WO2020134516A1 - 轴封部件、压缩机和冷媒循环系统 - Google Patents

轴封部件、压缩机和冷媒循环系统 Download PDF

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Publication number
WO2020134516A1
WO2020134516A1 PCT/CN2019/113988 CN2019113988W WO2020134516A1 WO 2020134516 A1 WO2020134516 A1 WO 2020134516A1 CN 2019113988 W CN2019113988 W CN 2019113988W WO 2020134516 A1 WO2020134516 A1 WO 2020134516A1
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WO
WIPO (PCT)
Prior art keywords
shaft seal
bearing
shaft
fluid
positioning
Prior art date
Application number
PCT/CN2019/113988
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
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Publication of WO2020134516A1 publication Critical patent/WO2020134516A1/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
    • F04D29/08—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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers 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
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/40—Sealings between relatively-moving surfaces by means of fluid
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/54—Other sealings for rotating shafts

Definitions

  • the present disclosure relates to a compressor and a refrigerant circulation system, and particularly to a shaft seal 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.
  • Hydrostatic gas bearings require an external air source to supply gas.
  • the back pressure of the bearing is required to be stable to prevent the gas film from being damaged by the back pressure fluctuations of the bearing and the instability of the bearing rotor system.
  • a first aspect of the present disclosure provides a shaft seal component, including:
  • a shaft seal disc body the shaft seal disc body has a shaft hole in the center, and a shaft seal structure is provided on the hole wall of the shaft hole;
  • a shaft seal positioning stop is coaxially and integrally provided at an axial end of the shaft seal disc body, and a radial inner side and a radial outer side connecting the shaft seal positioning stop are provided on the shaft seal positioning stop The first fluid channel.
  • the shaft seal structure includes a comb-tooth structure.
  • the end of the shaft seal positioning stop away from the shaft seal disc body has a bearing positioning end surface for axial positioning of the radial bearing.
  • the first fluid channel includes:
  • At least one through hole provided on the side wall of the positioning stop of the shaft seal;
  • the shaft seal component includes a plurality of the first fluid channels.
  • the plurality of first fluid channels are evenly arranged along the circumferential direction of the shaft seal positioning stop.
  • the plurality of first fluid channels are evenly arranged at an angular interval of 360°/(n+1) along the circumferential direction of the shaft seal positioning stop, where n is the plurality of first fluid channels The number of fluid channels.
  • the shaft seal component includes at least one of a shaft seal connection hole and a shaft seal positioning hole provided on the shaft seal disc body.
  • the diameter of the inner circumferential surface of the shaft seal positioning stop is larger than the diameter of the shaft hole.
  • a second aspect of the present disclosure provides a compressor, including:
  • Compressor rotor including main shaft
  • the shaft seal member is the shaft seal member according to the first aspect of the present disclosure
  • the main shaft passes through the shaft hole of the shaft seal member, the shaft seal structure of the shaft seal member and the main shaft
  • the first fluid passage of the shaft seal member communicates with the gap between the radial bearing and the main shaft.
  • the compressor further includes a bearing bearing member, and the bearing bearing member includes:
  • the diffuser has a shaft seal installation hole, an axial end of the diffuser is provided with a pressure expansion structure, and the shaft seal component is provided in the shaft seal installation hole;
  • a bearing housing is integrally provided at the other axial end of the diffuser, the bearing housing is provided with a bearing chamber coaxial with and communicating with the shaft seal mounting hole, and the radial bearing is provided in the bearing chamber.
  • the bearing carrier member includes a fluid inlet channel that communicates the bearing chamber with the outside of the bearing carrier member.
  • the bearing carrier component includes a fluid outflow channel that communicates the shaft seal mounting hole with the outside of the bearing carrier component, and the first fluid channel communicates with the fluid outflow channel.
  • an end of the shaft seal positioning stop away from the shaft seal disc body has a bearing positioning end surface for axial positioning of the radial bearing.
  • the shaft seal mounting hole is a stepped hole, including a large-diameter section near one end of the diffuser structure and a small-diameter section away from the end of the diffuser structure.
  • a stepped positioning surface is formed between the small-diameter sections, the shaft seal disc body is located in the large-diameter section, the shaft seal positioning stop is located in the small-diameter section, and the shaft seal disc body is close to the shaft seal The end surface of the positioning stop is in abutment or clearance fit with the stepped positioning surface.
  • the radial bearing is a gas bearing.
  • a third aspect of the present disclosure provides a refrigerant circulation system including the compressor described in the second aspect of the present disclosure.
  • the positioning seal of the shaft seal is beneficial to improve the precision of the fit between the shaft seal component and the sealed rotating shaft, which can more effectively prevent fluid leakage.
  • the fluid channel is helpful to prevent the components adjacent to the shaft seal components from trapping fluid, and to stabilize the back pressure of the related components, thereby improving the stability of the bearing rotor system.
  • the compressor and refrigerant circulation system provided by the present disclosure have the same advantages as the shaft seal component 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 perspective view of a shaft seal component of some embodiments of the present disclosure.
  • FIG. 3 is a schematic diagram of the side view of FIG. 2.
  • FIG. 4 is a schematic sectional view of FIG. 2.
  • FIG. 5 is a partial structural diagram of a compressor according to some embodiments of the present disclosure.
  • FIG. 6 is a schematic structural view of a bearing bearing component of a compressor of some embodiments of the present disclosure.
  • FIG. 7 is a schematic diagram of the left side view of the bearing bearing member shown in FIG. 6.
  • FIG. 8 is a schematic cross-sectional structural view of a shaft seal component according to other embodiments of the present disclosure.
  • an embodiment of the present disclosure provides a shaft seal member 70.
  • the shaft seal member 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 first communicating radially inward and radially outside of the shaft seal positioning stop 72 Fluid channel.
  • the shaft seal member 70 of the embodiment of the present disclosure has the functions of shaft seal, positioning, and fluid discharge.
  • the shaft seal positioning stop 72 facilitates the improvement of the cooperation accuracy between the shaft seal member 70 and the sealed rotating shaft (such as the main shaft 21 of the compressor).
  • the fluid leakage can be prevented more effectively.
  • the first fluid channel helps to prevent the components (such as radial bearings) that cooperate with the shaft seal component 70 from trapping fluid, helps stabilize the back pressure of related components, and thus improves the stability of the bearing rotor system.
  • the shaft seal structure 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 structure of the first fluid channel may be various, for example, as shown in FIGS. 1 to 5, in some embodiments, the first fluid channel includes a portion away from the shaft seal disc 71 toward the shaft seal disc 71 The end of the end is recessed into a groove 722.
  • FIG. 8 shows the structure of a shaft seal component of other embodiments of the present disclosure.
  • the first fluid channel may include at least one through hole 724 provided on the side wall of the shaft seal positioning stop 72. In the embodiment (not shown), the groove and the through hole may also be provided as the first fluid channel at the same time.
  • the shaft seal member 70 includes a plurality of first fluid channels.
  • the provision of a plurality of first fluid channels facilitates rapid and uniform discharge of fluids near related components, such as radial bearings, and helps prevent fluid from stagnation near related components.
  • the plurality of first fluid channels are uniformly 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 first 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 first fluid channels.
  • the number and distribution manner of the first fluid channels are favorable to correspond to the number and distribution manner of the fluid outflow channels 64 provided on the bearing carrying member 60. This arrangement is beneficial to cooperate with related components such as the bearing bearing component 60 to be described later to form a fluid discharge path, and it is advantageous to reserve a location for the arrangement of the fluid intake channel of the related components.
  • the shaft seal member 70 includes at least one of a shaft seal connecting hole 712 and a shaft seal positioning hole 713 provided on the shaft seal disc body 71.
  • the shaft seal positioning hole 713 can accurately determine the connection position between the shaft seal part 70 and related parts such as the bearing bearing part 60 described later, which is beneficial to quickly and accurately realize the first fluid passage and the corresponding fluid passage (such as the bearing bearing part 60
  • the fluid outflow channel 64) is in communication.
  • 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 disc body 71. This arrangement facilitates communication between the first fluid channel and the gap between the radial bearing and the main shaft 21, and facilitates uniform distribution of fluid between the first fluid channels.
  • An embodiment of the present disclosure also provides a compressor, including a compressor rotor 20, a radial bearing, and a shaft seal member 70.
  • the compressor rotor 20 includes a main shaft 21. Radial bearings are used to carry the main shaft 21.
  • the shaft seal member 70 is the aforementioned shaft seal member 70.
  • the main shaft 21 is inserted into the shaft hole of the shaft sealing member 70.
  • the shaft seal structure of the shaft seal member 70 cooperates with the main shaft 21.
  • the first fluid passage 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 compressor further includes a bearing bearing member 60, and the bearing bearing member 60 includes a diffuser and a bearing housing.
  • the diffuser has a shaft seal mounting hole 67, and an axial end of the diffuser (the right end in FIGS. 1, 5, and 6) is provided with a diffuser structure.
  • the diffuser structure may be, for example, a diffuser surface or a diffuser blade.
  • the shaft seal member 70 is provided in the shaft seal mounting hole 67.
  • the bearing seat is integrally arranged at the other axial end of the diffuser.
  • the bearing housing is provided with a bearing chamber 62 coaxial with and communicating with the shaft seal mounting hole 67.
  • the radial bearing is provided in the bearing chamber 62.
  • the bearing bearing member 60 simultaneously assumes the functions of installing the diffuser, the bearing seat and the shaft seal member.
  • the shaft seal member 70 cooperates with the radial bearing to be installed in the bearing bearing member 60, which 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 bearing carrying member 60 includes a fluid inlet passage 63 that communicates the bearing chamber 62 with the outside of the bearing carrying member 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 bearing carrier 60 includes a fluid outflow channel 64 that communicates with the shaft seal mounting hole 67 and the outside of the bearing carrier 60, and the first fluid channel is The fluid outflow channel 64 communicates. 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 first fluid passage 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 fluid outflow channel 64 is a hole provided inside the bearing carrying member 60.
  • 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.
  • This arrangement enables the shaft seal member 70 to simultaneously assume the axial positioning function of the radial bearing, which is beneficial to shorten the length of the compressor rotor, reduce the weight of the compressor rotor and the entire machine, and simplify the compressor structure.
  • the bearing positioning end face 721 and the corresponding end face of the radial bearing may be in clearance fit, for example.
  • the shaft seal mounting hole 67 is a stepped hole, including a large-diameter section located near one end of the diffuser structure and a small-diameter section away from the end of the diffuser structure.
  • the shaft seal disc body 71 is installed in the large diameter section to cooperate with the large diameter section
  • the shaft seal positioning stop 72 is installed in the small diameter section
  • the outer circumferential surface 723 of the shaft seal positioning stop 72 cooperates 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 disk 71 near the shaft seal positioning stop 72 abuts or gap fits with the step positioning surface 65.
  • This arrangement facilitates the axial positioning of the bearing member 70.
  • the shaft seal component assumes the axial positioning function of the radial bearing, it is also conducive to the axial positioning of the radial bearing.
  • the fluid inlet of the fluid inlet channel 63 is provided on the end surface of the other end of the diffuser in the axial direction. This arrangement facilitates the introduction of fluid into the passage 63 from the compressor housing.
  • the bearing carrier 60 includes a plurality of fluid outflow channels 64.
  • the plurality of fluid outflow channels 64 are evenly distributed along the circumferential direction of the bearing carrying member 60.
  • the plurality of fluid outflow channels 64 are evenly spaced along the circumferential direction of the bearing bearing member 60 by 360°/(m+1), where m is the number of the plurality of fluid outflow channels 64.
  • the number and distribution of the first fluid channels correspond to the number and distribution of the fluid outflow channels 64 provided on the bearing carrier 60.
  • 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 fluid outlet of the fluid outflow channel 64 is provided on the end surface of the second axial end of the diffuser and/or the outer peripheral surface of the bearing housing.
  • the bearing bearing member 60 includes a bearing positioning structure provided at the other end in the axial direction for axially positioning the radial bearing.
  • the bearing positioning structure includes a ring groove 66.
  • the ring groove 66 is provided on the side wall of the bearing chamber 62.
  • the snap ring 81 is installed in the ring groove 66.
  • the inner diameter of the snap ring 81 is smaller than the diameter of the bearing chamber 62.
  • the bearing bearing member 60 further includes a bearing member positioning stop 68 provided on the other axial end of the diffuser, and a diffuser positioning hole 691 and a diffuser provided on the diffuser 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 penetrated through the diffuser positioning hole 691 and the housing 10, and is fixedly connected to the housing 10 through a threaded connector passing through the diffuser mounting hole 692.
  • Embodiments of the present disclosure also provide a refrigerant circulation system, including the aforementioned compressor.
  • the compressor and refrigerant circulation system of the embodiments of the present disclosure have the corresponding advantages of the shaft seal member 70 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 member 70 installed in the shaft seal mounting hole 67 of the bearing bearing member 60 are respectively provided at the left and right ends of the motor barrel 11, and the inner space of the housing 10 It is divided into a motor accommodating chamber 14 in the middle of the housing 10, a primary compression chamber 15 at the left end of the housing 10 and a 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 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 primary diffuser 50 is hermetically fixed to the end wall of the motor barrel 11 so that the primary diffuser 50 isolates the primary compression chamber 15 at the left end of the housing 10 from the motor housing in the middle of the housing 10 ⁇ 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 second fluid passage for communicating radially inside and outside.
  • the second fluid channel is beneficial to ensure the stability of the back pressure of the thrust bearing assembly, thereby facilitating the stable operation of the compressor.
  • An end wall bearing chamber is 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 shaft seal 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.
  • each first fluid channel of the shaft seal member 70 corresponds to each fluid outflow channel 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, 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 two radial bearings 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 A fluid passage enters the fluid outflow passage 64 of each corresponding bearing bearing member 60, then enters the motor accommodating chamber 14, and then flows out of the housing 10 from 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 cavity 14 through the second fluid channel on the thrust bearing positioning ring 413.
  • the second 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 arrow in FIG. 5 indicates the flow path of the suspended gas supplied to the second radial bearing 43.
  • the suspended gas enters the fluid inlet passage 63 and 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 .
  • the suspended gas enters the inside of the second radial bearing 43, passes through the porous medium throttle of the second radial bearing 43, and enters the gap between the second radial bearing 43 and the main shaft 21.
  • a gas film is formed in the gap between the main shafts 21 to make the main shaft 21 float, 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 first 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.
  • 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.
  • 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 is beneficial 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 first 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 sets 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 can also 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 a diffuser, reducing the The number of parts reduces the length of the compressor rotor and improves the stability of the bearing rotor system.
  • the bearing bearing member 60 adopts the bearing member positioning stop 68 and the diffuser 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 the coaxiality of the bearing chamber 62 and 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 positioning hole 69, can be To precise positioning. 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 a static pressure gas bearing.
  • the shaft seal member 70 of the embodiment of the present disclosure is suitable for a compressor using a gas bearing, such as a centrifugal compressor, it is not excluded to use the shaft seal member 70 of the presently disclosed embodiment in other rotating systems.

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Abstract

轴封部件、压缩机和冷媒循环系统。轴封部件（70）包括：轴封盘体（71），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第一流体通道。该轴封部件兼具轴封、定位和排出流体功能，轴封定位止口利于提高轴封部件与所密封的转轴之间的配合精度，第一流体通道利于防止与轴封部件相邻的部件滞留流体，利于稳定相关部件的背压。

Description

轴封部件、压缩机和冷媒循环系统
相关申请
本公开是以申请号为201811593754.7，申请日为2018年12月25日，发明名称为“轴封部件、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
本公开涉及压缩机和冷媒循环系统，特别涉及一种轴封部件、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。
静压气体轴承需要外部气源供气，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封部件，包括：
轴封盘体，所述轴封盘体中心具有轴孔，所述轴孔的孔壁上设有轴封结构；
轴封定位止口，同轴且一体地设置于所述轴封盘体的轴向一端，所述轴封定位止口上设有连通所述轴封定位止口的径向内侧和径向外侧的第一流体通道。
在一些实施例中，所述轴封结构包括梳齿结构。
在一些实施例中，所述轴封定位止口远离所述轴封盘体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。
在一些实施例中，所述第一流体通道包括：
设置于所述轴封定位止口的侧壁上的至少一个通孔；和/或
从所述轴封定位止口的远离所述轴封盘体的一端向靠近所述轴封盘体的一端凹入的凹槽。
在一些实施例中，所述轴封部件包括多个所述第一流体通道。
在一些实施例中，所述多个第一流体通道沿所述轴封定位止口的周向均匀设置。
在一些实施例中，所述多个第一流体通道沿所述轴封定位止口的周向以360°/(n+1)的角度间隔均匀设置，其中，n为所述多个第一流体通道的数量。
在一些实施例中，所述轴封部件包括设置于所述轴封盘体上的轴封连接孔和轴封定位孔至少之一。
在一些实施例中，所述轴封定位止口的内周面的直径大于所述轴孔的直径。
本公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
轴封部件，为本公开第一方面所述的轴封部件，所述主轴穿设于所述轴封部件的所述轴孔内，所述轴封部件的所述轴封结构与所述主轴配合，所述轴封部件的所述第一流体通道与所述径向轴承和所述主轴之间的间隙连通。
在一些实施例中，所述压缩机还包括轴承承载部件，轴承承载部件包括：
扩压器，具有轴封安装孔，所述扩压器的轴向一端设置有扩压结构，所述轴封部件设置于所述轴封安装孔内；
轴承座，一体设置于所述扩压器的轴向另一端，所述轴承座设有与所述轴封安装孔同轴且连通的轴承室，所述径向轴承设置于所述轴承室内。
在一些实施例中，所述轴承承载部件包括流体进入通道，所述流体进入通道连通所述轴承室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流体流出通道，所述流体流出通道连通所述轴封安装孔与所述轴承承载部件外部，所述第一流体通道与所述流体流出通道连通。
在一些实施例中，所述轴封定位止口远离所述轴封盘体的一端具有用于对所述径向轴承进行轴向定位的轴承定位端面。
在一些实施例中，所述轴封安装孔为台阶孔，包括位于靠近所述扩压结构的一端的大径段和远离所述扩压结构的一端的小径段，所述大径段与所述小径段之间形成台阶定位面，所述轴封盘体位于所述大径段内，所述轴封定位止口位于所述小径段内，所述轴封盘体的靠近所述轴封定位止口的端面与所述台阶定位面抵接或间隙配合。
在一些实施例中，所述径向轴承为气体轴承。
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。
基于本公开提供的轴封部件兼具轴封、定位和排出流体功能，轴封定位止口利于提高轴封部件与所密封的转轴之间的配合精度，可更有效地防止流体泄漏，第一流体通道利于防止与轴封部件相邻的部件滞留流体，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。
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封部件相同的优点。
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封部件的立体结构示意图。
图3为图2的侧视结构示意图。
图4为图2的剖视结构示意图。
图5为本公开一些实施例的压缩机的局部结构示意图。
图6为本公开一些实施例的压缩机的轴承承载部件的结构示意图。
图7为图6所示的轴承承载部件的左视结构示意图。
图8为本公开另一些实施例的轴封部件的剖视结构示意图。
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5所示，本公开实施例提供一种轴封部件70。该轴封部件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第一流体通道。
本公开实施例的轴封部件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与所密封的转轴(如压缩机的主轴21)之间的配合精度，可以更有效地防止流体泄漏，第一流体通道利于防止与轴封部件70配合的部件(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至图5所示，在一些实施例中，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至图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。
第一流体通道的结构形式可以为多种，例如，如图1至图5所示，在一些实施例中，第一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。图8示出了本公开另一些实施例的轴封部件的结构。与图1至图5所示的实施例所示的轴承部件70相比，第一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724。在未图示的实施例中还可以同时设置凹槽和通孔作为第一流体通道。
如图3和图4、图8所示，在一些实施例中，轴封部件70包括多个第一流体通道。设置多个第一流体通道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3和图4、图8所示，在一些实施例中，多个第一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，多个第一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为多个第一流体通道的数量。n的数量可以为2、3、4、5、6或更多。如图3和图4、图8所示的实施例中，n＝5。第一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。该设置方式利于与相关部件如后述的轴承承载部件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。
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至少之一。轴封定位孔713可以准确确定轴封部件70与相关部件如后述的轴承承载部件60之间的连接位置，利于快速、准确实现第一流体通道与相应的流体通道(如轴承承载部件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至图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。该设置利于使第一流体通道与径向轴承与主轴21之间的间隙连通，及利于流体在各第一流体通道之间均匀分配。
本公开实施例还提供一种压缩机，包括压缩机转子20，径向轴承和轴封部件70。压缩机转子20包括主轴21。径向轴承用于承载主轴21。轴封部件70为前述的轴封部件70。主轴21穿设于轴封部件70的轴孔内。轴封部件70的轴封结构与主轴21配合。第一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和图5、图6所示，在一些实施例中，压缩机还包括轴承承载部件60，轴 承承载部件60包括扩压器和轴承座。扩压器具有轴封安装孔67，扩压器的轴向一端(图1、图5和图6的右端)设置有扩压结构。扩压结构例如可以为扩压面或扩压叶片。轴封部件70设置于轴封安装孔67内。轴承座一体设置于扩压器的轴向另一端。轴承座设有与轴封安装孔67同轴且连通的轴承室62。径向轴承设置于轴承室62内。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，轴封部件70配合将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。
如图1和图5、图6所示，在一些实施例中，轴承承载部件60包括流体进入通道63，流体进入通道63连通轴承室62与轴承承载部件60外部。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。
如图1和图5、图6所示，在一些实施例中，轴承承载部件60包括流体流出通道64，流体流出通道64连通轴封安装孔67与轴承承载部件60外部，第一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至图5所示，轴封部件70的第一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。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。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。轴承定位端面721与径向轴承的相应端面例如可以间隙配合。
如图1和图5、图6所示，在一些实施例中，轴封安装孔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，轴封定位止口72的外周面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抵接或间隙配合。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6所示，流体进入通道63的流体入口设置于扩压器的轴向另一端的端面上。该设置利于流体从压缩机壳体内导入流体进入通道63。
轴承承载部件60包括多个流体流出通道64。多个流体流出通道64沿轴承承载部件60的周向均布。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。m的数量可以为2、3、4、5、6或更多。在图1至图6所示的实施例中，m＝5。第一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。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。
如图1、图5和图6所示，流体流出通道64的流体出口设置于扩压器的轴向第二端的端面上和/或轴承座的外周面上。
轴承承载部件60包括设置于轴向另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。环槽66设置于轴承室62的侧壁上。卡环81安装于环槽66内，卡环81的内周直径小于轴承室62的直径。
如图6和图7所示，轴承承载部件60还包括设置于扩压器的轴向另一端的承载部件定位止口68和设置于扩压器上的扩压器定位孔691和扩压器安装孔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，包括前述的压缩机。
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封部件70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的轴封安装孔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第二流体通道。第二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的轴封安装孔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的各第一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，然后经各第一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上的第二流体通道流至电机容纳腔14。推力轴承定位环413上的第二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。
图5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、图5和图6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上的各第一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况下越小越好，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的第一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，同时也能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，通过销钉与扩压器定位孔69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. 一种轴封部件(70)，包括：
    轴封盘体(71)，所述轴封盘体(71)中心具有轴孔，所述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所述轴封盘体(71)的轴向一端，所述轴封定位止口(72)上设有连通所述轴封定位止口(72)的径向内侧和径向外侧的第一流体通道。
  2. 根据权利要求1所述的轴封部件(70)，其中所述轴封结构包括梳齿结构(711)。
  3. 根据权利要求1所述的轴封部件(70)，其中所述轴封定位止口(72)远离所述轴封盘体(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)。
  4. 根据权利要求1所述的轴封部件(70)，其中所述第一流体通道包括：
    设置于所述轴封定位止口(72)的侧壁上的至少一个通孔(724)；和/或
    从所述轴封定位止口(72)的远离所述轴封盘体(71)的一端向靠近所述轴封盘体(71)的一端凹入的凹槽(722)。
  5. 根据权利要求1所述的轴封部件(70)，其中所述轴封部件(70)包括多个所述第一流体通道，所述多个第一流体通道沿所述轴封定位止口(72)的周向均匀设置。
  6. 根据权利要求5所述的轴封部件(70)，其中所述多个第一流体通道沿所述轴封定位止口(72)的周向以360°/(n+1)的角度间隔均匀设置，其中，n为所述多个第一流体通道的数量。
  7. 根据权利要求1所述的轴封部件(70)，其中所述轴封部件(70)包括设置于所述轴封盘体(71)上的轴封连接孔(712)和轴封定位孔(713)至少之一。
  8. 根据权利要求1所述的轴封部件(70)，其中所述轴封定位止口(72)的内周 面的直径大于所述轴孔的直径。
  9. 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
    轴封部件(70)，为根据权利要求1至8任一项所述的轴封部件(70)，所述主轴(21)穿设于所述轴封部件(70)的所述轴孔内，所述轴封部件(70)的所述轴封结构与所述主轴(21)配合，所述轴封部件(70)的所述第一流体通道与所述径向轴承和所述主轴(21)之间的间隙连通。
  10. 根据权利要求9所述的压缩机，其中所述压缩机还包括轴承承载部件(60)，轴承承载部件(60)包括：
    扩压器，具有轴封安装孔(67)，所述扩压器的轴向一端设置有扩压结构，所述轴封部件(70)设置于所述轴封安装孔(67)内；
    轴承座，一体设置于所述扩压器的轴向另一端，所述轴承座设有与所述轴封安装孔(67)同轴且连通的轴承室(62)，所述径向轴承设置于所述轴承室(62)内。
  11. 根据权利要求10所述的压缩机，其中所述轴承承载部件(60)包括流体进入通道(63)，所述流体进入通道(63)连通所述轴承室(62)与所述轴承承载部件(60)外部。
  12. 根据权利要求10所述的压缩机，其中所述轴承承载部件(60)包括流体流出通道(64)，所述流体流出通道(64)连通所述轴封安装孔(67)与所述轴承承载部件(60)外部，所述第一流体通道与所述流体流出通道(64)连通。
  13. 根据权利要求10所述的压缩机，其中所述轴封定位止口(72)远离所述轴封盘体(71)的一端具有用于对所述径向轴承进行轴向定位的轴承定位端面(721)。
  14. 根据权利要求10所述的压缩机，其中所述轴封安装孔(67)为台阶孔，包括位于靠近所述扩压结构的一端的大径段和远离所述扩压结构的一端的小径段，所述大 径段与所述小径段之间形成台阶定位面(65)，所述轴封盘体(71)位于所述大径段内，所述轴封定位止口(72)位于所述小径段内，所述轴封盘体(71)的靠近所述轴封定位止口(72)的端面(714)与所述台阶定位面(65)抵接或间隙配合。
  15. 根据权利要求10所述的压缩机，其中所述径向轴承为气体轴承。
  16. 一种冷媒循环系统，包括权利要求10至15中任一项所述的压缩机。
PCT/CN2019/113988 2018-12-25 2019-10-29 轴封部件、压缩机和冷媒循环系统 WO2020134516A1 (zh)

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GB2261921A (en) * 1991-11-26 1993-06-02 Mtu Muenchen Gmbh Edge seal
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