WO2020134518A1 - 轴承承载部件、压缩机和冷媒循环系统 - Google Patents

轴承承载部件、压缩机和冷媒循环系统 Download PDF

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Publication number
WO2020134518A1
WO2020134518A1 PCT/CN2019/113992 CN2019113992W WO2020134518A1 WO 2020134518 A1 WO2020134518 A1 WO 2020134518A1 CN 2019113992 W CN2019113992 W CN 2019113992W WO 2020134518 A1 WO2020134518 A1 WO 2020134518A1
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WO
WIPO (PCT)
Prior art keywords
bearing
positioning
radial
shaft seal
compressor
Prior art date
Application number
PCT/CN2019/113992
Other languages
English (en)
French (fr)
Inventor
刘华
张治平
亓静利
李宏波
钟瑞兴
陈玉辉
叶文腾
刘胜
Original Assignee
珠海格力电器股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
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Application filed by 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Publication of WO2020134518A1 publication Critical patent/WO2020134518A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/002—Details, component parts, or accessories especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/122—Shaft sealings using sealing-rings especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0603—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion
    • F16C32/0614—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion the gas being supplied under pressure, e.g. aerostatic bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0662—Details of hydrostatic bearings independent of fluid supply or direction of load
    • F16C32/067—Details of hydrostatic bearings independent of fluid supply or direction of load of bearings adjustable for aligning, positioning, wear or play
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0681—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
    • F16C32/0696—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for both radial and axial load

Definitions

  • the present disclosure relates to the technical field of compressors and refrigeration, in particular to a bearing bearing component, a compressor and a refrigerant circulation system.
  • Hydrostatic gas bearings have the advantages of ultra-high precision, ultra-low friction, ultra-low vibration, ultra-low noise, long life, and no pollution. They are also suitable for high-speed and high-precision occasions. Has broad application prospects.
  • the static pressure gas bearing requires external air source to supply gas, and the bearing back pressure is required to be stable, to prevent the gas film damage caused by the fluctuation of the bearing back pressure, and the bearing rotor system instability is destroyed.
  • a first aspect of the present disclosure provides a bearing bearing component, including:
  • the mounting hole is coaxial and communicates with the bearing chamber
  • a fluid inlet channel that connects the bearing chamber to the outside of the bearing carrying member
  • the fluid outflow channel communicates the mounting hole with the outside of the bearing carrying member.
  • the bearing bearing component includes:
  • a bearing seat portion, the bearing chamber is provided in the bearing seat portion;
  • a diffuser part, the diffuser part and the bearing seat part are integrally arranged side by side along the axial direction of the bearing chamber, and the diffuser part is provided with a diffuser structure at the end away from the bearing seat part,
  • the mounting hole is provided in the diffuser section.
  • the fluid inlet of the fluid inlet channel is provided on an end surface of the diffuser portion near one end of the bearing seat portion.
  • the bearing carrier member includes a plurality of the fluid outflow channels, and the plurality of fluid outflow channels are evenly distributed along the circumferential direction of the bearing carrier member.
  • the plurality of fluid outflow channels are evenly spaced 360°/(m+1) along the circumferential direction of the bearing carrying member, where m is the number of the plurality of fluid outflow channels.
  • the bearing bearing member includes a bearing positioning structure provided at the end remote from the mounting hole for axial positioning of the radial bearing.
  • the bearing positioning structure includes a ring groove for installing a snap ring for axial positioning of the radial bearing, and the ring groove is provided on a side wall of the bearing chamber .
  • the bearing bearing member further includes at least one of a diffuser part mounting hole and a diffuser part positioning hole provided on the diffuser part.
  • the bearing bearing member further includes a bearing member positioning stop provided at an end of the diffuser portion near the bearing seat portion.
  • the mounting hole is a stepped hole, including a large diameter section away from one end of the bearing chamber and a small diameter section near one end of the bearing chamber, and a step is formed between the large diameter section and the small diameter section Positioning surface.
  • the second aspect of the present disclosure provides a compressor, including:
  • Compressor rotor including main shaft
  • the bearing bearing member is the bearing bearing member according to the first aspect of the present disclosure, and the radial bearing is installed in the bearing chamber of the bearing bearing member.
  • the radial bearing is a gas bearing.
  • the compressor further includes a shaft seal member installed in the mounting hole of the bearing bearing member, and an end of the shaft seal member near the radial bearing has bearing positioning At the end face, the bearing positioning end face cooperates with the end face of the radial bearing.
  • the shaft seal component includes a shaft seal fluid channel that communicates the fluid outflow channel and the gap between the radial bearing and the main shaft.
  • the compressor includes a housing
  • the bearing bearing member includes a bearing housing portion and a diffuser portion disposed side by side along the axial direction of the bearing chamber integrally with the bearing housing portion, the The bearing bearing member further includes a bearing member positioning stop provided at an end of the diffuser portion close to the bearing seat portion, the bearing member positioning stop fitting with the housing.
  • a third aspect of the present disclosure provides a refrigerant circulation system including the compressor described in the second aspect of the present disclosure.
  • the bearing bearing component includes a bearing chamber for mounting a radial bearing, a mounting hole coaxial with and communicating with the bearing chamber, a fluid inlet channel connecting the bearing chamber and the outside of the bearing bearing member, and It connects the mounting hole with the fluid outflow channel outside the bearing carrier part, therefore, the working fluid outside the bearing carrier part can be led to the bearing chamber through the fluid inlet channel for radial bearings, and the bearing chamber can be connected to the radial direction through the fluid outflow channel
  • the working fluid in the gap between the bearings leads out of the bearing load-bearing component, which helps prevent fluid from staying near the radial bearing and helps maintain the back pressure of the radial bearing stable, thereby facilitating the stable operation of the compressor using the bearing load-bearing component.
  • the compressor and the refrigerant circulation system provided by the present disclosure have the same advantages as the bearing bearing member provided by the present disclosure.
  • FIG. 1 is a schematic structural diagram of a compressor according to some embodiments of the present disclosure.
  • FIG. 2 is a schematic cross-sectional structural view of a bearing bearing component of some embodiments of the present disclosure.
  • FIG. 3 is a schematic view of the left side view of the bearing carrier shown in FIG. 2.
  • FIG. 4 is a partial structural diagram of a compressor according to some embodiments of the present disclosure.
  • FIG. 5 is a schematic perspective view of a shaft seal component of a compressor according to some embodiments of the present disclosure.
  • an embodiment of the present disclosure provides a bearing bearing member 60.
  • the bearing carrying member 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 that communicates the bearing chamber 62 with the outside of the bearing carrying member 60; and a fluid outlet passage 64. Connect the mounting hole 67 to the outside of the bearing carrying part.
  • the bearing carrying member 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 outside of the bearing carrying member 60, and a communicating mounting hole 67 with
  • the fluid outflow passage 64 outside the bearing carrying part therefore, the working fluid outside the bearing carrying part 60 can be led to the bearing chamber 62 through the fluid inlet passage 63 for radial bearings, and the bearing chamber 62 can be separated from the bearing chamber 62 through the fluid outflow passage 64
  • the working fluid in the gap between the radial bearings leads out of the bearing bearing member 60, which is conducive to the stability of the back pressure of the radial bearings.
  • the bearing carrier 60 includes a diffuser portion and a bearing seat portion.
  • the bearing chamber 62 is provided in the bearing seat.
  • the diffuser portion and the bearing housing portion are provided side by side in the axial direction of the bearing chamber 62 integrally.
  • the diffuser portion is provided with a diffuser structure at the end away from the bearing housing portion, and the mounting hole 67 is provided in the diffuser portion.
  • the bearing bearing member 60 of the embodiment of the present disclosure designs the diffuser and the bearing seat as one part, and at the same time provides mounting holes, integrating the functions of the diffuser and the bearing seat, which is beneficial to reducing the number of parts, improving assembly efficiency, and also reducing The small rotor length improves the stability of the bearing rotor system.
  • the bearing carrier 60 includes a fluid inlet passage 63 that connects the bearing chamber 62 and the outside of the bearing carrier 60.
  • the fluid inlet passage 63 can supply the radial bearing with the fluid required to carry the main shaft 21, such as a suspension gas.
  • the fluid inlet passage 63 may be, for example, a hole provided inside the bearing carrying member 60.
  • the hole diameter of the channel can be, for example, 3 mm or more.
  • the fluid inlet of the fluid inlet channel 63 is provided on the end surface of the diffuser portion near one end of the bearing seat portion. This arrangement facilitates the introduction of fluid into the channel 63 from the outside, such as the casing 10 of the compressor.
  • the bearing carrying member 60 includes a fluid outflow channel 64 that communicates the mounting hole 67 and the outside of the bearing carrying member 60. This arrangement is helpful to prevent fluid from staying near the radial bearing, and to keep the back pressure of the radial bearing stable, thereby facilitating the stable operation of the compressor.
  • the fluid outflow channel 64 is a hole provided inside the bearing carrying member 60. As shown in FIGS. 1 to 4, the fluid outlet of the fluid outflow channel 64 is provided on the end surface of the second axial end of the diffuser portion and/or the outer peripheral surface of the bearing seat portion.
  • the bearing carrying member 60 includes a plurality of fluid outflow channels 64. This arrangement facilitates the rapid and uniform discharge of the fluid near the relevant components, such as radial bearings, and prevents the fluid from staying near the relevant components.
  • a plurality of fluid outflow channels 64 are evenly distributed along the circumferential direction of the bearing carrier member 60. This arrangement facilitates the rapid and uniform discharge of the fluid near the relevant components, such as radial bearings, and prevents the fluid from staying near the relevant components.
  • a fluid inlet channel 63 is arranged at a position where the fluid outflow channel 64 is not arranged in the circumferential direction of the bearing carrier member 60. This arrangement can make all the fluid channels of the bearing carrier member 60 substantially evenly distributed, which is advantageous for the processing of the fluid channel and the assembly of the bearing carrier member 60 Positioning accuracy.
  • the number and distribution of the shaft seal fluid channels of the shaft seal member 70 described later correspond to the number and distribution of the fluid outflow channels 64 provided on the bearing carrying member 60.
  • the bearing bearing member 60 includes a bearing positioning structure provided at an end remote from the mounting hole 67 for axially positioning the radial bearing.
  • the bearing positioning structure includes a ring groove 66 for installing a snap ring 81 for axially positioning the radial bearing.
  • the ring groove 66 is provided on the side wall of the bearing chamber 62.
  • the bearing bearing member 60 further includes at least one of a diffuser part mounting hole 692 and a diffuser part positioning hole 691 provided on the diffuser part.
  • the positioning hole 691 of the diffuser part is used for positioning the bearing carrying member 60 in the circumferential direction in cooperation with the positioning pin.
  • the diffuser part mounting hole 692 is used to mount the bearing bearing member 60 on a related component, such as the casing 10 of the compressor, in cooperation with a screw connection.
  • the bearing bearing member 60 further includes a bearing member positioning stop 68 provided at an end of the diffuser portion near the bearing seat portion.
  • the bearing member positioning stop 68 can realize the radial positioning and the axial positioning of the bearing bearing member 60.
  • the mounting hole 67 is a stepped hole, including a large-diameter section close to the end away from the bearing chamber 62 and a small-diameter section close to the end of the bearing chamber 62, between the large-diameter section and the small-diameter section Between the step positioning surface 65.
  • This arrangement facilitates the directional positioning and axial positioning between the shaft seal member 70 and the bearing bearing member 60.
  • the bearing positioning end surface 721 of the shaft seal member 70 and the end surface clearance of the radial bearing fit together it also facilitates the axial direction of the radial bearing Positioning.
  • an embodiment of the present disclosure also provides a compressor.
  • the compressor includes a compressor rotor 20, a radial bearing, and a bearing bearing member 60.
  • the compressor rotor 20 includes a main shaft 21. Radial bearings are used to carry the main shaft 21.
  • the bearing bearing member 60 is the bearing bearing member 60 of the foregoing embodiment, and the radial bearing is installed in the bearing chamber 62 of the bearing bearing member 60.
  • the bearing bearing member 60 integrates the functions of a diffuser, a bearing seat, and a shaft seal mounting seat, which is beneficial to reducing the number of parts and improving the assembly efficiency, and at the same time, is beneficial to reducing the length of the compressor rotor and improving the operation stability of the compressor.
  • the radial bearing is a gas bearing.
  • the compressor further includes a shaft seal member 70.
  • the shaft seal member 70 is installed in the mounting hole 67 of the bearing carrier member 60.
  • the 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 cooperates with the end surface of the radial bearing.
  • the bearing bearing member 60 simultaneously assumes the function of installing the diffuser, the bearing seat and the shaft seal member, and the shaft seal member 70 and the radial bearing are installed in the bearing bearing member 60, which helps the compressor shorten the length of the compressor rotor and reduce the compressor rotor
  • the weight is beneficial to increase the critical speed of the compressor rotor.
  • the cooperation of the bearing bearing member 60, the shaft seal member 70 and the radial bearing is beneficial to make the compressor structure and arrangement compact, and can realize rapid and accurate assembly.
  • the shaft seal member 70 includes a shaft seal fluid channel that communicates the fluid outflow channel 64 and the gap between the radial bearing and the main shaft 21.
  • the shaft seal fluid channel is in communication with the fluid outflow channel 64. This arrangement is helpful to prevent fluid from staying near the radial bearing, and to keep the back pressure of the radial bearing stable, thereby facilitating the stable operation of the compressor.
  • the shaft seal component 70 includes a shaft seal disc body 71 and a shaft seal positioning stop 72.
  • the shaft seal disc body 71 has a shaft hole in the center, and a shaft seal structure is provided on the hole wall of the shaft hole.
  • the shaft seal positioning stop 72 is coaxially and integrally provided at one axial end of the shaft seal disc body 71, and the shaft seal positioning stop 72 is provided with a shaft seal connecting the radial inner side and the radial outer side of the shaft seal positioning stop 72 Fluid channel.
  • the shaft seal member 70 has the functions of shaft seal, positioning and fluid discharge.
  • the shaft seal positioning stop 72 is beneficial to improve the cooperation accuracy between the shaft seal member 70 and the sealed main shaft 21, which can prevent fluid leakage more effectively.
  • the fluid channel helps prevent fluids such as radial bearings cooperating with the shaft seal member 70 from stagnating fluid, helps stabilize the back pressure of related components, and thus improves the stability of the bearing rotor system.
  • the shaft seal structure of the shaft seal member 70 includes a comb-tooth structure 711.
  • Comb-tooth structure 711 is more suitable for sealing gas, suitable for use in compressors, and can effectively prevent leakage of pressurized gas.
  • the end of the shaft seal positioning stop 72 away from the shaft seal disc body 71 has a bearing positioning end surface 721 for axial positioning of the radial bearing.
  • the bearing positioning end surface 721 makes the shaft sealing member 70 also have the axial positioning function of the radial bearing, which is beneficial to simplify the structure of the device and shorten the rotor length of the device.
  • the structural form of the shaft seal fluid channel can be various, for example, as shown in FIGS. 1, 4 and 5, in some embodiments, the shaft seal fluid channel includes the end away from the shaft seal disc 71 toward the shaft seal A recess 722 in which one end of the disc body 71 is recessed.
  • the shaft seal fluid channel may include at least one through hole provided on the side wall of the shaft seal positioning stop 72. It is also possible to provide both grooves and through holes as shaft seal fluid channels.
  • the shaft seal component 70 includes multiple shaft seal fluid channels.
  • a plurality of shaft seal fluid channels are evenly arranged along the circumferential direction of the shaft seal positioning stop 72. This arrangement facilitates the rapid and uniform discharge of the fluid near the relevant components, such as radial bearings, and prevents the fluid from staying near the relevant components.
  • the plurality of shaft seal fluid channels are uniformly arranged at an angular interval of 360°/(n+1) along the circumferential direction of the shaft seal positioning stop 72, where n is the number of the plurality of shaft seal fluid channels.
  • the number and distribution modes of the shaft seal fluid channels are favorable to correspond to the number and distribution modes of the fluid outflow channels 64 provided on the bearing carrying member 60. This arrangement mode facilitates the bearing bearing member 60 to form a fluid discharge passage, and facilitates to reserve a setting position for the arrangement of the fluid inlet channel of the related parts.
  • the shaft seal fluid channel of the shaft seal member 70 is a plurality of grooves 722 provided on the shaft seal positioning stop 72.
  • the number of grooves 722 is not limited, and may be 3-12, for example.
  • the number of fluid outflow channels 64 and grooves 722 of the bearing carrier 60 is the same.
  • the shaft seal member 70 includes a shaft seal connection hole 712 and a shaft seal positioning hole 713 provided on the shaft seal disk 71.
  • the shaft seal positioning hole 713 can accurately determine the connection position between the shaft seal member 70 and the bearing bearing member 60, which facilitates quick and accurate communication between the shaft seal fluid channel and the fluid outflow channel 64 of the bearing bearing member 60.
  • the shaft seal connection hole 712 facilitates detachable connection with related components through a threaded connection.
  • the diameter of the inner circumferential surface of the shaft seal positioning stop 72 is larger than the diameter of the shaft hole of the shaft seal disk 71. This arrangement facilitates the communication between the shaft seal fluid channel and the gap between the radial bearing and the main shaft 21, and facilitates the uniform distribution of fluid among the shaft seal fluid channels.
  • the shaft seal structure of the shaft seal member 70 cooperates with the main shaft 21.
  • the shaft seal fluid channel communicates with the gap between the radial bearing and the main shaft 21. This arrangement helps to prevent fluid from staying near the radial bearing, and helps to keep the back pressure of the radial bearing stable, thereby helping to ensure the stable operation of the compressor.
  • the end of the shaft seal positioning stop 72 away from the shaft seal disc body 71 has a bearing positioning end surface 721 for axial positioning of the radial bearing.
  • the positioning end face 721 is in clearance fit with the corresponding end face of the radial bearing.
  • the mounting hole 67 of the bearing bearing member 60 is a stepped hole, including a large-diameter section located at an end near the diffuser structure and a small-diameter section away from the end at the diffuser structure.
  • the shaft seal disc body 71 is installed in the large-diameter section and cooperates with the large-diameter section, the shaft seal positioning stop 72 is installed in the small-diameter section, and the outer circumferential surface 723 of the shaft seal is matched with the small-diameter section.
  • a step positioning surface 65 is formed between the large-diameter section and the small-diameter section, and the end surface 714 of the shaft seal disc 71 near the shaft seal positioning stop 72 is in clearance fit with the step positioning surface 65.
  • This arrangement facilitates the axial positioning of the bearing member 70.
  • the shaft seal member 70 assumes the axial positioning function of the radial bearing, it is also beneficial to the axial positioning of the radial bearing.
  • the bearing carrying member 60 includes a bearing member positioning stop 68 provided at an end of the diffuser near the bearing seat portion and a diffuser portion positioning hole 691 provided on the diffuser portion The diffuser part mounting hole 692.
  • the bearing member positioning stop 68 cooperates with the inner wall of the right end of the motor barrel 11 of the casing 10 of the compressor to determine the radial position and the axial position of the bearing bearing member 60.
  • the bearing bearing member 60 is circumferentially positioned between the positioning member penetrating the positioning hole 691 of the diffuser portion and the housing 10, and is fixedly connected to the housing 10 by a threaded connector passing through the mounting hole 692 of the diffuser portion.
  • An embodiment of the present disclosure also provides a refrigerant circulation system, including the compressor of the embodiment of the present disclosure.
  • the compressor and refrigerant circulation system of the embodiments of the present disclosure have the corresponding advantages of the bearing bearing member 60 of the embodiments of the present disclosure.
  • the compressor mainly includes a housing 10, a compressor rotor 20, a motor stator 30, a bearing assembly, a primary diffuser 50, a bearing bearing member 60 and a shaft seal member 70.
  • the housing 10 includes a motor barrel 11 and a primary volute 12 and a secondary volute 13 respectively connected to the left and right ends of the motor barrel 11.
  • the left end of the motor barrel 11 has an end wall, and the right end is open.
  • the first-stage diffuser 50, the bearing bearing member 60, and the shaft seal members 70 installed in the mounting holes 67 of the bearing bearing member 60 are provided at the left and right ends of the motor barrel 11, respectively, and divide the internal space of the housing 10 into The motor accommodating chamber 14 in the middle of the housing 10, the primary compression chamber 15 at the left end of the housing 10 and the secondary compression chamber 16 at the right end of the housing 10.
  • the compressor rotor 20 mainly includes a main shaft 21, a first-stage impeller 22, a second-stage impeller 23, and a thrust disk member 24.
  • the motor stator 30 is fixed to the inner wall of the motor barrel 11 and has a rotor mounting hole.
  • a spiral groove may be provided on the inner wall of the motor barrel 11 for passing cooling fluid for cooling the motor stator 30.
  • the main shaft 21 is provided in the motor stator 30 and penetrates the rotor mounting hole of the motor stator 30.
  • the central part of the main shaft 21 is provided with a permanent magnet for generating a magnetic field, and the left and right ends of the permanent magnet are respectively provided with a first end shaft segment and a second end shaft segment. Therefore, in this 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 compressor motor. After the winding of the motor stator 30 is energized, the main shaft 21 is rotated, thereby driving the entire compressor rotor to rotate.
  • 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 first-stage impeller 22 and the first-stage diffuser 50 is located in the first-stage compression chamber 15.
  • the diffuser structure on the secondary impeller 23 and the bearing bearing member 60 is located in the secondary compression chamber 16.
  • the thrust disk component 24 is disposed near the first-stage impeller 22 and includes a thrust disk and an integrally installed mounting sleeve.
  • the thrust disc member 24 is fixedly fitted on the outer periphery of the first end shaft section of the main shaft 21.
  • the mounting sleeve is located between the first-stage impeller 22 and the thrust disk.
  • the thrust disc member 24 can be sleeved on the first end shaft section of the main shaft 21 by means of a hot sleeve.
  • the bearing assembly includes a thrust bearing assembly 41, a first radial bearing 42 and a second radial bearing 43.
  • the thrust bearing assembly 41 includes a first thrust bearing 411, a second thrust bearing 412 and a thrust bearing positioning ring 413.
  • the first thrust bearing 411, the second thrust bearing 412, the first radial bearing 42 and the second radial bearing 43 are all static pressure gas bearings.
  • the left end of the primary diffuser 50 has a diffuser structure, such as a diffuser surface or diffuser blade.
  • the center of the first-stage diffuser 50 is provided with a shaft hole, and a shaft seal structure, such as a comb tooth structure, is provided in the shaft hole.
  • the mounting sleeve of the thrust disc component 24 is located in the shaft hole of the first-stage diffuser 50 and cooperates with the shaft seal structure provided in the shaft hole.
  • the radially outer end of the first-stage diffuser 50 is hermetically fixed to the end wall of the motor barrel 11 so that the first-stage diffuser 50 isolates the first-stage compression chamber 15 at the left end of the housing 10 from the motor housing in the middle of the housing 10 ⁇ 14.
  • the right end of the first-stage diffuser 50 has a diffuser positioning stop
  • the left end of the end wall of the motor barrel 11 has a diffuser installation port
  • the first-stage diffuser 50 has a diffuser positioning stop It is installed in the installation port of the diffuser and cooperates with the installation port of the diffuser, so as to realize the axial and radial positioning of the primary diffuser 50.
  • the inside of the diffuser positioning stop of the first-stage diffuser 50 and the bottom wall of the diffuser mounting opening of the motor barrel 11 form a thrust bearing assembly installation chamber.
  • the thrust bearing assembly 41 is installed in the thrust bearing assembly installation chamber.
  • the left and right end surfaces of the thrust disk of the thrust disk member 24 cooperate with the first thrust surface of the first thrust bearing 411 and the second thrust surface of the second thrust bearing 412, respectively, so that the thrust disk and the first thrust bearing 411 and the second thrust bearing 412 collectively define the axial position of the compressor rotor 21.
  • the radially outer end of the first thrust surface of the first thrust bearing 411 is further provided with a first positioning surface
  • the radially outer end of the second thrust surface of the second thrust bearing 412 is further provided with a second positioning surface
  • the thrust bearing positioning ring The left and right end surfaces of 413 are in clearance fit with the first and second positioning surfaces, respectively, so that the distance between the left and right end surfaces of the thrust bearing positioning ring 413 can define the distance between the first thrust surface and the second thrust surface, The sum of the clearance between the thrust disk and the first thrust surface and the clearance between the thrust disk and the second thrust surface may be defined.
  • the thrust bearing positioning ring 413 is fixedly connected to the second thrust bearing 42 and the end wall of the motor barrel 11 through a threaded connection.
  • the thrust bearing locating ring 413 is provided with a locating ring fluid channel for connecting the radially inner side and the radially outer side.
  • the locating ring fluid channel is conducive to ensuring the stability of the back pressure of the thrust bearing assembly, thereby facilitating the stable operation of the compressor.
  • An end wall bearing chamber is provided in the radial middle of the end wall of the motor barrel 10, and the first radial bearing 42 is provided in the end wall bearing chamber.
  • the left end of the first radial bearing 42 is in clearance fit with the side of the second thrust bearing 412 away from the second thrust surface, and the right end of the first radial bearing 42 is in clearance with the snap ring 82 installed in the snap groove of the end wall bearing chamber
  • 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 carrier 60 integrates a diffuser (in the embodiment shown in FIG. 1, a two-stage diffuser) and a bearing housing, and the second radial bearing 43 is installed in the bearing chamber 62 of the bearing carrier 60.
  • the second radial bearing 43 is sleeved on the outer periphery of the second end shaft section of the main shaft 21.
  • the shaft seal member 70 is fixedly installed in the mounting hole 67 of the bearing carrier member 60. As described above, the bearing bearing member 60 is fixedly mounted on the right end of the motor barrel 11. And the bearing bearing member 60 and the motor barrel 11 are in a sealed connection. After the shaft seal member 70 is mounted on the bearing bearing member 60 and fitted outside the main shaft 21, the seal structure in the shaft hole of the bearing member 70 forms a seal with the second end shaft section of the main shaft 21, and the bearing member 70 is radially outward The end is hermetically connected to the radially inner end of the bearing carrying member 60 so that the shaft sealing member 70 and the bearing carrying member 60 isolate the second compression chamber 16 of the housing 10 from the motor receiving chamber 14.
  • 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
  • the clearance fit with the snap ring 81 allows the axial position of the second radial bearing 43 to be determined by the shaft seal member 70 and the snap ring 81 together.
  • the respective shaft seal fluid channels of the shaft seal member 70 communicate with the respective fluid outflow channels 64 of the bearing bearing member 60.
  • the motor barrel 11 is provided with a first gas inlet passage 17 for supplying suspended gas to the first radial bearing 42 and the second radial bearing 43.
  • the fluid inlet passage 63 of the bearing carrying member 60 communicates with the first gas inlet passage 17 through the fluid inlet provided on the end face of the diffuser portion thereof, so that the suspended gas can be passed into the bearing chamber 62 of the bearing carrying member 60 and pass through
  • the porous medium of the second radial bearing 43 enters the gap between the second radial bearing 43 and the second end shaft section of the main shaft 21, and then enters the inner cavity of the shaft seal positioning stop 72 of the shaft seal member 70, and then
  • the shaft seal fluid channel enters the corresponding fluid outflow channel 64 of each bearing bearing member 60, and then enters the motor accommodating chamber 14, and then flows out of the housing 10 through an outlet (not shown) provided on the motor barrel 11.
  • the housing 10 is also provided with a second gas inlet channel for supplying the suspension gas to the thrust bearing assembly 41, and the second gas inlet channel is independent of the first gas inlet channel.
  • the suspended gas of the second gas inlet channel is supplied into the first thrust bearing 411 and the second thrust bearing 412 respectively, and enters the first thrust surface and the thrust through the porous medium of the first thrust bearing 411 and the porous medium of the second thrust bearing 412
  • the gap between the discs and the gap between the second thrust surface and the thrust discs then flow to the motor accommodating chamber 14 through the positioning ring fluid channel on the thrust bearing positioning ring 413.
  • the positioning ring fluid channel on the thrust bearing positioning ring 413 facilitates the timely removal of suspended gas and ensures the stable back pressure of the thrust bearing assembly 41.
  • the second gas inlet channel may communicate with the first gas inlet channel, so that each branch flow channel and the corresponding branch flow channel Each gas bearing supplies suspended gas.
  • the arrows therein indicate the flow path of the suspended gas supplied to the second radial bearing 43.
  • the suspension gas enters the fluid inlet passage 63 and the bearing chamber 62 of the bearing bearing member 60 from the first gas inlet passage 17 at the bottom of the motor barrel 11, and then supplies the second radial bearing 43 to suspend the 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 the suspended gas flows between the second radial bearing 43 and the main shaft 21 A gas film is formed in the gap between them, the main shaft 21 is floated, and then discharged from both ends of the gap.
  • the suspended gas discharged from the left end enters the motor accommodating chamber 14 and then is discharged from the housing 10 together with the cooling gas that cools the motor.
  • the suspended gas discharged from the right end enters the fluid outflow channels 64 of the bearing bearing member 60 through the shaft seal fluid passages on the shaft seal member 70, and then enters the motor accommodating chamber 14 together with the cooling gas for cooling the motor from the housing 10 discharge.
  • Hydrostatic gas bearings are required to have high accuracy, and the bearing clearance is generally below 10 ⁇ m.
  • the sealing gap of the shaft seal structure of the shaft seal member 70 should also be as small as possible while ensuring relative rotation.
  • the sealing gap can be as low as 0.02 mm.
  • Such a small sealing gap has a coaxiality between the shaft seal structure and the main shaft 21
  • the requirements are very high, and the shaft seal member 70 realizes the positioning of the compressor-related components, such as the bearing bearing member 70 and the housing 10 through the shaft seal positioning stop 72, which helps to ensure the coaxiality of the shaft seal structure and the main shaft 21.
  • the shaft seal structure is configured as a comb-tooth structure, which cooperates with the main shaft 21 to prevent the exhaust gas of the second-stage impeller 23 of the compressor from entering the bearing chamber 62 of the bearing bearing member 60, which is beneficial to reduce the compressor leakage loss and improve the energy efficiency of the compressor. It is also advantageous to prevent the back pressure of the bearing chamber 62 from increasing due to too much leakage.
  • the back pressure of the bearing chamber 62 affects the gas film pressure distribution between the second radial bearing 43 and the main shaft 21, which in turn affects the bearing stiffness and damping, which in turn affects the rotor dynamic stability.
  • the bearing Back pressure fluctuations can also cause bearing vortex. Therefore, the static pressure gas bearing is used to ensure that the back pressure is stable and it is beneficial to ensure 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 bearing member 60 prevent the gas discharged from the left end from being retained in the shaft seal member 70 and the bearing bearing member 60, thus effectively preventing the bearing of the second radial bearing 43
  • the back pressure is 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 together with the snap ring 81, restricts the axial position of the second radial bearing 43 to prevent the second radial bearing 43 from moving around Cause bearing instability.
  • the shaft seal member 70 of the embodiment of the present disclosure is beneficial to reduce leakage loss and to ensure the stable working back pressure of the radial bearing adjacent to the shaft seal member 70, thereby improving the energy efficiency of the compressor and the bearing rotor System stability.
  • the bearing bearing member 60 of the embodiment of the present disclosure designs the diffuser and the bearing seat as one part, and at the same time provides the shaft seal mounting hole, integrating the functions of the diffuser, the bearing seat and the shaft seal mounting seat, which is beneficial to reducing the number of parts and improving
  • the assembly efficiency also helps to reduce the length of the compressor rotor and improve the stability of the bearing rotor system.
  • the bearing bearing member 60 Since the bearing bearing member 60 has a fluid inlet channel 63 and a fluid outlet channel 64, it is conducive to ensuring the normal operation of the second radial bearing 43 and the stable working back pressure, which is beneficial to improving the stability of the bearing rotor system, and at the same time has the role of the diffuser part, reducing The number of parts is reduced, the length of the compressor rotor is reduced, and the stability of the bearing rotor system is improved.
  • the bearing bearing member 60 adopts the bearing member positioning stop 68 and the diffuser part positioning hole 691 together with the positioning pin to perform double positioning, and the bearing member positioning stop 68 and the right end surface and inner wall surface of the motor barrel 11 can ensure the bearing bearing member 60 and its bearing chamber 62 and the coaxiality of the main shaft 21, thereby ensuring the coaxiality of the second radial bearing 43 and the main shaft 21 after assembly, through the pin and the diffuser part positioning hole 691, the bearing bearing member 60 Precise positioning in the circumferential direction. Therefore, the bearing carrying member 60 can improve assembly efficiency and accuracy.
  • the bearing bearing member 60 of the embodiment of the present disclosure and the bearing member 70 cooperating therewith are suitable for compressors bearing with static pressure gas bearings.
  • the bearing bearing member 60 and the shaft seal member 70 of the embodiment of the present disclosure are suitable for compressors using gas bearings, such as centrifugal compressors, it is not excluded that the bearing bearing member 60 of the embodiment of the present disclosure is adopted in other rotating systems ⁇ 70 ⁇ The shaft seal 70.

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Abstract

一种轴承承载部件、压缩机和冷媒循环系统。轴承承载部件（60）包括：轴承室（62），用于安装径向轴承；安装孔（67），与轴承室（62）同轴且连通；流体进入通道（63），连通轴承室（62）与轴承承载部件（60）外部；和流体流出通道（64），连通安装孔（67）与轴承承载部件（60）外部。该轴承承载部件（60）利于向径向轴承供应流体并保持径向轴承的背压稳定，从而利于压缩机稳定工作。

Description

轴承承载部件、压缩机和冷媒循环系统
相关申请
本公开是以申请号为201811593246.9，申请日为2018年12月25日，发明名称为“轴承承载部件、压缩机和冷媒循环系统”的中国专利申请为基础，并主张其优先权，该中国专利申请的公开内容在此作为整体引入本公开中。
技术领域
本公开涉及压缩机及制冷技术领域，特别涉及一种轴承承载部件、压缩机和冷媒循环系统。
背景技术
静压气体轴承具有超高精度、超低摩擦、超低振动、超低噪音、寿命长、无污染等优点，同时适用于高转速和高精度场合，在离心压缩机特别是小型化离心压缩机中具有广阔应用前景。静压气体轴承由于需要外部气源供气，且要求轴承工作背压稳定，防止轴承背压波动造成气膜破坏，使轴承转子系统失稳遭到破坏。
发明内容
本公开第一方面提供一种轴承承载部件，包括：
轴承室，用于安装径向轴承；
安装孔，与所述轴承室同轴且连通；
流体进入通道，连通所述轴承室与所述轴承承载部件外部；和
流体流出通道，连通所述安装孔与所述轴承承载部件外部。
在一些实施例中，所述轴承承载部件包括：
轴承座部，所述轴承室设置于所述轴承座部；和
扩压器部，所述扩压器部与所述轴承座部一体地沿所述轴承室的轴向并排设置，所述扩压器部远离所述轴承座部的一端设置有扩压结构，所述安装孔设置于所述扩压器部。
在一些实施例中，所述流体进入通道的流体入口设置于所述扩压器部的靠近所述轴承座部一端的端面上。
在一些实施例中，所述轴承承载部件包括多个所述流体流出通道，所述多个流体流出通道沿所述轴承承载部件的周向均布。
在一些实施例中，所述多个流体流出通道沿所述轴承承载部件的周向间隔360°/(m+1)均布，其中，m为所述多个流体流出通道的数量。
在一些实施例中，所述轴承承载部件包括设置于所述远离所述安装孔的一端的用于对所述径向轴承进行轴向定位的轴承定位结构。
在一些实施例中，所述轴承定位结构包括环槽，所述环槽用于安装对所述径向轴承进行轴向定位的卡环，所述环槽设置于所述轴承室的侧壁上。
在一些实施例中，所述轴承承载部件还包括设置于所述扩压器部上的扩压器部安装孔和扩压器部定位孔至少之一。
在一些实施例中，所述轴承承载部件还包括设置于所述扩压器部的靠近所述轴承座部的一端的承载部件定位止口。
在一些实施例中，所述安装孔为台阶孔，包括远离所述轴承室一端的大径段和靠近所述轴承室一端的小径段，所述大径段与所述小径段之间形成台阶定位面。
本开第二方面提供一种压缩机，包括：
压缩机转子，包括主轴；
径向轴承，用于承载所述主轴；和
轴承承载部件，为本公开第一方面所述的轴承承载部件，所述径向轴承安装于所述轴承承载部件的所述轴承室内。
在一些实施例中，所述径向轴承为气体轴承。
在一些实施例中，所述压缩机还包括轴封部件，所述轴封部件安装于所述轴承承载部件的安装孔内，所述轴封部件的靠近所述径向轴承的一端具有轴承定位端面，所述轴承定位端面与所述径向轴承的端面配合。
在一些实施例中，所述轴封部件包括连通所述流体流出通道与所述径向轴承与所述主轴之间的间隙的轴封流体通道。
在一些实施例中，所述压缩机包括壳体，所述轴承承载部件包括轴承座部和与所述轴承座部一体地沿所述轴承室的轴向并排设置的扩压器部，所述轴承承载部件还包括设置于所述扩压器部的靠近所述轴承座部的一端的承载部件定位止口，所述承载部件定位止口与所述壳体配合。
本公开第三方面提供一种冷媒循环系统，包括本公开第二方面所述的压缩机。
根据本公开提供的轴承承载部件和压缩机，轴承承载部件包括用于安装径向轴承的轴承室、与轴承室同轴且连通的安装孔、连通轴承室与轴承承载部件外部的流体进入通道和连通安装孔与轴承承载部件外部的流体流出通道，因此，能通过流体进入通道将轴承承载部件外部的工作流体引向轴承室供径向轴承使用，并能通过流体流出通道将轴承室与径向轴承之间的间隙内的工作流体引出轴承承载部件，利于防止径向轴承附近滞留流体，利于保持径向轴承的背压稳定，从而利于采用该轴承承载部件的压缩机稳定工作。
本公开提供的压缩机和冷媒循环系统具有本公开提供的轴承承载部件相同的优点。
通过以下参照附图对本公开的示例性实施例的详细描述，本公开的其它特征及其优点将会变得清楚。
附图说明
此处所说明的附图用来提供对本公开的进一步理解，构成本公开的一部分，本公开的示意性实施例及其说明用于解释本公开，并不构成对本公开的不当限定。在附图中：
图1为本公开一些实施例的压缩机的结构示意图。
图2为本公开一些实施例的轴承承载部件的剖视结构示意图。
图3为图2所示的轴承承载部件的左视结构示意图。
图4为本公开一些实施例的压缩机的局部结构示意图。
图5为本公开一些实施例的压缩机的轴封部件的立体结构示意图。
具体实施方式
下面将结合本公开实施例中的附图，对本公开实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本公开一部分实施例，而不是全部的实施例。以下对至少一个示例性实施例的描述实际上仅仅是说明性的，决不作为对本公开及其应用或使用的任何限制。基于本公开中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本公开保护的范围。
除非另外具体说明，否则在这些实施例中阐述的部件和步骤的相对布置、数字表达式和数值不限制本公开的范围。同时，应当明白，为了便于描述，附图中所示出的 各个部分的尺寸并不是按照实际的比例关系绘制的。对于相关领域普通技术人员已知的技术、方法和设备可能不作详细讨论，但在适当情况下，所述技术、方法和设备应当被视为授权说明书的一部分。在这里示出和讨论的所有示例中，任何具体值应被解释为仅仅是示例性的，而不是作为限制。因此，示例性实施例的其它示例可以具有不同的值。应注意到：相似的标号和字母在下面的附图中表示类似项，因此，一旦某一项在一个附图中被定义，则在随后的附图中不需要对其进行进一步讨论。
在本公开的描述中，需要理解的是，使用“第一”、“第二”等词语来限定零部件，仅仅是为了便于对相应零部件进行区别，如没有另行声明，上述词语并没有特殊含义，因此不能理解为对本公开保护范围的限制。
在本公开的描述中，需要理解的是，方位词如“前、后、上、下、左、右”、“横向、竖向、垂直、水平”和“顶、底”等，仅是为了便于描述本公开和简化描述，在未作相反说明的情况下，这些方位词并不指示和暗示所指的装置或元件必须具有特定的方位或者以特定的方位构造和操作，因此不能理解为对本公开保护范围的限制；方位词“内、外”是指相对于各部件本身的轮廓的内外。
如图1至图4所示，本公开实施例提供一种轴承承载部件60。该轴承承载部件60包括：轴承室，用于安装径向轴承；安装孔67，与轴承室62同轴且连通；流体进入通道63，连通轴承室62与轴承承载部件60外部；和流体流出通道64，连通安装孔67与轴承承载部件外部。
该轴承承载部件60包括用于安装径向轴承的轴承室、与轴承室62同轴且连通的安装孔67、连通轴承室62与轴承承载部件60外部的流体进入通道63和连通安装孔67与轴承承载部件外部的流体流出通道64，因此，能通过流体进入通道63将轴承承载部件60外部的工作流体引向轴承室62供径向轴承使用，并能通过流体流出通道64将轴承室62与径向轴承之间的间隙内的工作流体引出轴承承载部件60，利于径向轴承的背压稳定。
在一些实施例中，轴承承载部件60包括扩压器部和轴承座部。轴承室62设置于轴承座部。扩压器部与轴承座部一体地沿轴承室62的轴向并排设置，扩压器部远离轴承座部的一端设置有扩压结构，安装孔67设置于扩压器部。
本公开实施例的轴承承载部件60将扩压器和轴承座设计成一个零件，同时设置安装孔，集成了扩压器和轴承座的功能，利于减少零件数量，提高装配效率，同时也利于减小转子长度，提高轴承转子系统的稳定性。
如图1至图4所示，在一些实施例中，轴承承载部件60包括连通轴承室62与轴承承载部件60外部的流体进入通道63。流体进入通道63可以为径向轴承供应承载主轴21所需的流体，如悬浮气体。流体进入通道63例如可以为设置于轴承承载部件60内部的孔道。该孔道的孔径例如可以在3mm以上。
如图1至图4所示，在一些实施例中，流体进入通道63的流体入口设置于扩压器部的靠近轴承座部一端的端面上。该设置利于流体从外部，如压缩机的壳体10内，导入流体进入通道63。
如图1至图4所示，在一些实施例中，轴承承载部件60包括连通安装孔67与轴承承载部件60外部的流体流出通道64。该设置利于防止径向轴承附近滞留流体，利于保持径向轴承的背压稳定，从而利于压缩机稳定工作。流体流出通道64为设置于轴承承载部件60内部的孔道。如图1至图4所示，流体流出通道64的流体出口设置于扩压器部的轴向第二端的端面上和/或轴承座部的外周面上。
如图1至图4所示，在一些实施例中，轴承承载部件60包括多个流体流出通道64。该设置利于相关部件如径向轴承附近的流体快速、均匀排出，利于防止流体在相关部件附近滞留。
如图1至图4所示，在一些实施例中，多个流体流出通道64沿轴承承载部件60的周向均布。该设置利于相关部件如径向轴承附近的流体快速、均匀排出，利于防止流体在相关部件附近滞留。
如图1至图4所示，在一些实施例中，多个流体流出通道64沿轴承承载部件60的周向间隔360°/(m+1)均布，其中，m为多个流体流出通道64的数量。在图1至图4所示的实施例中，m＝5。轴承承载部件60的周向未布置流体流出通道64的位置，布置有流体进入通道63，该设置可以使轴承承载部件60的所有流体通道大致分布均匀，利于流体通道加工和轴承承载部件60组装时定位准确。后面描述的轴封部件70的轴封流体通道的数量及分布方式与设置于轴承承载部件60上的流体流出通道64的数量及分布方式对应一致。
如图1至图4所示，在一些实施例中，轴承承载部件60包括设置于远离安装孔67的一端的用于对径向轴承进行轴向定位的轴承定位结构。轴承定位结构包括环槽66，用于安装对径向轴承进行轴向定位的卡环81，环槽66设置于轴承室62的侧壁上。
如图3所示，在一些实施例中，轴承承载部件60还包括设置于扩压器部上的扩压器部安装孔692和扩压器部定位孔691至少之一。扩压器部定位孔691用于配合定 位销钉对轴承承载部件60进行周向定位。扩压器部安装孔692用于配合螺纹连接件将轴承承载部件60安装于相关部件如压缩机的壳体10上。
如图1至图4所示，在一些实施例中，轴承承载部件60还包括设置于扩压器部的靠近轴承座部的一端的承载部件定位止口68。承载部件定位止口68可以实现轴承承载部件60的径向定位和轴向定位。
如图1至图4所示，在一些实施例中，安装孔67为台阶孔，包括靠近远离轴承室62一端的大径段和靠近轴承室62一端的小径段，大径段与小径段之间形成台阶定位面65。该设置利于轴封部件70与轴承承载部件60之间的定向定位和轴向定位，在轴封部件70的轴承定位端面721与径向轴承的端面间隙配合时，还利于径向轴承的轴向定位。
如图1所示，本公开实施例还提供一种压缩机。该压缩机包括压缩机转子20、径向轴承和轴承承载部件60。压缩机转子20包括主轴21。径向轴承用于承载主轴21。轴承承载部件60为前述实施例的轴承承载部件60，径向轴承安装于轴承承载部件60的轴承室62内。轴承承载部件60集成了扩压器、轴承座和轴封安装座的功能，利于减少零件数量，提高装配效率，同时也利于减小压缩机转子长度，提高压缩机的运行稳定性。
在一些实施例中，径向轴承为气体轴承。
如图1至图5所示，在一些实施例中，压缩机还包括轴封部件70。轴封部件70安装于轴承承载部件60的安装孔67内。轴封部件70的靠近径向轴承的一端具有轴承定位端面721，轴承定位端面721与径向轴承的端面配合。轴承承载部件60同时承担扩压器、轴承座与轴封部件安装的功能，将轴封部件70和径向轴承安装于轴承承载部件60内，利于压缩机缩短压缩机转子长度，减轻压缩机转子重量，利于提高压缩机转子的临界转速。轴承承载部件60、轴封部件70和径向轴承配合利于使压缩机结构及布置紧凑，能实现快速、准确组装。
如图1至图4所示，在一些实施例中，轴封部件70包括连通流体流出通道64与径向轴承与主轴21之间的间隙的轴封流体通道。轴封流体通道与流体流出通道64连通。该设置利于防止径向轴承附近滞留流体，利于保持径向轴承的背压稳定，从而利于压缩机稳定工作。
如图1、图4和图5所示，在一些实施例中，轴封部件70包括轴封盘体71和轴封定位止口72。轴封盘体71中心具有轴孔，轴孔的孔壁上设有轴封结构。轴封定位 止口72同轴且一体地设置于轴封盘体71的轴向一端，轴封定位止口72上设有连通轴封定位止口72的径向内侧和径向外侧的轴封流体通道。
该轴封部件70兼具轴封、定位和排出流体功能，轴封定位止口72利于提高轴封部件70与所密封的主轴21之间的配合精度，可以更有效地防止流体泄漏，轴封流体通道利于防止与轴封部件70配合的如径向轴承滞留流体，利于稳定相关部件的背压，从而利于提升轴承转子系统稳定性。
如图1、图4和图5所示，在一些实施例中，轴封部件70的轴封结构包括梳齿结构711。梳齿结构711更适于密封气体，适于应用于压缩机中，能有效防止带压气体泄漏。
如图1、图4和图5所示，在一些实施例中，轴封定位止口72远离轴封盘体71的一端具有用于对径向轴承进行轴向定位的轴承定位端面721。轴承定位端面721使轴封部件70兼具了径向轴承的轴向定位功能，利于简化所在装置的结构，缩短所在装置的转子长度。
轴封流体通道的结构形式可以为多种，例如，如图1、图4和图5所示，在一些实施例中，轴封流体通道包括从远离轴封盘体71的一端向靠近轴封盘体71的一端凹入的凹槽722。在未图示的实施例中，轴封流体通道可以包括设置于轴封定位止口72的侧壁上的至少一个通孔。还可以同时设置凹槽和通孔作为轴封流体通道。
如图1、图4和图5所示，在一些实施例中，轴封部件70包括多个轴封流体通道。多个轴封流体通道沿轴封定位止口72的周向均匀设置。该设置利于相关部件如径向轴承附近的流体快速、均匀排出，利于防止流体在相关部件附近滞留。
在一些实施例中，多个轴封流体通道沿轴封定位止口72的周向以360°/(n+1)的角度间隔均匀设置，其中，n为多个轴封流体通道的数量。n的数量可以为2、3、4、5、6或更多。如图1、图4和图5所示的实施例中，n＝5。轴封流体通道的数量及分布方式利于与设置于轴承承载部件60上的流体流出通道64的数量及分布方式相对应。该设置方式利于轴承承载部件60配合形成流体排出通路，利于为相关部件的流体进入通道的设置预留设置位置。
如图5所示，在一些实施例中，轴封部件70的轴封流体通道为设置于轴封定位止口72上的多个凹槽722。凹槽722的数量不限，例如可以是3-12个。轴承承载部件60的流体流出通道64与凹槽722的数量相同。
另外，轴封部件70包括设置于轴封盘体71上的轴封连接孔712和轴封定位孔713。 轴封定位孔713可以准确确定轴封部件70与轴承承载部件60之间的连接位置，利于快速、准确实现轴封流体通道与轴承承载部件60的流体流出通道64连通。轴封连接孔712利于通过螺纹连接件实现与相关部件的可拆卸连接。
如图1、图4和图5所示，在一些实施例中，轴封定位止口72的内周面的直径大于轴封盘体71的轴孔的直径。该设置利于使轴封流体通道与径向轴承与主轴21之间的间隙连通，及利于流体在各轴封流体通道之间均匀分配。
如图1、图4和图5所示，本公开实施例的压缩机中，轴封部件70的轴封结构与主轴21配合。轴封流体通道与径向轴承和主轴21之间的间隙连通。该设置利于防止流体在径向轴承附近滞留，利于保持径向轴承的背压稳定，从而利于保证压缩机稳定运行。
如图1、图4和图5所示，在一些实施例中，轴封定位止口72远离轴封盘体71的一端具有用于对径向轴承进行轴向定位的轴承定位端面721，轴承定位端面721与径向轴承的相应端面间隙配合。该设置使轴封部件70同时承担了径向轴承的轴向定位功能，利于缩短压缩机转子的长度，减小压缩机转子及整机重量，简化压缩机结构。
如图1至图4所示，在一些实施例中，轴承承载部件60的安装孔67为台阶孔，包括位于靠近扩压结构的一端的大径段和远离扩压结构的一端的小径段。轴封盘体71安装于大径段内与大径段配合，轴封定位止口72安装于小径段内，其外周面723与小径段配合。大径段与小径段之间形成台阶定位面65，轴封盘体71的靠近轴封定位止口72的端面714与台阶定位面65间隙配合。该设置利于轴承部件70的轴向定位。同时，因轴封部件70承担径向轴承的轴向定位功能，也利于径向轴承的轴向定位。
如图1至图3所示，轴承承载部件60包括设置于扩压器的靠近轴承座部的一端的承载部件定位止口68和设置于扩压器部上的扩压器部定位孔691和扩压器部安装孔692。承载部件定位止口68与压缩机的壳体10的电机筒体11的右端内壁配合，以确定轴承承载部件60的径向位置和轴向位置。轴承承载部件60通过穿设于扩压器部定位孔691的定位件与壳体10之间进行周向定位，通过穿过扩压器部安装孔692的螺纹连接件与壳体10固定连接。
本公开实施例还提供一种冷媒循环系统，包括本公开实施例的压缩机。
本公开实施例的压缩机和冷媒循环系统具有本公开实施例的轴承承载部件60的相应优点。
以下进一步结合图1至图6对本公开一些实施例进行更详细说明。
如图1所示，压缩机主要包括壳体10、压缩机转子20、电机定子30、轴承组件、一级扩压器50、轴承承载部件60和轴封部件70。
壳体10包括电机筒体11和分别连接于电机筒体11左右两端的一级蜗壳12和二级蜗壳13。电机筒体11的左端具有端壁，右端敞口。
一级扩压器50和轴承承载部件60及安装于轴承承载部件60的安装孔67内的轴封部件70分别设置于电机筒体11的左右两端，并将壳体10的内部空间分隔为位于壳体10中部的电机容纳腔14、位于壳体10左端的一级压缩腔15和位于壳体10右端的二级压缩腔16。
压缩机转子20主要包括主轴21、一级叶轮22、二级叶轮23及推力盘部件24。
电机定子30固定于电机筒体11内壁，具有转子安装孔。电机筒体11内壁上可以设置螺旋槽，用于通入冷却电机定子30的冷却流体。
主轴21设置于电机定子30内，贯穿电机定子30的转子安装孔。主轴21中部设有用于产生磁场的永磁体，永磁体的左右两端分别设有第一端部轴段和第二端部轴段。因此，本实施例中，主轴21也是压缩机的电机的电机转子。电机定子30和主轴21构成压缩机的电机。电机定子30的绕组通电后带动主轴21转动，从而带动整个压缩机转子转动。
一级叶轮22和二级叶轮23分别固定连接于主轴21的左右两端。一级叶轮22和一级扩压器50的扩压结构位于一级压缩腔15内。二级叶轮23和轴承承载部件60上的扩压结构位于二级压缩腔16内。
推力盘部件24靠近一级叶轮22设置，包括推力盘和一体设置的安装套。推力盘部件24固定地套装于主轴21的第一端部轴段外周。安装套位于一级叶轮22和推力盘之间。推力盘部件24可以通过热套的方式套装于主轴21的第一端部轴段上。
轴承组件包括推力轴承组件41、第一径向轴承42和第二径向轴承43。
如图1所示，推力轴承组件41包括第一推力轴承411、第二推力轴承412和推力轴承定位环413。在图1至图6所示的实施例中，第一推力轴承411、第二推力轴承412、第一径向轴承42和第二径向轴承均43为静压气体轴承。
一级扩压器50的左端具有扩压结构，如扩压面或扩压叶片。一级扩压器50的中心设有轴孔，轴孔内设有轴封结构，如梳齿结构。推力盘部件24的安装套位于一级扩压器50的轴孔内，并与轴孔内设置的轴封结构配合。一级扩压器50的径向外端密封地固定于电机筒体11的端壁上，从而一级扩压器50隔离壳体10左端的一级压缩 腔15与壳体10中部的电机容纳腔14。
如图1所示，一级扩压器50的右端具有扩压器定位止口，电机筒体11的端壁左端具有扩压器安装口，一级扩压器50的扩压器定位止口安装于扩压器安装口中并与扩压器安装口配合，从而实现一级扩压器50的轴向和径向定位。一级扩压器50的扩压器定位止口内部与电机筒体11的扩压器安装口的底壁围成了推力轴承组件安装室。
推力轴承组件41设置于推力轴承组件安装室内。推力盘部件24的推力盘的左右两端面分别与第一推力轴承411的第一推力面和第二推力轴承412的第二推力面配合，从而推力盘与第一推力轴承411和第二推力轴承412共同限定压缩机转子21的轴向位置。
第一推力轴承411的第一推力面的径向外端还设置有第一定位面，第二推力轴承412的第二推力面的径向外端还设置有第二定位面，推力轴承定位环413的左右两端面分别与第一定位面和第二定位面间隙配合，从而，推力轴承定位环413的左右两端面之间的距离可以限定第一推力面与第二推力面之间的距离，可以限定推力盘与第一推力面的间隙以及推力盘与第二推力面之间的间隙之和。推力轴承定位环413通过螺纹连接件固定连接于第二推力轴承42及电机筒体11的端壁上。
推力轴承定位环413上设有用于连通其径向内侧和径向外侧的定位环流体通道。定位环流体通道利于保证推力轴承组件的背压稳定，从而利于压缩机的稳定工作。
电机筒体10的端壁的径向中部设置有端壁轴承室，第一径向轴承42设置于端壁轴承室中。第一径向轴承42的左端与第二推力轴承412的远离第二推力面的一侧间隙配合，第一径向轴承42的右端与安装在端壁轴承室的卡槽内的卡环82间隙配合，从而第一径向轴承42的轴向位置被第二推力轴承412和卡环82共同确定。
轴承承载部件60集成了扩压器(图1所示的实施例中，为二级扩压器)与轴承座，第二径向轴承43安装于轴承承载部件60的轴承室62内。第二径向轴承43套装于主轴21的第二端部轴段外周。
轴封部件70固定安装于轴承承载部件60的安装孔67内。如前所述，轴承承载部件60固定安装于电机筒体11的右端。且轴承承载部件60与电机筒体11之间为密封连接。轴封部件70安装于轴承承载部件60并套装于主轴21外之后，轴承部件70的轴孔内的轴封结构与主轴21的第二端部轴段之间形成密封，轴承部件70径向外端与轴承承载部件60的径向内端密封连接，从而轴封部件70与轴承承载部件60隔离壳体10的第二压缩腔16与电机容纳腔14。
轴承承载部件60、轴封部件70与第二径向轴承43组装好后，轴封部件70的轴承定位端面721与第二径向轴承43的右端面间隙配合，第二径向轴承43的左端与卡环81间隙配合，从而第二径向轴承43的轴向位置被轴封部件70与卡环81共同确定。同时，轴封部件70的各轴封流体通道与轴承承载部件60的各流体流出通道64对应连通。
如图1所示，电机筒体11上设置有用于向第一径向轴承42和第二径向轴承43供应悬浮气体的第一气体进入通道17。轴承承载部件60的流体进入通道63通过设置于其扩压器部端面上的流体入口与第一气体进入通道17连通，从而可以将悬浮气体通入轴承承载部件60的轴承室62内，并通过第二径向轴承43的多孔介质进入第二径向轴承43与主轴21的第二端部轴段之间的间隙，再进入轴封部件70的轴封定位止口72内腔，然后经各轴封流体通道进入各对应的轴承承载部件60的流体流出通道64，之后进入电机容纳腔14内，再从设置于电机筒体11上的出口(未图示)流出壳体10。
本实施例中，壳体10上还设置有为推力轴承组件41供应悬浮气体的第二气体进入通道，第二气体进入通道与第一气体进入通道独立。第二气体进入通道的悬浮气体分别供应至第一推力轴承411和第二推力轴承412内部，并经第一推力轴承411的多孔介质和第二推力轴承412的多孔介质进入第一推力面与推力盘之间的间隙及第二推力面与推力盘之间的间隙，再通过推力轴承定位环413上的定位环流体通道流至电机容纳腔14。推力轴承定位环413上的定位环流体通道利于及时排走悬浮气体，保证推力轴承组件41的背压稳定。
在一些未图示的实施例中，第二气体进入通道可以与第一气体进入通道连通，从而可以通过同一壳体进气口和相同的主流道为各分支流道及与分支流道对应的各气体轴承供应悬浮气体。
如图4所示，其中的箭头表示供应给第二径向轴承43的悬浮气体的流动路径。如图1至图4所示，悬浮气体从电机筒体11底部的第一气体进入通道17进入轴承承载部件60的流体进入通道63及轴承室62，再供给第二径向轴承43，悬浮气体进入第二径向轴承43内部，经过第二径向轴承43的多孔介质节流，进入第二径向轴承43与主轴21之间的间隙，悬浮气体在第二径向轴承43与主轴21之间的间隙内形成气膜，使主轴21浮起，然后从间隙两端排出。从左端排出的悬浮气体进入电机容纳腔14，之后与冷却电机的冷却气体一起从壳体10排出。从右端排出的悬浮气体通过轴 封部件70上的各轴封流体通道进入轴承承载部件60的各流体流出通道64，再进入电机容纳腔14，与用于冷却电机的冷却气体一起从壳体10排出。
静压气体轴承要求具有很高的精度，轴承间隙一般在10μm以下。轴封部件70的轴封结构的密封间隙也宜在确保相对转动的情部下越小越好，例如密封间隙可低至0.02mm，如此小的密封间隙对轴封结构与主轴21的同轴度要求很高，轴封部件70通过轴封定位止口72实现与压缩机相关部件，如轴承承载部件70及壳体10的定位，利于保证其轴封结构与主轴21的同轴度。
轴封结构设置为梳齿结构，与主轴21配合，可以阻止压缩机二级叶轮23的排气进入轴承承载部件60的轴承室62，利于减小压缩机泄露损失，提高压缩机的能效，同时也利于防止轴承室62的背压因泄露量太大而增大。
轴承室62的背压影响第二径向轴承43与主轴21之间的气膜压力分布情况，进而影响轴承刚度和阻尼，而轴承刚度和阻尼又影响转子动力学稳定性，另一方面，轴承背压波动也会造成轴承涡动，因此，静压气体轴承在使用中，保证背压稳定利于保证轴承转子系统稳定性。轴封部件70的轴封流体通道及轴承承载部件60的流体流出通道64防止了从左端排出的气体滞留在轴封部件70与轴承承载部件60内，因此有效防止第二径向轴承43的轴承背压不稳。
轴封部件70的轴承定位端面721与第二径向轴承43的右端面间隙配合，与卡环81一起限制第二径向轴承43的轴向位置，可以防止第二径向轴承43左右窜动造成轴承失稳。
可见，本公开实施例的轴封部件70，在利于减小泄露损失的同时，利于保证与轴封部件70相邻的径向轴承的工作背压稳定，从而利于提高压缩机的能效和轴承转子系统稳定性。
本公开实施例的轴承承载部件60将扩压器和轴承座设计成一个零件，同时设置轴封安装孔，集成了扩压器、轴承座和轴封安装座的功能，利于减少零件数量，提高装配效率，同时也利于减小压缩机转子长度，提高轴承转子系统的稳定性。
由于轴承承载部件60具有流体进入通道63和流体流出通道64，利于保证第二径向轴承43正常工作及工作背压稳定，利于提高轴承转子系统稳定性，同时兼具扩压器部作用，减少了零件数量，减小压缩机转子的长度，提高轴承转子系统稳定性。
轴承承载部件60采用承载部件定位止口68与扩压器部定位孔691配合定位销钉一起进行双重定位，用承载部件定位止口68与电机筒体11的右端面及内壁面可以保 证轴承承载部件60及其轴承室62与主轴21的同轴度，进而保证第二径向轴承43装配后与主轴21的同轴度，通过销钉与扩压器部定位孔691配合，可以对轴承承载部件60的周向精确定位。因此，该轴承承载部件60能提高装配效率和精度。
由于静压气体轴承的轴承间隙一般为几微米至数十微米，静压气体轴承支承的旋转机械对两个径向轴承的同轴承要求极高，如果同轴度差，会使轴承性能降低，严重时会导致转子无法浮起。因此本公开实施例的轴承承载部件60及与其配合的轴承部件70均适用于采用静压气体轴承承载的压缩机。当然，虽然本公开实施例的轴承承载部件60和轴封部件70适用于采用气体轴承的压缩机，例如离心压缩机，但并不排除在其它转动系统中采用本公开实施例的轴承承载部件60和轴封部件70。
最后应当说明的是：以上实施例仅用以说明本公开的技术方案而非对其限制；尽管参照较佳实施例对本公开进行了详细的说明，所属领域的普通技术人员应当理解：依然可以对本公开的具体实施方式进行修改或者对部分技术特征进行等同替换，其均应涵盖在本公开请求保护的技术方案范围当中。

Claims (16)

  1. 一种轴承承载部件(60)，包括：
    轴承室(62)，用于安装径向轴承；
    安装孔(67)，与所述轴承室(62)同轴且连通；
    流体进入通道(63)，连通所述轴承室(62)与所述轴承承载部件(60)外部；和
    流体流出通道(64)，连通所述安装孔(67)与所述轴承承载部件(60)外部。
  2. 根据权利要求1所述的轴承承载部件(60)，其中所述轴承承载部件(60)包括：
    轴承座部，所述轴承室(62)设置于所述轴承座部；和
    扩压器部，所述扩压器部与所述轴承座部一体地沿所述轴承室(62)的轴向并排设置，所述扩压器部远离所述轴承座部的一端设置有扩压结构，所述安装孔(67)设置于所述扩压器部。
  3. 根据权利要求2所述的轴承承载部件(60)，其中所述流体进入通道(63)的流体入口设置于所述扩压器部的靠近所述轴承座部的一端的端面上。
  4. 根据权利要求1所述的轴承承载部件(60)，其中所述轴承承载部件(60)包括多个所述流体流出通道(64)，所述多个流体流出通道(64)沿所述轴承承载部件(60)的周向均布。
  5. 根据权利要求4所述的轴承承载部件(60)，其中所述多个流体流出通道(64)沿所述轴承承载部件(60)的周向间隔360°/(m+1)均布，其中，m为所述多个流体流出通道(64)的数量。
  6. 根据权利要求1所述的轴承承载部件(60)，其中所述轴承承载部件(60)包括设置于所述远离所述安装孔(67)的一端的用于对所述径向轴承进行轴向定位的轴承定位结构。
  7. 根据权利要求6所述的轴承承载部件(60)，其中所述轴承定位结构包括环槽(66)，所述环槽(66)用于安装对所述径向轴承(43)进行轴向定位的卡环(81)，所述环槽(66)设置于所述轴承室(62)的侧壁上。
  8. 根据权利要求2至7中任一项所述的轴承承载部件(60)，其中所述轴承承载部件(60)还包括设置于所述扩压器部上的扩压器部安装孔(692)和扩压器部定位孔(691)至少之一。
  9. 根据权利要求2至7中任一项所述的轴承承载部件(60)，其中所述轴承承载部件(60)还包括设置于所述扩压器部的靠近所述轴承座部的一端的承载部件定位止口(68)。
  10. 根据权利要求1至7中任一项所述的轴承承载部件(60)，其中所述安装孔(67)为台阶孔，包括远离所述轴承室(62)一端的大径段和靠近所述轴承室(62)一端的小径段，所述大径段与所述小径段之间形成台阶定位面(65)。
  11. 一种压缩机，包括：
    压缩机转子(20)，包括主轴(21)；
    径向轴承，用于承载所述主轴(21)；和
    轴承承载部件(60)，为权利要求1至10中任一项所述的轴承承载部件(60)，所述径向轴承安装于所述轴承承载部件(60)的所述轴承室(62)内。
  12. 根据权利要求11所述的压缩机，其中所述径向轴承为气体轴承。
  13. 根据权利要求11所述的压缩机，其中所述压缩机还包括轴封部件(70)，所述轴封部件(70)安装于所述轴承承载部件(60)的安装孔(67)内，所述轴封部件(70)的靠近所述径向轴承的一端具有轴承定位端面(721)，所述轴承定位端面(721)与所述径向轴承的端面配合。
  14. 根据权利要求13所述的压缩机，其中所述轴封部件(70)包括连通所述流体流出通道(64)与所述径向轴承与所述主轴(21)之间的间隙的轴封流体通道。
  15. 根据权利要求14所述的压缩机，其中所述压缩机包括壳体(10)，所述轴承承载部件(60)包括轴承座部和与所述轴承座部一体地沿所述轴承室(62)的轴向并排设置的扩压器部，所述轴承承载部件(60)还包括设置于所述扩压器部的靠近所述轴承座部的一端的承载部件定位止口(68)，所述承载部件定位止口(68)与所述壳体(10)配合。
  16. 一种冷媒循环系统，包括权利要求11至15中任一项所述的压缩机。
PCT/CN2019/113992 2018-12-25 2019-10-29 轴承承载部件、压缩机和冷媒循环系统 WO2020134518A1 (zh)

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