CN111365284A

CN111365284A - Bearing part, compressor and refrigerant circulating system

Info

Publication number: CN111365284A
Application number: CN201811593246.9A
Authority: CN
Inventors: 刘华; 张治平; 亓静利; 李宏波; 钟瑞兴; 陈玉辉; 叶文腾; 刘胜
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2018-12-25
Filing date: 2018-12-25
Publication date: 2020-07-03
Also published as: WO2020134518A1

Abstract

The utility model provides a bearing part, compressor and refrigerant circulation system. The bearing carrying member includes: a bearing chamber for mounting a radial bearing; a mounting hole coaxial and communicating with the bearing chamber; a fluid inlet passage communicating the bearing chamber with an exterior of the bearing carrier; and a fluid outflow passage communicating the mounting hole with an outside of the bearing carrying member. The bearing carrying component provided by the disclosure facilitates supplying fluid to the radial bearing and keeps the back pressure of the radial bearing stable, thereby facilitating stable operation of the compressor.

Description

Bearing part, compressor and refrigerant circulating system

Technical Field

The disclosure relates to the technical field of compressors and refrigeration, in particular to a bearing part, a compressor and a refrigerant circulating system.

Background

The static pressure gas bearing has the advantages of ultrahigh precision, ultralow friction, ultralow vibration, ultralow noise, long service life, no pollution and the like, is suitable for high-speed and high-precision occasions, and has wide application prospect in centrifugal compressors, particularly miniaturized centrifugal compressors. The static pressure gas bearing requires an external gas source for gas supply and requires stable working backpressure of the bearing, so that the gas film damage caused by the fluctuation of the backpressure of the bearing is prevented, and the instability of a bearing rotor system is damaged.

Disclosure of Invention

The purpose of the present disclosure is to provide a bearing part, a compressor and a refrigerant circulating system.

A first aspect of the present disclosure provides a bearing carrier comprising:

a bearing chamber for mounting a radial bearing;

a mounting hole coaxial and communicating with the bearing chamber;

a fluid inlet passage communicating the bearing chamber with an exterior of the bearing carrier; and

and the fluid outflow channel is communicated with the mounting hole and the outside of the bearing part.

In some embodiments, the bearing carrier comprises:

a bearing seat portion to which the bearing chamber is provided; and

the bearing chamber is arranged in the bearing chamber, the diffuser portion and the bearing seat portion are integrally arranged along the axial direction of the bearing chamber side by side, one end, far away from the bearing seat portion, of the diffuser portion is provided with a diffusion structure, and the mounting hole is formed in the diffuser portion.

In some embodiments, a fluid inlet of the fluid inlet passage is disposed on an end surface of the diffuser portion near one end of the bearing seat portion.

In some embodiments, the bearing carrier comprises a plurality of said fluid outflow channels, said plurality of fluid outflow channels being equispaced circumferentially of the bearing carrier.

In some embodiments, the plurality of fluid outflow channels are spaced 360 °/equi-spaced along the circumference of the bearing carrier, where m is the number of the plurality of fluid outflow channels.

In some embodiments, the bearing carrying part comprises a bearing locating structure arranged at the end remote from the mounting hole for axially locating the radial bearing.

In some embodiments, the bearing locating feature includes an annular groove for receiving a snap ring for axially locating the radial bearing, the annular groove being disposed on a sidewall of the bearing housing.

In some embodiments, the bearing-carrying member further includes a diffuser portion mounting hole and/or a diffuser portion positioning hole disposed on the diffuser portion.

In some embodiments, the bearing-carrying member further comprises a carrying-member positioning spigot disposed at an end of the diffuser portion proximate to the bearing seat portion.

In some embodiments, the mounting hole is a stepped hole and includes a large diameter section far away from one end of the bearing chamber and a small diameter section near one end of the bearing chamber, and a stepped positioning surface is formed between the large diameter section and the small diameter section.

The present invention in a second aspect provides a compressor comprising:

a compressor rotor including a main shaft;

a radial bearing for carrying the main shaft; and

a bearing carrying member according to the first aspect of the present disclosure, wherein the radial bearing is mounted in the bearing chamber of the bearing carrying member.

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

In some embodiments, the compressor further includes a shaft seal member, the shaft seal member is mounted in the mounting hole of the bearing carrier member, and one end of the shaft seal member close to the radial bearing has a bearing positioning end surface, and the bearing positioning end surface is matched with an end surface of the radial bearing.

In some embodiments, the shaft seal member includes a shaft seal fluid passage communicating the fluid outflow passage with a gap between the radial bearing and the main shaft.

In some embodiments, the compressor includes a housing, and the bearing-carrying member includes a carrying-member positioning spigot disposed at an end of the diffuser portion proximate to the bearing seat portion, the carrying-member positioning spigot cooperating with the housing.

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

According to the bearing part and the compressor provided by the disclosure, the bearing part comprises a bearing chamber for mounting the radial bearing, a mounting hole which is coaxial and communicated with the bearing chamber, a fluid inlet channel which is communicated with the bearing chamber and the outside of the bearing part, and a fluid outlet channel which is communicated with the mounting hole and the outside of the bearing part, so that the working fluid outside the bearing part can be guided to the bearing chamber through the fluid inlet channel for the radial bearing to use, and the working fluid in the gap between the bearing chamber and the radial bearing can be guided out of the bearing part through the fluid outlet channel, thereby being beneficial to preventing the fluid from being retained near the radial bearing, being beneficial to keeping the back pressure of the radial bearing stable, and being beneficial to the stable operation of the compressor adopting the bearing part.

The compressor and the refrigerant circulating system provided by the disclosure have the same advantages as the bearing part provided by the disclosure.

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

Drawings

The accompanying drawings, which are included to provide a further understanding of the disclosure and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the disclosure and together with the description serve to explain the disclosure and not to limit the disclosure. In the drawings:

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

Fig. 2 is a schematic cross-sectional structural view of a bearing carrier according to an embodiment of the present disclosure.

Fig. 3 is a left side view of the bearing support member shown in fig. 2.

Fig. 4 is a partial structural schematic view of a compressor according to an embodiment of the present disclosure.

Fig. 5 is a schematic perspective view illustrating a shaft seal component of a compressor according to an embodiment of the present disclosure.

Detailed Description

The technical solutions in the embodiments of the present disclosure will be clearly and completely described below with reference to the drawings in the embodiments of the present disclosure, and it is obvious that the described embodiments are only a part of the embodiments of the present disclosure, and not all of the embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the disclosure, its application, or uses. All other embodiments, which can be derived by a person skilled in the art from the embodiments disclosed herein without making any creative effort, shall fall within the protection scope of the present disclosure.

The relative arrangement of the components and steps, the numerical expressions, and numerical values set forth in these embodiments do not limit the scope of the present disclosure unless specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective portions shown in the drawings are not drawn in an actual proportional relationship for the convenience of description. Techniques, methods, and apparatus known to those 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 all examples shown and discussed herein, any particular value should be construed as merely illustrative, and not limiting. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, further discussion thereof is not required in subsequent figures.

In the description of the present disclosure, it should be understood that the terms "first", "second", etc. are used to define the components, and are used only for convenience of distinguishing the corresponding components, and if not otherwise stated, the terms have no special meaning, and thus, should not be construed as limiting the scope of the present disclosure.

In the description of the present disclosure, it is to be understood that the directional terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal" and "top, bottom", etc., are used merely for convenience in describing the present disclosure and for simplicity in description, and in the absence of any contrary indication, these directional terms are not intended to indicate or imply that the referenced device or element must have a particular orientation or be constructed and operated in a particular orientation, and therefore should not be taken as limiting the scope of the present disclosure; the terms "inner and outer" refer to the inner and outer relative to the profile of the respective component itself.

As shown in fig. 1-4, the disclosed embodiment discloses a bearing carrier 60. The bearing carrier 60 includes: a bearing chamber for mounting a radial bearing; a mounting hole 67 coaxial with and communicating with the bearing chamber 62; a fluid inlet passage 63 communicating the bearing chamber 62 with the exterior of the bearing-carrying member 60; and a fluid outflow passage 64 communicating the mounting hole 67 with the outside of the bearing carrier.

The bearing member 60 includes a bearing chamber for mounting the radial bearing, a mounting hole 67 coaxial with and communicating with the bearing chamber 62, a fluid inlet channel 63 communicating the bearing chamber 62 with the outside of the bearing member 60, and a fluid outlet channel 64 communicating the mounting hole 67 with the outside of the bearing member, so that the working fluid outside the bearing member 60 can be introduced to the bearing chamber through the fluid inlet channel 63 for use by the radial bearing, and the working fluid in the gap between the bearing chamber 62 and the radial bearing can be led out of the bearing member 60 through the fluid outlet channel 64, facilitating the back pressure stabilization of the radial bearing.

In some embodiments, the bearing carrying member 60 includes a diffuser portion and a bearing seat portion. The bearing chamber 62 is provided in the bearing seat portion. The diffuser portion and the bearing seat portion are integrally arranged side by side along the axial direction of the bearing chamber 62, one end of the diffuser portion, which is far away from the bearing seat portion, is provided with a diffuser structure, and the mounting hole 67 is arranged in the diffuser portion.

The bearing part 60 of the embodiment of the present disclosure designs the diffuser and the bearing seat as one part, and sets the mounting hole at the same time, thereby integrating the functions of the diffuser and the bearing seat, facilitating the reduction of the number of parts, improving the assembly efficiency, and simultaneously facilitating the reduction of the rotor length and improving the stability of the bearing rotor system.

As shown in fig. 1-4, in some embodiments, the bearing carrier 60 includes a fluid inlet passage 63 that communicates between the bearing chamber 62 and the exterior of the bearing carrier 60. The fluid inlet channel 63 may supply the radial bearing with the fluid, such as the suspension gas, required for carrying the main shaft 21. The fluid inlet passage 63 may be, for example, a bore provided inside the bearing carrier part 60. The pore diameter of the pore channel may be 3mm or more, for example.

As shown in fig. 1 to 4, in some embodiments, the fluid inlet of the fluid inlet passage 63 is provided on an end surface of the diffuser portion near one end of the bearing seat portion. This arrangement facilitates the introduction of fluid into the fluid inlet passage 63 from the exterior, such as within the compressor housing 10.

As shown in fig. 1-4, in some embodiments, the bearing carrier 60 includes a fluid outflow passage 64 that communicates the mounting hole 67 with the exterior of the bearing carrier 60. This setting does benefit to near the fluid that is detained of radial bearing, does benefit to the backpressure that keeps radial bearing stable to do benefit to the stable work of compressor. The fluid outflow channel 64 is an orifice provided inside the bearing support structure 60. As shown in fig. 1 to 4, the fluid outlet of the fluid outflow passage 64 is provided on the end surface of the axial second end of the diffuser portion and/or on the outer peripheral surface of the bearing seat portion.

As shown in fig. 1-4, in some embodiments, the bearing carrier 60 includes a plurality of fluid outflow channels 64. This arrangement facilitates rapid, uniform drainage of fluid adjacent associated components, such as radial bearings, and prevents fluid retention adjacent associated components.

As shown in fig. 1-4, in some embodiments, a plurality of fluid outflow passages 64 are equispaced circumferentially of the bearing carrier 60. This arrangement facilitates rapid, uniform drainage of fluid adjacent associated components, such as radial bearings, and prevents fluid retention adjacent associated components.

As shown in fig. 1-4, in some embodiments, the plurality of fluid outflow channels 64 are evenly spaced at 360 °/(m +1) intervals along the circumference of the bearing carrier 60, where m is the number of the plurality of fluid outflow channels 64. In the embodiment shown in fig. 1 to 4, m is 5. The fluid inlet channel 63 is arranged at the position of the bearing carrier 60 where the fluid outlet channel 64 is not arranged in the circumferential direction, so that all the fluid channels of the bearing carrier 60 are approximately uniformly distributed, and the positioning accuracy during the machining of the fluid channels and the assembly of the bearing carrier 60 is facilitated. The number and distribution of the shaft seal fluid passages of the shaft seal member 70 described later correspond to the number and distribution of the fluid outflow passages 64 provided on the bearing support member 60.

As shown in fig. 1-4, in some embodiments, the bearing-carrying member 60 includes a bearing-locating feature disposed at an end distal from the mounting hole 67 for axially locating the radial bearing. The bearing positioning structure includes a ring groove 66 for mounting a snap ring 81 for axially positioning the radial bearing 43, and the ring groove 66 is provided on the side wall of the bearing chamber 62.

As shown in fig. 3, in some embodiments, the bearing-carrying member 60 further includes a diffuser portion mounting hole and/or a diffuser portion positioning hole 69 provided on the diffuser portion. The diffuser portion positioning hole 69 is used for circumferentially positioning the bearing carrier 60 in cooperation with a positioning pin. The diffuser portion mounting hole is used to mate with a threaded connection to mount the bearing-carrying member 60 to an associated component, such as the compressor housing 10.

As shown in fig. 1-4, in some embodiments, the bearing carrier 60 further includes a carrier locating spigot 68 disposed at an end of the diffuser portion proximate the bearing seat portion. The bearing carrier positioning seam 68 may enable radial positioning and axial positioning of the bearing carrier 60.

As shown in fig. 1-4, in some embodiments, the mounting hole 67 is a stepped hole including a large diameter section near an end away from the bearing chamber 62 and a small diameter section near an end of the bearing chamber 62, with a stepped locating surface 65 formed therebetween. This arrangement facilitates the directional and axial positioning between the shaft seal member 70 and the bearing carrier member 60, as well as the axial positioning of the radial bearing when the bearing locating end face 721 of the shaft seal member 70 is clearance fit with the end face of the radial bearing.

As shown in fig. 1, the embodiment of the present disclosure also provides a compressor. The compressor includes a compressor rotor 20, a radial bearing and a bearing carrying member 60. The compressor rotor 20 includes a main shaft 21. The radial bearing is used to carry the main shaft 21. The bearing carrier 60 is the bearing carrier 60 of the previous embodiment, and the radial bearing is mounted in the bearing chamber 62 of the bearing carrier 60. The bearing part 60 integrates the functions of a diffuser, a bearing seat and a shaft seal mounting seat, is beneficial to reducing the number of parts and improving the assembly efficiency, and is also beneficial to reducing the length of a rotor of the compressor and improving the operation stability of the compressor.

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

As shown in fig. 1-5, in some embodiments, the compressor further includes a shaft seal member 70. The shaft seal member 70 is mounted in the mounting hole 67 of the bearing carrying member 60. One end of the shaft seal member 70 adjacent the radial bearing has a bearing locating end surface 721, and the bearing locating end surface 721 mates with the end surface of the radial bearing. The bearing part 60 simultaneously bears the installation functions of the diffuser, the bearing seat and the shaft seal part, and the shaft seal part 70 and the radial bearing are installed in the bearing part 60, so that the length of the compressor rotor can be shortened by the compressor, the weight of the compressor rotor can be reduced, and the critical rotating speed of the compressor rotor can be improved. The bearing part 60, the shaft seal part 70 and the radial bearing are matched to be beneficial to enabling the structure and arrangement of the compressor to be compact and realizing quick and accurate assembly.

As shown in fig. 1-4, in some embodiments, the shaft seal member 70 includes a shaft seal fluid passage that communicates between the fluid outflow passage 64 and the gap between the radial bearing and the main shaft 21. The shaft seal fluid passage communicates with the fluid outflow passage 64. This setting does benefit to near the fluid that is detained of radial bearing, does benefit to the backpressure that keeps radial bearing stable to do benefit to the stable work of compressor.

As shown in fig. 1, 4 and 5, in some embodiments, the shaft seal member 70 includes a shaft seal disc 71 and a shaft seal locating spigot 72. The center of the shaft seal disc body 71 is provided with a shaft hole, and a shaft seal structure is arranged on the wall of the shaft hole. The shaft seal positioning spigot 72 is coaxially and integrally arranged at one axial end of the shaft seal disc body 71, and a shaft seal fluid passage for communicating the radial inner side and the radial outer side of the shaft seal positioning spigot 72 is arranged on the shaft seal positioning spigot 72.

The shaft seal part 70 has the functions of shaft seal, positioning and fluid discharge, the shaft seal positioning spigot 72 is beneficial to improving the matching precision between the shaft seal part 70 and the sealed spindle 21, fluid leakage can be effectively prevented, a shaft seal fluid passage is beneficial to preventing fluid retention such as a radial bearing matched with the shaft seal part 70, and the back pressure of related parts is beneficial to stabilizing, so that the stability of a bearing rotating system is promoted.

As shown in fig. 1, 4 and 5, in some embodiments, the shaft seal structure of shaft seal member 70 includes a comb-tooth structure 711. Comb tooth structure 711 is more suitable for sealing gas, is suitable for being applied to a compressor, and can effectively prevent pressurized gas from leaking.

As shown in fig. 1, 4 and 5, in some embodiments, the end of the shaft seal locating spigot 72 remote from the shaft seal disc 71 has a bearing locating end surface 721 for axially locating the radial bearing. The bearing positioning end surface 721 enables the shaft seal component 70 to have the axial positioning function of a radial bearing, which is beneficial to simplifying the structure of the device and shortening the length of the rotor of the device.

The configuration of the shaft seal fluid passage can be varied, for example, as shown in fig. 1, 4 and 5, and in some embodiments, the shaft seal fluid passage includes a recess 722 that is recessed from an end distal from the shaft seal disc 71 to an end proximal to the shaft seal disc 71. In an embodiment not shown, the shaft seal fluid passage may include at least one through hole disposed in a sidewall of the shaft seal retention spigot 72. It is also possible to provide both the groove and the through hole as the shaft seal fluid passage.

As shown in fig. 1, 4 and 5, in some embodiments, the shaft seal member 70 includes a plurality of shaft seal fluid passages. The plurality of shaft seal fluid passages are evenly disposed circumferentially along the shaft seal retention spigot 72. This arrangement facilitates rapid, uniform drainage of fluid adjacent associated components, such as radial bearings, and prevents fluid retention adjacent associated components.

In some embodiments, the plurality of shaft seal fluid passages are evenly disposed at angular intervals of 360 °/n +1 along the circumference of the shaft seal positioning spigot 72, where n is the number of the plurality of shaft seal fluid passages. The number of n may be 2, 3, 4, 5, 6 or more. In the embodiment shown in fig. 1, 4 and 5, n is 5. The number and distribution of the shaft seal fluid passages advantageously corresponds to the number and distribution of the fluid outlet passages 64 provided in the bearing support member 60. This arrangement facilitates the bearing carrier 60 to cooperate to form a fluid exhaust path, facilitating a location for the fluid entry passage of the associated component.

As shown in fig. 5, in some embodiments, the shaft seal fluid passage of the shaft seal member 70 is a plurality of recesses 722 disposed on the shaft seal locating spigot 72. The number of the grooves 722 is not limited, and may be, for example, 3 to 12. The fluid outflow channels 64 of the bearing carrying structure 60 are the same number as the grooves 722.

In addition, the shaft seal member 70 includes a shaft seal attachment hole 712 and a shaft seal positioning hole 713 provided on the shaft seal disc 71. The shaft seal positioning hole 713 can accurately determine the connection position between the shaft seal component 70 and the bearing component 60, and is favorable for quickly and accurately communicating the shaft seal fluid passage with the fluid outflow passage 64 of the bearing component 60. The shaft seal attachment holes 712 facilitate removable attachment to associated components via threaded connections.

As shown in fig. 1, 4 and 5, in some embodiments, the diameter of the inner peripheral surface of the shaft seal positioning spigot 72 is larger than the diameter of the shaft hole of the shaft seal disc 71. This arrangement facilitates communicating the shaft seal fluid passages with the gap between the radial bearing and the main shaft 21 and facilitates uniform distribution of fluid between the shaft seal fluid passages.

As shown in fig. 1, 4 and 5, in the compressor according to the embodiment of the present disclosure, the shaft seal structure of the shaft seal member 70 is engaged with the main shaft 21. The shaft seal fluid passage communicates with the gap between the radial bearing and the main shaft 21. This setting does benefit to and prevents that fluid from being detained near journal bearing, does benefit to the back pressure that keeps journal bearing stable to do benefit to and guarantee compressor steady operation.

As shown in fig. 1, 4 and 5, in some embodiments, an end of the shaft seal locating spigot 72 remote from the shaft seal disc 71 has a bearing locating end surface 721 for axially locating the radial bearing, the bearing locating end surface 721 being clearance fit with a corresponding end surface of the radial bearing. The arrangement ensures that the shaft seal part 70 simultaneously bears the axial positioning function of the radial bearing, is beneficial to shortening the length of the compressor rotor, reduces the weight of the compressor rotor and the whole machine and simplifies the structure of the compressor.

1-4, in some embodiments, the mounting bore 67 is a stepped bore including a large diameter section located near one end of the diffuser structure and a small diameter section located away from one end of the diffuser structure. The shaft seal disc body 71 is arranged in the large-diameter section and matched with the large-diameter section, and the shaft seal positioning spigot 72 is arranged in the small-diameter section and matched with the small-diameter section. A step positioning surface 65 is formed between the large-diameter section and the small-diameter section, and an end surface 714 of the shaft seal disc body 71 close to the positioning ring is in clearance fit with the step positioning surface 65. This arrangement facilitates axial positioning of the bearing member 70. Meanwhile, the shaft seal component has the axial positioning function of the radial bearing, so that the axial positioning of the radial bearing is facilitated.

As shown in fig. 1, the bearing receiving member 60 includes a receiving member positioning spigot 68 provided at one end of the diffuser near the bearing seat portion, and a diffuser portion positioning hole 69 and a diffuser portion mounting hole provided on the diffuser portion. The bearing positioning spigot 68 cooperates with the right end inner wall of the motor cylinder 11 of the compressor housing 10 to determine the radial and axial position of the bearing carrier 60. The bearing support member 60 is circumferentially positioned between the positioning member inserted into the diffuser portion positioning hole 69 and the housing 10, and is fixedly connected to the housing 10 by a screw connection member inserted into the diffuser portion mounting hole.

The embodiment of the disclosure also provides a refrigerant circulating system, which comprises the compressor of the embodiment of the disclosure.

The compressor and the refrigerant circulation system of the embodiment of the present disclosure have the corresponding advantages of the bearing support member 60 of the embodiment of the present disclosure.

Some embodiments of the present disclosure are described in further detail below with reference to fig. 1-5.

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

The casing 10 includes a motor cylinder 11, and a first-stage volute 12 and a second-stage volute 13 respectively connected to the left and right ends of the motor cylinder 11. The left end of the motor barrel 11 is provided with an end wall, and the right end is open.

The first-stage diffuser 50, the bearing member 60, and the shaft seal member 70 installed in the installation hole 67 of the bearing member 60 are respectively disposed at the left and right ends of the motor cylinder 11, and divide the inner space of the casing 10 into a motor accommodating chamber 14 located in the middle of the casing 10, a first-stage compression chamber 15 located at the left end of the casing 10, and a second-stage compression chamber 16 located at the right end of the casing 10.

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

The motor stator 30 is fixed on the inner wall of the motor cylinder 11 and is provided with a rotor mounting hole. The inner wall of the motor cylinder 11 may be provided with a spiral groove for introducing a cooling fluid for cooling the motor stator 30.

The main shaft 21 is disposed in the motor stator 30 and penetrates through a rotor mounting hole of the motor stator 30. The middle part of the main shaft 21 is provided with a permanent magnet for generating a magnetic field, and the left end and the right end of the permanent magnet are respectively provided with a first end shaft section and a second end shaft section. Therefore, in the present embodiment, the main shaft 21 is also a motor rotor of the motor of the compressor. The motor stator 30 and the main shaft 21 constitute a motor of the compressor. The windings of the motor stator 30 are energized to rotate the main shaft 21, thereby rotating the entire compressor rotor.

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

A thrust disc member 24 is disposed adjacent the primary impeller 22 and includes a thrust disc and an integrally disposed mounting sleeve. The thrust disk member 24 is fixedly fitted around the outer periphery of the first end shaft section of the main shaft 21. The mounting sleeve is located between the primary impeller 22 and the thrust disc. The thrust disc member 24 may be shrink-fitted onto the first end shaft section of the main shaft 21.

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

As shown in fig. 1, the thrust bearing assembly 41 includes a first thrust bearing 411, a second thrust bearing 412, and a thrust bearing retaining ring 413. In the embodiment shown in fig. 1-5, the first thrust bearing 411, the second thrust bearing 412, the first radial bearing 42, and the second radial bearing are all hydrostatic gas bearings.

The left end of the one-stage diffuser 50 has a diffuser structure, such as a diffuser surface or diffuser vanes. The first-stage diffuser 50 has a shaft hole in the center thereof, and a shaft seal structure, such as a comb structure, is disposed in the shaft hole. The thrust disc member 24 is mounted in the axial bore of the first stage diffuser 50 and is fitted with a shaft seal arrangement provided in the axial bore. The radially outer end of the first-stage diffuser 50 is sealingly fixed to the end wall of the motor cylinder 11, so that the first-stage diffuser 50 separates the first-stage compression chamber 15 at the left end of the casing 10 from the motor accommodating chamber 14 in the middle of the casing 10.

As shown in fig. 1, the right end of the first-stage diffuser 50 is provided with a diffuser positioning spigot, the left end of the end wall of the motor barrel 11 is provided with a diffuser mounting opening, and the diffuser positioning spigot of the first-stage diffuser 50 is mounted in the diffuser mounting opening and matched with the diffuser mounting opening, so that the axial and radial positioning of the first-stage diffuser 50 is realized. The inner part of the diffuser positioning spigot of the first-stage diffuser 50 and the bottom wall of the diffuser mounting opening of the motor barrel 11 enclose a thrust bearing assembly mounting chamber.

The thrust bearing assembly 41 is disposed within the thrust bearing assembly mounting chamber. The left and right end faces of the thrust disk member 24 are respectively fitted with the first thrust face of the first thrust bearing 411 and the second thrust face of the second thrust bearing 412, so that the thrust disk defines the axial position of the compressor rotor 21 together with the first thrust bearing 411 and the second thrust bearing 412.

The radial outer end of the first thrust surface of the first thrust bearing 411 is also provided with a first positioning surface, the radial outer end of the second thrust surface of the second thrust bearing 412 is also provided with a second positioning surface, the left end surface and the right end surface of the thrust bearing positioning ring 413 are in clearance fit with the first positioning surface and the second positioning surface respectively, therefore, the distance between the left end surface and the right end surface of the thrust bearing positioning ring 413 can limit the distance between the first thrust surface and the second thrust surface, and the sum of the gap between the thrust disc and the first thrust surface and the gap between the thrust disc and the second thrust surface can be limited. The thrust bearing positioning ring 413 is fixedly connected to the second thrust bearing 42 and the end wall of the motor barrel 11 through a threaded connection.

The thrust bearing retainer ring 413 has a retainer ring fluid passage communicating between its radially inner and radially outer sides. The retaining ring fluid passage facilitates ensuring that the back pressure of the thrust bearing assembly is stable, thereby facilitating stable operation of the compressor.

A radially intermediate portion of the end wall of the motor cartridge 10 is provided with an end wall bearing chamber in which a first radial bearing 42 is provided. The left end of the first radial bearing 42 is in clearance fit with one side of the second thrust bearing 412, which is far away from the second thrust surface, and the right end of the first radial bearing 42 is in clearance fit with the snap ring 82 installed in the snap groove of the end wall bearing chamber, so that the axial position of the first radial bearing 42 is determined by the second thrust bearing 412 and the snap ring 82 together.

The bearing carrying member 60 integrates a diffuser (a two-stage diffuser in the embodiment shown in fig. 1) and a bearing housing, and the second radial bearing 43 is mounted in a bearing chamber 62 of the bearing carrying member 60. The second radial bearing 43 is fitted around the second end shaft section of the main shaft 21.

The shaft seal member 70 is fixedly mounted in the mounting hole 67 of the bearing support member 60. As described above, the bearing support member 60 is fixedly mounted on the right end of the motor cylinder 11. And the bearing part 60 is connected with the motor cylinder 11 in a sealing way. After the shaft seal member 70 is mounted on the bearing carrier 60 and sleeved outside the main shaft 21, a seal is formed between the shaft seal structure in the shaft hole of the bearing member 70 and the second end shaft section of the main shaft 21, and the radially outer end of the bearing member 70 is connected with the radially inner end of the bearing carrier 60 in a sealing manner, so that the shaft seal member 70 and the bearing carrier 60 isolate the second compression chamber 16 of the housing 10 from the motor accommodating chamber 14.

After the bearing support member 60, the shaft seal member 70 and the second radial bearing 43 are assembled, the bearing positioning end surface 721 of the shaft seal member 70 is in clearance fit with the right end surface of the second radial bearing 43, and the left end of the second radial bearing 43 is in clearance fit with the snap ring 81, so that the axial position of the second radial bearing 43 is determined by the shaft seal member 70 and the snap ring 81. Meanwhile, each shaft seal fluid passage of the shaft seal member 70 communicates with each fluid outflow passage 64 of the bearing carrying member 60 correspondingly.

As shown in fig. 1, the motor cylinder 11 is provided with a first gas inlet passage 17 for supplying a suspension gas to the first radial bearing 42 and the second radial bearing 43. The fluid inlet channel 63 of the bearing carrier 60 is connected to the first gas inlet channel 17 through a fluid inlet disposed on the diffuser portion end surface thereof, so that the suspension gas can be introduced into the bearing chamber of the bearing carrier 60, and pass through the porous medium of the second radial bearing 43 to enter the gap between the second radial bearing 43 and the second end shaft segment of the main shaft 21, and then enter the inner cavity of the positioning ring 72 of the shaft seal member 70, and then enter the fluid outlet channel 64 of each corresponding bearing carrier 60 through each shaft seal fluid channel, and then enter the motor accommodating cavity 14, and then flow out of the housing 10 through an outlet (not shown) disposed on the motor cylinder 11.

In this embodiment, the housing 10 is further provided with a second gas inlet passage for supplying the suspension gas to the thrust bearing assembly 41, which is independent of the first gas inlet passage. The suspension gas in the second gas inlet channel is supplied to the inside of the first thrust bearing 411 and the second thrust bearing 412 respectively, and enters the gap between the first thrust surface and the thrust disk and the gap between the second thrust surface and the thrust disk through the porous medium of the first thrust bearing 411 and the porous medium of the second thrust bearing 412, and then flows to the motor accommodating chamber 14 through the positioning ring fluid channel on the positioning ring 413 of the thrust bearing. The positioning ring fluid channel on the thrust bearing positioning ring 413 facilitates timely removal of the suspended gas, ensuring stable backpressure of the thrust bearing assembly 41.

In some embodiments, not shown, the second gas inlet channel may be in communication with the first gas inlet channel such that each of the branch flow channels and each of the gas bearings corresponding to the branch flow channels may be supplied with the suspension gas through the same housing gas inlet and the same main flow channel.

As shown in fig. 4, the arrows therein indicate the flow path of the suspension gas supplied to the second radial bearing 43. The suspension gas enters the fluid inlet channel 63 and the bearing chamber 62 of the bearing carrier 60 from the first gas inlet channel 17 at the bottom of the motor cylinder 11, and then is supplied to the second radial bearing 43, the suspension gas enters the inside of the second radial bearing 43, passes through the porous medium throttling of the second radial bearing 43, enters the gap between the second radial bearing 43 and the main shaft 21, and forms a gas film in the gap between the second radial bearing 43 and the main shaft 21, so that the main shaft 21 is floated, and then is discharged from both ends of the gap. The levitation gas discharged from the left end enters the motor accommodating chamber 14 and is then discharged from the housing 10 together with the cooling gas cooling the motor. The suspension gas discharged from the right end passes through the shaft seal fluid passages of the shaft seal member 70 into the fluid outflow passages 64 of the bearing support structure 60 and then into the motor accommodating chamber 14, and is discharged from the housing 10 together with the cooling gas for cooling the motor.

The hydrostatic gas bearings are required to have high accuracy, and the bearing gap is generally 10 μm or less. The sealing gap of the shaft seal structure of the shaft seal part 70 is preferably smaller and better under the condition of ensuring relative rotation, for example, the sealing gap can be as low as 0.02mm, the requirement on the coaxiality of the shaft seal structure and the main shaft 21 is high due to the small sealing gap, and the shaft seal part 70 realizes the positioning of parts related to the compressor, such as the bearing part 70 and the shell 10, through the shaft seal positioning spigot 72, so that the coaxiality of the shaft seal structure and the main shaft 21 is favorably ensured.

The shaft seal structure sets up to the broach structure, with the main shaft 21 cooperation, can prevent compressor secondary impeller 23's exhaust to get into bearing chamber 62 of bearing carrier 60, does benefit to and reduces the compressor and reveals the loss, improves the efficiency of compressor, also does benefit to simultaneously and prevents that bearing chamber 62's backpressure from increasing because of revealing the volume too greatly.

The back pressure of the bearing chamber 62 affects the pressure distribution of the air film between the second radial bearing 43 and the main shaft 21, and further affects the bearing stiffness and damping, which affect the dynamic stability of the rotor, and on the other hand, the fluctuation of the bearing back pressure also causes the bearing to whirl, so that the stability of the back pressure is guaranteed in the use of the static pressure gas bearing, which is beneficial to the stability of the bearing rotor system. The shaft seal fluid passage of the shaft seal member 70 and the fluid outflow passage 64 of the bearing support structure 60 prevent the gas discharged from the left end from being retained in the shaft seal member 70 and the bearing support member 60, and thus effectively prevent the bearing back pressure of the second radial bearing 43 from being unstable.

The bearing positioning end surface 721 of the shaft seal member 70 is in clearance fit with the right end surface of the second radial bearing 43, and limits the axial position of the second radial bearing 43 together with the snap ring 81, so that bearing instability caused by the left and right play of the second radial bearing 43 can be prevented.

It can be seen that the shaft seal component 70 of the embodiment of the present disclosure is beneficial to reducing leakage loss and simultaneously is beneficial to ensuring stable working back pressure of the radial bearing adjacent to the shaft seal component 70, thereby being beneficial to improving energy efficiency of the compressor and stability of the bearing rotor system.

The bearing part 60 of the embodiment of the present disclosure designs the diffuser and the bearing seat into one part, and sets the shaft seal mounting hole at the same time, so that the functions of the diffuser, the bearing seat and the shaft seal mounting seat are integrated, the reduction of the number of parts is facilitated, the assembly efficiency is improved, the reduction of the length of the compressor rotor is facilitated, and the stability of the bearing rotor system is improved.

Because bearing carrier 60 has fluid entering channel 63 and fluid outflow channel 64, do benefit to and guarantee that second radial bearing 43 normally works and the work backpressure is stable, do benefit to and improve bearing rotor system stability, have diffuser portion effect concurrently simultaneously, reduced part quantity, reduce compressor rotor's length, improve bearing rotor system stability.

The bearing part 60 is positioned doubly by matching the bearing part positioning spigot 68 and the diffuser part positioning hole 69 with the positioning pin, the bearing part 60 and the bearing chamber 62 thereof can be ensured to be coaxial with the main shaft 21 by using the bearing part positioning spigot 68 and the right end surface and the inner wall surface of the motor cylinder 11, and further the coaxiality of the second radial bearing 43 assembled with the main shaft 21 is ensured, and the bearing part 60 can be accurately positioned in the circumferential direction by matching the pin with the diffuser part positioning hole 69. Therefore, the bearing support member 60 can improve the assembling efficiency and precision.

Because the bearing clearance of the static pressure gas bearing is generally several microns to tens of microns, the rotating machinery supported by the static pressure gas bearing has extremely high requirement on the coaxial bearings of the two radial bearings, if the coaxiality is poor, the performance of the bearing is reduced, and the rotor can not float in serious cases. The bearing-carrying structure 60 and the bearing component 70 cooperating therewith of the disclosed embodiment are therefore suitable for use in a compressor that employs a hydrostatic gas bearing for carrying. Of course, while the bearing carrier 60 and shaft seal member 70 of the disclosed embodiments are applicable to compressors employing gas bearings, such as centrifugal compressors, it is not precluded that the bearing carrier 60 and shaft seal member 70 of the disclosed embodiments are employed in other rotary systems.

Finally, it should be noted that: the above examples are intended only to illustrate the technical solutions of the present disclosure and not to limit them; although the present disclosure has been described in detail with reference to preferred embodiments, those of ordinary skill in the art will understand that: modifications to the embodiments of the disclosure or equivalent replacements of parts of the technical features may be made, which are all covered by the technical solution claimed by the disclosure.

Claims

1. A bearing carrier (60), comprising:

a bearing chamber (62) for mounting a radial bearing;

a mounting hole (67) coaxial with and communicating with the bearing chamber (62);

a fluid inlet passage (63) communicating the bearing chamber (62) with the exterior of the bearing carrier (60); and

a fluid outflow passage (64) communicating the mounting hole (67) with an outside of the bearing carrying member (60).

2. The bearing carrier (60) of claim 1 wherein the bearing carrier (60) comprises:

a bearing seat portion to which the bearing chamber (62) is provided; and

the diffuser portion, the diffuser portion with bearing housing portion is integrative follows the axial of bearing chamber (62) sets up side by side, the diffuser portion is kept away from the one end of bearing housing portion is provided with the diffusion structure, mounting hole (67) set up in the diffuser portion.

3. The bearing carrier (60) of claim 2 wherein the fluid inlet of the fluid inlet passage (63) is disposed on an end face of the diffuser portion proximate to the end of the bearing seat portion.

4. The bearing carrier (60) of claim 1 wherein said bearing carrier (60) comprises a plurality of said fluid outflow channels (64), said plurality of fluid outflow channels (64) being equispaced circumferentially of said bearing carrier (60).

5. The bearing carrier (60) of claim 4 wherein the plurality of fluid outflow channels (64) are evenly spaced at 360 °/(m +1) intervals along a circumferential direction of the bearing carrier (60), where m is the number of the plurality of fluid outflow channels (64).

6. The bearing carrier (60) of claim 1 wherein said bearing carrier (60) includes a bearing locating feature disposed at said end remote from said mounting aperture (67) for axially locating said radial bearing.

7. The bearing carrier (60) of claim 6 wherein said bearing locating feature comprises an annular groove (66) for receiving a snap ring (81) for axially locating said radial bearing (43), said annular groove (66) being disposed on a side wall of said bearing chamber (62).

8. The bearing carrier (60) of any of claims 2 to 7 wherein the bearing carrier (60) further comprises a diffuser portion mounting hole and/or a diffuser portion positioning hole (69) disposed on the diffuser portion.

9. The bearing carrier (60) of any of claims 2 to 7 wherein the bearing carrier (60) further comprises a carrier locating spigot (68) disposed at an end of the diffuser portion proximate the bearing seat portion.

10. The bearing carrier (60) according to any one of claims 1 to 7, wherein the mounting hole (67) is a stepped hole comprising a large diameter section distal from one end of the bearing chamber (62) and a small diameter section proximal to one end of the bearing chamber (62), the large diameter section and the small diameter section forming a stepped locating surface (65) therebetween.

11. A compressor, comprising:

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

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

a bearing carrier (60) being the bearing carrier (60) of any one of claims 1 to 9, the radial bearing being mounted within the bearing chamber (62) of the bearing carrier (60).

12. The compressor of claim 11, wherein the radial bearing is a gas bearing.

13. The compressor of claim 11, further comprising a shaft seal member (70), wherein the shaft seal member (70) is mounted in the mounting hole (67) of the bearing carrying member (60), one end of the shaft seal member (70) close to the radial bearing has a bearing positioning end surface (721), and the bearing positioning end surface (721) is engaged with an end surface of the radial bearing.

14. The compressor of claim 13, wherein the shaft seal member (70) includes a shaft seal fluid passage communicating between the fluid outflow passage (64) and a gap between the radial bearing and the main shaft (21).

15. The compressor of claim 14, including a housing (10), wherein the bearing carrier (60) includes a carrier locating spigot (68) disposed at an end of the diffuser portion proximate the bearing seat portion, the carrier locating spigot (68) engaging the housing (10).

16. A refrigerant circulation system comprising the compressor of any one of claims 11 to 15.