be effectively improved, the bearing capacity can be improved, and the operation reliability of the compressor 10 can be improved.

In addition, in order to achieve the exhaust of the second hydrostatic thrust bearing 6, as shown in fig. 2, in this embodiment, a second slit 62 is provided between the inner surface of the second hydrostatic thrust bearing 6 and the inner surface of the cover 97 and the outer surface of the rotor 3, and the third gap 61 of the second hydrostatic thrust bearing 6 communicates with the motor chamber 96 through the second slit 62. Since the motor chamber 96 communicates with the air outlet hole 84, the third gap 61 communicating with the motor chamber 96 communicates with the air outlet hole 84. In this way, the gas in the third gap 61 can flow to the gas outlet hole 84 through the second gap 62, and flow out of the casing 1 through the gas outlet hole 84, thereby exhausting the second hydrostatic thrust bearing 6.

It can be seen that the exhaust gas path 9 of this embodiment can realize smooth exhaust of the left radial hydrostatic bearing, the first hydrostatic thrust bearing 5, and the second hydrostatic thrust bearing 6 based on a simpler structure, effectively improving the operational reliability of the compressor 10.

Having described the left bearing assembly above, the differences between the right bearing assembly and the left bearing assembly will be mainly described.

As shown in fig. 1, in this embodiment, the main difference between the right bearing assembly and the left bearing assembly is that the bearing housing 42 of the right bearing assembly (i.e., the right bearing housing) is only for supporting the hydrostatic bearing 41 of the right bearing assembly (i.e., the right hydrostatic bearing) and no longer supports the hydrostatic thrust bearing, and therefore, the right bearing housing includes only the first mounting groove 424 for receiving the right hydrostatic bearing and does not include the second mounting groove 425 for receiving the hydrostatic thrust bearing, and the first mounting groove 424 of the right bearing housing does not have a groove bottom, but is directly opened toward one end of the stator 2, communicating with the motor cavity 96. In this case, the right hydrostatic bearing is provided with the second exhaust chamber 82 and the second recess 86 only on the right side, and is no longer provided with the first exhaust chamber 81 and the first recess 85 on the left side. The second exhaust chamber 82 communicates with the motor chamber 96 through the second recess 86 and the communication hole 83 located on the sleeve 411 of the right radial hydrostatic bearing.

Meanwhile, since the right bearing housing is only used to support the right radial hydrostatic bearing and no longer to support the hydrostatic thrust bearing, in this embodiment, the right bearing assembly is equipped with only the first air supply passage 71 for supplying air to the right radial hydrostatic bearing, and is not equipped with the aforementioned second air supply passage 72 and third air supply passage 73, that is, in this embodiment, the air supply passage 7 includes two first air supply passages 71, one second air supply passage 72 and one third air supply passage 73. One of the first air supply paths 71, one of the second air supply paths 72 and one of the third air supply paths 73 form a left air supply path for supplying air to the left radial hydrostatic bearing, the first hydrostatic thrust bearing 5 and the second hydrostatic thrust bearing 6, and the other first air supply path 71 forms a right air supply path for supplying air to the right radial hydrostatic bearing.

The air supply and exhaust processes of the left radial hydrostatic bearing, the first and second hydrostatic thrust bearings 5 and 6, and the right radial hydrostatic bearing will be described next with reference to fig. 1 and 2.

First, the air supply and exhaust processes of the left radial hydrostatic bearing, the first hydrostatic thrust bearing 5, and the second hydrostatic thrust bearing 6 will be described.

As shown in fig. 1 and 2, in this embodiment, the air outside the housing 1 enters the first air supply passage 712 through the air intake hole 711 of the left air supply passage, and thereafter, is split into three for air supply to the left radial hydrostatic bearing, the first hydrostatic thrust bearing 5, and the second hydrostatic thrust bearing 6, respectively.

Wherein, the gas supplied to the left radial hydrostatic bearing flows from the first gas supply channel 712 to the first gap 419 between the left radial hydrostatic bearing and the rotor 3 via the first annular groove 716, the vent hole 717, the second annular groove 718 and the first orifice 719 of the left radial hydrostatic bearing in sequence, so as to form a gas film, and then, the gas in the first gap 419 flows to both sides, a part of the gas flows to the second gas discharge chamber 82 directly to the left, and the other part flows to the first gas discharge chamber 81 to the right, and reaches the second gas discharge chamber 82 through the first groove 85 and the communication hole 83 penetrating the sleeve 411 of the left radial hydrostatic bearing;

the gas supplied to the first hydrostatic thrust bearing 5 flows out from the first gas supply passage 712, flows through the second gas supply passage 721, the first gas supply chamber 722, and the second orifice 724 in this order, flows to the second gap 51 between the first hydrostatic thrust bearing 5 and the thrust disk 31, forms a gas film, then reaches the first gas discharge chamber 81 through the first gap 52 between the first hydrostatic thrust bearing 5 and the rotor 3, and is collected together with the gas discharged from the right side of the first gap 419, then reaches the second gas discharge chamber 82 through the first groove 85 and the communication hole 83 together, is collected together with the gas discharged from the left side of the first gap 419, reaches the gas discharge hole 87 through the second groove 86 located radially outside the second gas discharge chamber 82, and flows to the gas discharge hole 84, and is discharged;

The gas that supplies the second hydrostatic thrust bearing 6 flows out from the first gas supply passage 712, and flows into the third gap 61 between the second hydrostatic thrust bearing 6 and the thrust disk 31 through the third gas supply passage 731, the second gas supply chamber 732, and the third orifice 734 in this order, forming a gas film, and thereafter reaches the left side portion of the motor chamber 96 through the second hydrostatic thrust bearing 6 and the second gap 62 between the cover 97 and the rotor 3, and reaches the right side portion of the motor chamber 96 through the gas gap between the stator 2 and the rotor 3, and finally is discharged through the gas outlet hole 84.

Next, the air supply and exhaust process of the right radial hydrostatic bearing will be described.

As shown in fig. 1 and 2, in this embodiment, the air outside the casing 1 flows into the first gap 419 between the right radial hydrostatic bearing and the rotor 3 via the air intake hole 711 of the right air supply passage 712, the first annular groove 716, the air vent 717, the second annular groove 718, and the first orifice 719 in this order, forming an air film, after which the air in the first gap 419 flows to both sides, a part flows directly to the left toward the motor chamber 96, and the other part flows to the right, reaching the second exhaust chamber 82 between the right radial hydrostatic bearing and the right diffuser, and then sequentially passes through the second groove 86 located radially outside the second exhaust chamber 82 and the communication hole 83 penetrating the right radial hydrostatic bearing sleeve 411, reaching the motor chamber 96, and finally being discharged through the air outlet hole 84 provided in the casing 1.

It can be seen that this embodiment adopts the gas circuit of "two advances one and go out", carries out the bearing about for and carries out air feed and exhaust about, and the gas circuit is all comparatively simple, can effectively simplify the gas circuit structure when satisfying air feed exhaust requirement, reduces the leakage risk, improves the operational reliability of gas bearing and compressor 10.

Moreover, the embodiment optimizes the exhaust gas path, and through arranging the first groove 85 and the second groove 86, the problem of unsmooth exhaust caused by axial movement of the radial hydrostatic bearing can be skillfully solved, the exhaust smoothness of the gas bearing in the compressor 10 is effectively improved, the bearing capacity and the bearing stability of the gas bearing are improved, and the running reliability of the compressor 10 is improved.

It can be seen that the compressor 10 of this embodiment has the characteristics of simple air path and reliable air supply and exhaust.

The compressor 10 is applied to a refrigerant circulation system, so that the operation reliability of the refrigerant circulation system can be effectively improved, and the performance of the refrigerant circulation system can be improved.

Accordingly, the present application also provides a refrigerant circulation system including the compressor 10 of any of the embodiments of the present application. Illustratively, the refrigerant circulation system is an air conditioning system.

The foregoing description of the exemplary embodiments of the present application is not intended to limit the invention to the particular embodiments disclosed, but on the contrary, the intention is to cover all modifications, equivalents, alternatives, and alternatives falling within the spirit and scope of the invention.

Claims (17)

1. A compressor (10), characterized by comprising:

a housing (1);

a stator (2) fixedly arranged in the housing (1);

a rotor (3) rotatably penetrating the stator (2);

the bearing assembly (4) comprises a radial hydrostatic bearing (41), a bearing seat (42) and a diffuser (43), wherein the radial hydrostatic bearing (41) is sleeved on the rotor (3) in an axially movable manner, a first gap (419) is formed between the radial hydrostatic bearing and the outer surface of the rotor (3) so as to allow air to enter into the rotor to form an air film, the bearing seat (42) is sleeved outside the radial hydrostatic bearing (41), and the diffuser (43) is sleeved on the rotor (3) and is positioned on one side, far away from the stator (2), of the radial hydrostatic bearing (41); and

an exhaust gas path (8) for exhausting the gas in the first gap (419) to the outside of the housing (1), and including a gas outlet hole (84), the gas outlet hole (84) being provided on the housing (1) and communicating with the outside of the housing (1), and the exhaust gas path (8) further including at least one of:

A first exhaust chamber (81) and a first groove (85), wherein the first exhaust chamber (81) is positioned between a first end surface (417) of the radial hydrostatic bearing (41) facing the stator (2) and a first surface (426) of the bearing seat (42) opposite to the first end surface (417), and the first groove (85) is positioned on the first end surface (417) and/or the first surface (426) and is communicated with the first exhaust chamber (81) and the air outlet hole (84);

a second exhaust cavity (82) and a second groove (86), wherein the second exhaust cavity (82) is positioned between a second end face (418) of the radial hydrostatic bearing (41) facing the diffuser (43) and a second surface (431) of the diffuser (43) opposite to the second end face (418), and the second groove (86) is positioned on the second end face (418) and/or the second surface (431) and is communicated with the second exhaust cavity (82) and the air outlet hole (84).

2. The compressor (10) of claim 1, wherein the exhaust gas circuit (8) comprises at least two of the first grooves (85), the at least two first grooves (85) being spaced apart along the circumference of the rotor (3); and/or the exhaust gas circuit (8) comprises at least two second grooves (86), the at least two second grooves (86) being arranged at intervals along the circumference of the rotor (3).

3. The compressor (10) of claim 1, wherein the exhaust gas path (8) includes the first exhaust gas chamber (81), the first groove (85), the second exhaust gas chamber (82), and the second groove (86), and the exhaust gas path (8) further includes a communication hole (83), the communication hole (83) communicates the first groove (85) and the second exhaust gas chamber (82) or the second groove (86), and the second groove (86) communicates the second exhaust gas chamber (82) and the gas outlet hole (84).

4. A compressor (10) according to claim 3, wherein the radial hydrostatic bearing (41) comprises a sleeve (411) and a carrier (412), the sleeve (411) being fitted over the carrier (412), the first gap (419) being located between the carrier (412) and the rotor (3), the communication hole (83) being located on the sleeve (411).

5. The compressor (10) according to claim 1, characterized in that the air outlet opening (84) is located on the side of the bearing block (42) remote from the diffuser (43), and the exhaust gas circuit (8) further comprises a bleed opening (87), which bleed opening (87) is provided on the bearing block (42) and/or on the housing (1) and communicates the first exhaust gas chamber (81) and/or the second exhaust gas chamber (82) with the air outlet opening (84).

6. The compressor (10) of claim 1, wherein the compressor (10) includes a first gas supply path (71), the first gas supply path (71) being in communication with the first gap (419) and supplying gas to the first gap (419) to form a gas film.

7. The compressor (10) of claim 6, wherein the first air supply path (71) includes an air intake hole (711), a first air supply channel (712), and a first air intake channel (713), the air intake hole (711) being provided on the housing (1) and in communication with the exterior of the housing (1), the first air supply channel (712) being provided on the bearing housing (42) and in communication with the air intake hole (711), the first air intake channel (713) being provided on the radial hydrostatic bearing (41) and in communication with the first air supply channel (712) and the first gap (419).

8. The compressor (10) of claim 7, wherein the radial hydrostatic bearing (41) includes a sleeve (411) and a carrier (412), the sleeve (411) is sleeved outside the carrier (412), the first gap (419) is located between the carrier (412) and an outer surface of the rotor (3), the first air intake passage (713) includes a first passage section (714) and a second passage section (715), the first passage section (714) is disposed on the sleeve (411) and communicates with the first air supply passage (712), and the second passage section (715) is disposed on the carrier (412) and communicates with the first passage section (714) and the first gap (419).

9. The compressor (10) of claim 8, wherein the first channel section (714) includes a first annular groove (716) and a vent hole (717), the first annular groove (716) being disposed on an outer surface of the sleeve (411) in communication with the first gas supply channel (712), the vent hole (717) being disposed at a bottom of the first annular groove (716) and in communication with the first annular groove (716) and the second channel section (715); and/or, the second channel section (715) comprises a second annular groove (718) and a first throttling hole (719), the second annular groove (718) is arranged on the outer surface of the carrier (412) and is communicated with the first channel section (714), and the first throttling hole (719) is arranged at the bottom of the second annular groove (718) and is communicated with the second annular groove (718) and the first gap (419).

10. The compressor (10) of claim 9 wherein the first passage section (714) includes at least two of the vent holes (717), the at least two vent holes (717) being spaced apart along the circumference of the first annular groove (716); and/or the second channel section (715) comprises at least two first throttle openings (719), the at least two first throttle openings (719) being arranged at intervals along the axial and/or circumferential direction of the second annular groove (718).

11. Compressor (10) according to any of claims 1-10, characterized in that the compressor (10) comprises two bearing assemblies (4), the two bearing assemblies (4) being arranged at both axial ends of the rotor (3).

12. The compressor (10) of claim 11, wherein the compressor (10) comprises two first air supply circuits (71), the two first air supply circuits (71) supplying air to first gaps (419) of radial hydrostatic bearings (41) of the two bearing assemblies (4), respectively.

13. The compressor (10) according to any one of claims 1-10, wherein a thrust disc (31) is provided on the rotor (3), the thrust disc (31) being located on a side of the radial hydrostatic bearing (41) remote from the diffuser (43), and wherein the compressor (10) further comprises at least one of:

the first hydrostatic thrust bearing (5) is sleeved on the rotor (3) and arranged on one side of the thrust disc (31) close to the radial hydrostatic bearing (41), a second gap (51) is arranged between the first hydrostatic thrust bearing (5) and the adjacent axial end face of the thrust disc (31), the compressor (10) comprises a second air supply air channel (72), the second air supply air channel (72) is communicated with the second gap (51) so as to supply air to the second gap (51) to form an air film, and the second gap (51) is communicated with a first air exhaust cavity (81) of the air exhaust air channel (8);

The second hydrostatic thrust bearing (6) is sleeved on the rotor (3), and is arranged on one side, far away from the radial hydrostatic bearing (41), of the thrust disc (31), a third gap (61) is formed between the second hydrostatic thrust bearing (6) and the adjacent axial end face of the thrust disc (31), the compressor (10) comprises a third air supply air passage (73), the third air supply air passage (73) is communicated with the third gap (61) so as to supply air to the third gap (61) to form an air film, and the third gap (61) is communicated with the air outlet hole (84).

14. The compressor (10) of claim 13, wherein the second air supply circuit (72) includes a second air supply channel (721), the second air supply channel (721) being disposed on the bearing housing (42) and communicating a first air supply channel (712) of the first air supply circuit (71) of the compressor (10) with the second gap (51); and/or, the third air supply channel (73) comprises a third air supply channel (731), and the third air supply channel (731) is arranged on the bearing seat (42) and is communicated with the first air supply channel (712) of the first air supply channel (71) of the compressor (10) and the third gap (61).

15. The compressor (10) of claim 14 wherein the second supply gas circuit (72) further includes a first supply gas chamber (722) and a second orifice (724), the first supply gas chamber (722) being located between the first hydrostatic thrust bearing (5) and an adjacent axial end face of the bearing housing (42) and in communication with the second supply gas channel (721), the second orifice (724) being disposed on the first hydrostatic thrust bearing (5) and in communication with the first supply gas chamber (722) and the second gap (51); and/or, the third air supply channel (73) comprises a second air supply cavity (732) and a third orifice (734), the second air supply cavity (732) is located between the adjacent axial end surfaces of the second hydrostatic thrust bearing (6) and the sealing cover (97) and is communicated with the third air supply channel (731), the third orifice (734) is arranged on the second hydrostatic thrust bearing (6) and is communicated with the second air supply cavity (732) and the third gap (61), and the sealing cover (97) is sleeved on the rotor (3) and is located on one side, far away from the radial hydrostatic thrust bearing (41), of the second hydrostatic thrust bearing (6).

16. A refrigerant circulation system, characterized by comprising a compressor (10) according to any one of claims 1-15.

17. The refrigerant circulation system of claim 16, wherein the refrigerant circulation system is an air conditioning system.

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