WO2020134433A1 - 离心压缩机及空调设备 - Google Patents

离心压缩机及空调设备 Download PDF

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Publication number
WO2020134433A1
WO2020134433A1 PCT/CN2019/113018 CN2019113018W WO2020134433A1 WO 2020134433 A1 WO2020134433 A1 WO 2020134433A1 CN 2019113018 W CN2019113018 W CN 2019113018W WO 2020134433 A1 WO2020134433 A1 WO 2020134433A1
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WO
WIPO (PCT)
Prior art keywords
bearing
diffuser
thrust
centrifugal compressor
radial
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/CN2019/113018
Other languages
English (en)
French (fr)
Inventor
刘华
张治平
李宏波
钟瑞兴
陈玉辉
叶文腾
亓静利
刘胜
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Electric Appliances Inc of Zhuhai
Original Assignee
Gree Electric Appliances Inc of Zhuhai
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
Publication date
Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Priority to US17/295,723 priority Critical patent/US11608833B2/en
Priority to MYPI2021002490A priority patent/MY209235A/en
Priority to EP19904130.2A priority patent/EP3904693B1/en
Publication of WO2020134433A1 publication Critical patent/WO2020134433A1/zh
Priority to PH12021551046A priority patent/PH12021551046A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/051—Axial thrust balancing
    • F04D29/0513—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/051—Axial thrust balancing
    • 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
    • F04D29/053—Shafts
    • 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
    • F04D29/083—Sealings 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
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/266—Rotors specially for elastic fluids mounting compressor rotors on shafts
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps

Definitions

  • the present disclosure relates to the technical field of air compression equipment, in particular to a centrifugal compressor and air conditioning equipment.
  • the dynamic pressure gas bearing has the advantages of high precision, low friction loss, long life, low vibration, no pollution, no need to provide lubricating media, etc. It is also suitable for high speed and high precision occasions, in centrifugal compressors, especially miniaturized centrifugal compressors Has broad application prospects. But the gap of the gas bearing is very small, only a few microns or even tens of microns, and the machining accuracy of parts is required to be sub-micron. Therefore, it is very important to ensure the thrust face clearance of the thrust bearing. If the clearance control is not accurate, the performance of the thrust bearing will be reduced, and in severe cases, the bearing will fail.
  • An aspect of an embodiment of the present disclosure provides a centrifugal compressor, including:
  • the diffuser the end of the diffuser away from the diffuser surface is provided with a first thrust bearing
  • a support assembly, the end of the support assembly facing the diffuser is provided with a second thrust bearing
  • the thrust disk is configured to be rotatable together with the main shaft, and is located between the diffuser and the support assembly in the axial direction.
  • the thrust disk has a thrust portion, and a gap between the thrust portion on both sides and the first thrust bearing and the second thrust bearing It is defined by the diffuser and the support assembly against each other.
  • the end of the diffuser away from the diffuser surface is provided with a first groove
  • the first thrust bearing is provided at the bottom of the first groove in the axial direction
  • the thrust portion is located in the first groove
  • the centrifugal compressor further includes a housing and a radial bearing, wherein the support assembly includes:
  • a fixed plate, a second thrust bearing is provided on the side of the fixed plate facing the diffuser;
  • the bearing support is provided on the side of the fixing plate away from the diffuser.
  • the first end of the bearing support is connected to the fixing plate, and the second end is connected to the housing for supporting the main shaft through the radial bearing.
  • the fixed plate and the bearing support form an integral structure.
  • the fixed plate is used to limit the displacement of the radial bearing in the axial direction toward the diffuser side.
  • the end of the fixing plate facing the bearing support is provided with a positioning ring
  • the bearing support is provided with an annular second groove
  • the positioning ring is embedded in the second groove
  • the inner wall of the positioning ring and the radial bearing The outer wall of part of the length is fitted.
  • the centrifugal compressor further includes a housing and a radial bearing, wherein the support assembly includes:
  • the bearing support is connected with the housing.
  • the second thrust bearing is provided on the bearing support toward the diffuser.
  • the bearing support is used to support the main shaft through the radial bearing.
  • the centrifugal compressor further includes a housing and a radial bearing
  • the support assembly includes a bearing support
  • the first end of the bearing support abuts the diffuser
  • the second end is connected to the housing for
  • the main shaft is supported by radial bearings, and the radial dimension of the bearing support gradually increases from the first end to the second end.
  • the centrifugal compressor further includes a radial bearing
  • the support assembly includes a bearing support for supporting the main shaft through the radial bearing.
  • the bearing support is provided with a vent hole for the radial bearing The space communicates with the space where the first thrust bearing and the second thrust bearing are located.
  • the first thrust bearing is directly fixed on the bottom of the first groove.
  • the centrifugal compressor further includes an impeller and a locking member
  • the main shaft is provided with a cavity and a shaft core is provided at the center, the end of the shaft core extends beyond the end of the main shaft; the impeller is sleeved on the shaft core And the impeller is locked on the shaft core through the locking part, and the impeller is located on the outside of the diffuser.
  • the thrust disc further includes a connecting portion, the connecting portion is connected to the thrust portion, and is sleeved on the main shaft, a through hole is provided at the bottom of the first groove, and the connecting portion is embedded in the through hole.
  • the centrifugal compressor further includes a sealing structure and an impeller provided at the end of the main shaft.
  • the impeller is located outside the diffuser.
  • the sealing structure adopts at least one of the following arrangement forms:
  • the side wall of the through hole is provided with a first axial comb tooth sealing structure
  • the end of the impeller facing the diffuser is provided with a radial comb tooth seal structure
  • the impeller has an embedded portion embedded in the diffuser, and a second axial comb tooth seal structure is provided on the embedded portion along the axial direction.
  • the seal structure also includes: a first axial comb tooth seal structure, a radial comb tooth seal structure and a second axial comb tooth seal structure are provided at the same time, and the radial comb tooth seal structure is located radially Between an axial comb tooth seal structure and a second axial comb tooth seal structure.
  • the centrifugal compressor further includes a radial bearing for supporting the main shaft, and at least one of the first thrust bearing, the second thrust bearing, and the radial bearing is an air suspension bearing.
  • Another aspect of the embodiments of the present disclosure provides an air-conditioning apparatus including the centrifugal compressor of the above embodiment.
  • FIG. 1 is a schematic structural view of some embodiments of the centrifugal compressor of the present disclosure
  • FIG. 2 is a schematic view of the installation structure of a diffuser, a thrust plate and a fixed plate in a centrifugal compressor of the present disclosure
  • FIG. 3 is a schematic view of the installation structure of the diffuser, thrust disk, fixed plate and bearing support in the centrifugal compressor of the present disclosure
  • FIG. 4 is a schematic diagram of the integrated structure of the fixed plate and the bearing support in the centrifugal compressor of the present disclosure
  • FIG. 5 is a schematic view of the installation structure of the bearing support and the housing in the centrifugal compressor of the present disclosure
  • FIG. 6 is a schematic structural view of some embodiments of a sealing structure in a centrifugal compressor of the present disclosure.
  • first and second appearing in this disclosure are just for convenience of description, to distinguish different component parts having the same name, and do not indicate a sequential or primary-secondary relationship.
  • the embodiments of the present disclosure provide a centrifugal compressor and air conditioning equipment, which can improve the assembly accuracy of the thrust bearing in the compressor.
  • a two-stage centrifugal compressor As shown in FIG. 1, taking a two-stage centrifugal compressor as an example, it includes a first volute 61, a second volute 63, and an intermediate casing 62.
  • the first casing is provided at both ends of the intermediate casing 62 in the axial direction 61 and the second volute 63 together form the compressor housing 6.
  • the main shaft 1 is set at the center position of the compressor casing 6, two ends of the main shaft 1 are respectively provided with an impeller 2, the inner end of the impeller 2 is provided with a diffuser 3, when the impeller 2 rotates at a high speed, the gas rotates with the centrifugal force The gas is thrown into the rear diffuser 3 for diffusion, which converts the velocity energy of the outlet of the impeller 2 into pressure energy, and the gas with increased pressure is discharged from the volute.
  • radial bearings 8 are provided at both ends of the main shaft 1 respectively.
  • the radial bearings 8 are supported by bearing supports 52 that are connected to the intermediate housing 62.
  • a stator assembly 7 is provided between the main shaft 1 and the intermediate housing 62. Since the impeller 2 generates an axial force during operation, a thrust bearing is provided at one end of the main shaft 1 to balance the axial force generated by the impeller 2.
  • the working principle of this type of compressor is as follows: the main shaft 1 rotates at a high speed during the operation of the compressor, the gas enters the diffuser 3 through the impeller 2 on the left, and the gas enters the first volute 61 after a first stage of compression.
  • the exhaust channel on the volute 61 guides compressed gas into the right impeller 2 and enters into the right diffuser 3 after centrifugal action of the right impeller 2.
  • the gas enters the second volute 63 after two-stage compression And discharge the compressor through the exhaust passage on the second volute 63.
  • the centrifugal compressor includes: a main shaft 1, an impeller 2, a diffuser 3, a thrust disk 4, and a support assembly 5.
  • a magnetic steel 13 is provided at an intermediate position of the main shaft 1 in the axial direction, a diffuser 3 is fixed on the housing 6, and an end of the diffuser 3 away from the diffuser surface is provided with a first thrust bearing 10, and the diffuser surface is Close to the end face of the impeller 2.
  • the support assembly 5 is provided at the end of the diffuser 3 away from the diffuser surface.
  • One end of the diffuser 3 is fixed to the casing 6 of the compressor, and the other end abuts against the end surface of the diffuser 3.
  • the support assembly 5 faces a side of the diffuser 3
  • a second thrust bearing 10' is provided on the side.
  • the thrust disk 4 is fixed to the main shaft 1 and is configured to rotate together with the main shaft 1.
  • the thrust disk 4 has a thrust portion 41, for example, a disk-like structure, and both sides of the thrust portion 41 are connected to the first thrust bearing 10 and the second thrust bearing
  • the gap between 10' is defined by the diffuser 3 and the support assembly 5 abutting each other.
  • the left and right sides of the thrust portion 41 and the thrust bearings on both sides form a working surface, which can withstand bidirectional axial forces, ensuring stable and reliable operation of the compressor under full operating conditions and reverse operation.
  • first thrust bearing 10 and the second thrust bearing 10' are static or dynamic pressure gas thrust bearings, or magnetic levitation bearings.
  • gas will form a gas film with pressure in this gap for thrust and lubrication. Since the thrust bearing itself is in the compressor cavity, the gas is full In the cavity environment, during the rotation of the rotor, the gas can be brought into the gap to form a dynamic pressure gas thrust bearing.
  • the thrust disk cooperates with the thrust bearings on both sides, and can withstand the axial force in the left and right directions, so as to ensure the stability of the compressor during full-operation and reverse operation.
  • the operating condition of the compressor refers to the evaporation temperature and condensation temperature of the system where the compressor is located.
  • the full operating condition refers to the compressor working within a certain evaporation temperature range and condensation temperature range.
  • both the diffuser 3 and the support assembly 5 need to be fixed on the compressor housing 6, their positions are fixed, and the support assembly 5 and the diffuser 3 abut against each other to limit the combination, thereby limiting the thrust plate 4
  • the position of the bearing and the clearance between the thrust bearings on both sides can accurately guarantee the clearance of the thrust bearing, reduce the difficulty of assembly, improve the assembly efficiency and assembly accuracy, and ensure the working performance of the thrust bearing, thereby improving the operational stability of the compressor.
  • the end of the diffuser 3 away from the diffuser surface is provided with a first groove 31, the bottom of the first groove 31 along the axial direction is provided with a first thrust bearing 10, and the thrust portion 41 is located in the first groove Within 31, there is a gap between both sides of the thrust portion 41 and the first thrust bearing 10 and the second thrust bearing 10'.
  • the axial depth of the first groove 31 can accurately ensure the clearance of the thrust bearings on both sides, which can improve assembly accuracy, reduce assembly difficulty, and increase assembly efficiency.
  • the performance of the thrust bearing can be guaranteed, and the performance of the thrust bearing can be reduced or even failed due to inaccurate clearance control, thereby improving the operation stability of the compressor.
  • the depth of the first groove 31 includes: the thickness of the thrust portion 41, the thickness of the thrust bearings on both sides and the clearance between the thrust bearings on both sides. Therefore, in order to ensure the clearance between the thrust bearings on both sides, by increasing the first recess
  • the depth of the groove 31, the thickness of the thrust portion 41, and the thickness of the thrust bearings on both sides control the clearance.
  • the specific method is to calculate the design depth and tolerance range of the first groove 31 according to the clearance range to be achieved by the thrust bearing, the thickness tolerance range of the thrust portion 41 and the thickness tolerance range of the thrust bearing.
  • the thrust bearing clearance can be ensured to improve the assembly accuracy and reduce the assembly difficulty, thereby improving the assembly efficiency.
  • the centrifugal compressor further includes a housing 6 and a radial bearing 8 for carrying the radial force of the rotor.
  • the radial force of the rotor mainly comes from the gravity of the rotor itself.
  • the radial bearing 8 is a static pressure or dynamic pressure gas radial bearing, or a magnetic suspension bearing.
  • the support assembly 5 includes a fixed plate 51 and a bearing support 52.
  • the fixed plate 51 abuts on the diffuser 3
  • the second thrust bearing 10' is provided on the side of the fixed plate 51 facing the diffuser 3
  • the bearing support 52 is provided on the fixed plate 51 away from the diffuser 3
  • the first end of the bearing support 52 is connected to the fixing plate 51, and the second end is connected to the housing 6 for supporting the spindle 1 through the radial bearing 8.
  • the support assembly 5 in this embodiment adopts a split structure, and the second thrust bearing 10' is installed through the fixing plate 51, and the radial bearing 8 is installed on the bearing support 52, which is beneficial to improve the radial bearings 8 at both ends of the main shaft 1 and the thrust bearing.
  • the installation position accuracy including the coaxiality of the two radial bearings 8 and the perpendicularity of the thrust bearings, can improve the working stability of the rotor system.
  • the second end of the bearing support 52 is provided with a flange 525, and the outer end of the flange 525 is provided with a stop 527.
  • the bearing support 52 is installed in the intermediate housing through the flange 525 Within 62, and fixed by fasteners, at the same time, the bearing support 52 relies on the stop 527 for radial positioning.
  • the two bearing supports 52 are first repositioned through the stop 527 to cooperate with the intermediate housing 62, and then the flange 525 and the intermediate housing 62 are fixed by fasteners, and then pinned. Subsequently, the intermediate housing 62 and the two bearing supports 52 are positioned as an integral component on the processing equipment, and the end surfaces of the two bearing supports 52 and the fixing plate 51 are processed to ensure the perpendicularity of the thrust bearing and the radial bearing 8 Then, the mounting holes 522 of the two bearing supports 52 are machined in order from one side to ensure the coaxiality of the two radial bearings 8.
  • the bearing support 52 is removed, and the radial bearing 8 is installed into the mounting hole 522 of the bearing support 52 by means of hot fitting, and then the fixing plate 51 is installed at the first end of the bearing support 52.
  • the bearing support 52 is fixedly mounted on the housing 6 by the pin position determined during processing.
  • each key positioning part is processed in one clamping process, the coaxiality of the two radial bearings 8 and the perpendicularity of the thrust bearing can be ensured, thereby improving the working stability of the rotor system.
  • the fixed plate 51 is also used to limit the displacement of the radial bearing 8 in the axial direction toward the diffuser 3 side, whereby the fixed plate 51 can be installed with the second thrust bearing 10'
  • the axial limit of the bearing 8 can make the structure of the bearing support assembly more compact, and it is beneficial to ensure the mounting surface of the second thrust bearing 10' and the axial limit surface of the radial bearing 8 through the processing parallelism on both sides of the fixing plate 51 Parallelism, thereby improving the installation accuracy of the thrust bearing and the radial bearing 8.
  • the end of the fixing plate 51 facing the bearing support 52 is provided with a positioning ring 511.
  • the bearing support 52 is provided with an annular second groove 521.
  • the positioning ring 511 is embedded in the second groove 521 to The fixed plate 51 is positioned radially, and there is a gap between the fixed plate 51 and the spindle 1.
  • the inner wall of the positioning ring 511 matches the outer wall of a partial length of the radial bearing 8 and is used to support the partial length of the radial bearing 8 and at the same time play an axial thrust role on the radial bearing 8.
  • the first thrust bearing 10 is fixed on the diffuser 3 through the fastener 32
  • the second thrust bearing 10 ′ is fixed on the fixing plate 51 through the fastener 32
  • the fixing plate 51 and the diffuser 3 abut against each other.
  • a positioning stop 33 is provided on the outer periphery of the diffuser 3 so as to be positioned and installed with the housing 6.
  • the fixing plate 51 and the bearing support 52 form an integrated structure.
  • the support assembly 5 adopts an integrated structure to simplify the structure and reduce assembly difficulty, and it is easy to ensure the perpendicularity of the radial bearing 8 and the thrust bearing through the processing accuracy of the support assembly 5.
  • the centrifugal compressor further includes a housing 6 and a radial bearing 8, wherein the support assembly 5 includes a bearing support 52, and the first end of the bearing support 52 abuts the diffuser 3 The second end is connected to the housing 6, the second thrust bearing 10' is provided on the bearing support 52 on the side facing the diffuser 3, the bearing support 52 is also used to support the main shaft 1 through the radial bearing 8 .
  • the bearing support 52 reserves a thrust table when processing the mounting hole 522 to axially limit the radial bearing 8.
  • the fixing plate 51 is omitted, the axial dimension of the bearing support assembly can be further reduced, the structure can be simplified, the assembly difficulty is reduced, and the machining accuracy of the support assembly 5 is easy to ensure the radial The perpendicularity of the bearing 8 and the thrust bearing.
  • the centrifugal compressor further includes a housing 6 and a radial bearing 8.
  • the support assembly 5 includes a bearing support 52.
  • the first end of the bearing support 52 abuts the diffuser 3.
  • the two ends are connected to the housing 6 for supporting the main shaft 1 through the radial bearing 8. Since the outer diameter of the thrust bearing is smaller than the inner diameter of the housing 6, accordingly, the outer dimension of the bearing support 52 in the longitudinal section from the first end to the second end gradually increases, that is, the bearing support 52 extends from the first end to the first The radial expansion at the two ends gradually increases. For weight reduction, as shown in FIG.
  • the bearing support 52 is provided with a weight reduction groove 524 on the side away from the thrust bearing, for example, the weight reduction groove 524 is provided in an annular shape.
  • the inner wall of the weight reduction groove 524 is parallel to the side wall of the mounting hole 522, and the outer wall It is consistent with the outer shape of the bearing support 52.
  • Such a V-shaped bearing support 52 can improve the overall structural strength of the bearing support 52 by adopting a structure with a gradual cross-sectional area, the force distribution is uniform everywhere, the load carrying capacity can be optimized, and the inclined outer surface is easy to achieve by casting. When casting with a mold, it has a draft angle.
  • the bearing support 52 is provided with a vent hole 526 for communicating the space where the radial bearing 8 is located with the space where the first thrust bearing 10 and the second thrust bearing 10 ′ are located, so that the radial bearing
  • the working environment of 8 is consistent with the first thrust bearing 10 and the second thrust bearing 10'.
  • the working back pressure of the radial bearing 8 is consistent with the first thrust bearing 10 and the second thrust bearing 10'.
  • the pressure and temperature of the overall motor cavity are stable.
  • the working environment of the thrust bearing and the radial bearing is the same as that of the motor cavity, that is, gas circulation is guaranteed, and the back pressure is relative. It is stable to prevent the bearing gas film from fluctuating due to large back pressure fluctuations, thereby improving bearing performance.
  • the bearing support 52 is provided with an operation hole 523 in the radial direction, so as to install a vibration sensor or a temperature sensor on the outer wall of the radial bearing 8 through the operation hole 523 to monitor the working state of the radial bearing 8.
  • the radially outer hole section of the operation hole 523 serves as a bypass hole to ensure that the pressure and temperature of the thrust bearing and the radial bearing 8 and the motor cavity are the same.
  • the radially inner hole section of the operation hole 523 serves to dissipate heat from the radial bearing 8 effect.
  • the first thrust bearing 10 is directly fixed on the bottom of the first groove 31 of the diffuser 3.
  • the first thrust bearing 10 uses a dynamic pressure thrust bearing, which is a sheet structure, and the dynamic pressure thrust bearing is directly fixed on the bottom of the first groove 31.
  • This structure integrates the diffuser 3 and the thrust bearing fixing plate into one part.
  • the bottom of the first groove 31 is used as the fixing plate of the first thrust bearing 10. No additional thrust bearing fixing plate is needed, which can further reduce the bearing support.
  • the axial dimensions of the components make the structure more compact.
  • the centrifugal compressor further includes an impeller 2 and a locking member 9.
  • a cavity 11 is provided in the main shaft 1 and a shaft core 12 is provided at the center.
  • the end of the shaft core 12 extends Out of the end of the main shaft 1; the impeller 2 is sleeved on the outer end of the shaft core 12, and the impeller 2 is locked on the shaft core 12 through the locking member 9, and the impeller 2 is located outside the diffuser 3.
  • the impeller 2 is detachably disposed relative to the main shaft 1, which can reduce the difficulty of disassembly and assembly of the impeller, and simplify the assembly process and required equipment of the impeller, improve assembly efficiency and operability of disassembly and inspection work and maintenance.
  • this installation method can not only prevent the main shaft 1 or the impeller 2 from deforming, but also ensure the installation strength of the impeller 2 to avoid stress concentration, thereby improving the compression capacity of the compressor.
  • the weight of the main shaft 1 can be reduced to increase the critical speed of the main shaft 1, which further improves the limit working capacity of the compressor.
  • the shaft core 12 is formed directly when processing the cavity 11, so that the shaft core 12 and the remaining part of the main shaft 1 are processed into an integrated body, and the shaft core 12 does not need to be additionally installed in the cavity of the main shaft 1, which can be further reduced
  • the difficulty of assembly increases the connection strength between the shaft core 12 and the main shaft 1, and also ensures the position accuracy of the shaft core 12, which effectively solves the problem of the runout of the front end of the rotor and reduces the length of the cantilever end, thereby improving the working stability and reliability of the compressor.
  • the cavity 11 is a ring groove, or a plurality of holes symmetrical with respect to the center of the axis.
  • the thrust plate 4 further includes a connecting portion 42, the thrust plate 4 is connected to the thrust portion 41, and is sleeved on the main shaft 1, a through hole 34 is provided at the bottom of the first groove 31, and the connecting portion 42 is embedded in the through Hole 34.
  • the connecting portion 42 is in interference fit with the main shaft 1 so that the thrust disk 4 can rotate with the main shaft 1.
  • the diffuser 3 and the fixed plate 51 are fixedly arranged and have a gap with the main shaft 1.
  • the thrust plate 4 has a cylindrical stepped structure.
  • the centrifugal compressor further includes a sealing structure and an impeller 2 provided at the end of the main shaft 1.
  • the impeller 2 is located outside the diffuser 3.
  • the side wall of the through hole 34 is provided with a first axial comb-tooth seal structure 35, which forms a shaft seal with the thrust disk 4, which can reduce the refrigerant passing through the diffuser 3 and the thrust disk 4 as the impeller exhausts Gap into the motor cavity.
  • the end of the impeller 2 facing the diffuser 3 is provided with a radial comb seal structure 21, which can reduce the flow of refrigerant to the periphery along the gap between the impeller 2 and the diffuser 3.
  • the impeller 2 has an embedded portion 22 embedded in the diffuser 3, for example, the embedded portion 22 is an elongated bar-shaped structure extending in the axial direction, and the embedded portion 22 is provided radially inward along the length of the embedded portion 22 There is a second axial comb-tooth seal structure 23 to reduce the flow of refrigerant to the periphery along the gap between the impeller 2 and the diffuser 3.
  • the comb-tooth seal structure includes a plurality of spaced-apart teeth, the teeth are trapezoidal, one of the side walls of the teeth is a vertical surface, and the other side wall is an inclined surface and is inclined from the high pressure side to the low pressure side.
  • This embodiment can reduce the amount of refrigerant leakage between the impeller 2 and the diffuser 3, and between the diffuser 3 and the thrust disk 4, which can not only ensure the clearance required for the operation of the main shaft 1 and the impeller 2, but also prevent the gap
  • the refrigerant leakage caused by too large effectively solve the compressor sealing problem, and help to improve the energy efficiency of the compressor.
  • this structure integrates the diffuser 3, the thrust bearing fixing plate and the shaft seal into one part, which can simplify the installation structure, make the structure more compact, and improve the assembly efficiency.
  • a positioning stop 33 is provided on the outer periphery of the diffuser 3, so as to be positioned and installed with the housing 6, and then matched with pins for precise positioning.
  • Shaft seals and thrust bearings that require high verticality share the positioning stop 33 and pins for positioning, unify the assembly benchmark, reduce assembly difficulty, and improve assembly accuracy, which can improve the verticality of the thrust bearing fixing surface to ensure the work of the thrust bearing
  • the performance can also improve the coaxiality of the first axial comb-tooth seal structure 35 to prevent the comb teeth from wearing and affecting the sealing performance.
  • the material of the diffuser 3 is lower than the hardness of the thrust disk 4.
  • the diffuser 3 uses aluminum, and the thrust disk uses 45 steel or 40Cr. In this way, if the first axial comb-tooth seal structure 35 on the diffuser 3 and the main shaft 1 are worn, the comb teeth are first worn to prevent the main shaft 1 from being worn.
  • the seal structure includes a first axial comb-teeth seal structure 35, a radial comb-teeth seal structure 21, and a second axial comb-teeth seal structure 23, and the radial comb-teeth seal structure 21 is located radially Between an axial comb seal structure 35 and a second axial comb seal structure 23.
  • This arrangement can make the airflow form a detour flow path, optimize the airflow deceleration and pressure reduction effect, and improve the sealing performance.
  • the end of the impeller 2 facing the diffuser 3 is provided with a boss 24, the boss 24 extends into the third groove 36 of the diffuser 3, and the radial comb tooth seal structure 21 is provided at the end of the boss 24 In order to achieve radial sealing, further extend the gas flow path, optimize the effect of deceleration and pressure reduction of air flow, and improve the sealing performance.
  • the present disclosure also provides an air conditioner including the centrifugal compressor of the above embodiment.
  • the centrifugal compressor of the present disclosure can withstand the axial force in two directions, ensure the stability of the compressor in full operating conditions and in reverse operation; and can accurately ensure the assembly clearance of the thrust bearing and the performance of the thrust bearing, thereby improving the compressor Operating stability. Both of these factors can improve the stability and reliability of the air conditioning equipment.

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Abstract

一种离心压缩机及空调设备，其中，离心压缩机包括：主轴(1)；扩压器(3)，扩压器(3)远离扩压面的一端设有第一推力轴承(10)；支承组件(5)，支承组件(5)朝向扩压器(3)的一端设有第二推力轴承(10')；以及推力盘(4)，被配置为与主轴(1)一起可转动，且沿轴向位于扩压器(3)与支承组件(5)之间，推力盘(4)具有推力部(41)，推力部(41)两侧与第一推力轴承(10)和第二推力轴承(10')之间的间隙通过扩压器(3)与支承组件(5)相互抵靠进行限定。离心压缩机能够保持推力轴承的间隙，保证推力轴承的性能，提高压缩机的运行稳定性。

Description

离心压缩机及空调设备
本公开是以申请号为 201811593330.0，申请日为 2018年12月25日的中国申请为基础，并主张其优先权，该中国申请的公开内容在此作为整体引入本公开中。
技术领域
本公开涉及空气压缩设备技术领域，尤其涉及一种离心压缩机及空调设备。
背景技术
动压气体轴承具有精度高、摩擦损耗小、寿命长、振动小、无污染，无需提供润滑介质等优点，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。但是气体轴承的间隙非常小，只有数微米乃至数十微米的程度，且要求零件的加工精度为亚微米级。因此保证推力轴承的推力面间隙是非常重要的，如果间隙控制不准确，则会降低推力轴承性能，严重时则会造成轴承失效。
发明内容
本公开的实施例一方面提供了一种离心压缩机，包括：
主轴；
扩压器，扩压器远离扩压面的一端设有第一推力轴承；
支承组件，支承组件朝向扩压器的一端设有第二推力轴承；以及
推力盘，被配置为与主轴一起可转动，且沿轴向位于扩压器与支承组件之间，推力盘具有推力部，推力部两侧与第一推力轴承和第二推力轴承之间的间隙通过扩压器与支承组件相互抵靠进行限定。
在一些实施例中，扩压器远离扩压面的一端设有第一凹槽，第一推力轴承设在第一凹槽沿轴向的底部，推力部位于第一凹槽内。
在一些实施例中，离心压缩机还包括壳体和径向轴承，其中，支承组件包括：
固定板，固定板上朝向扩压器的一侧设置第二推力轴承；和
轴承支座，设在固定板远离扩压器的一侧，轴承支座的第一端与固定板连接，第二端与壳体连接，用于通过径向轴承对主轴进行支撑。
在一些实施例中，固定板与轴承支座形成一体结构。
在一些实施例中，固定板用于限制径向轴承沿轴向朝向扩压器一侧的位移。
在一些实施例中，固定板朝向轴承支座的一端设有定位环，轴承支座上设有环形的第二凹槽，定位环嵌入第二凹槽中，且定位环的内壁与径向轴承部分长度段的外壁配合。
在一些实施例中，离心压缩机还包括壳体和径向轴承，其中，支承组件包括：
轴承支座，与壳体连接，第二推力轴承设在轴承支座上朝向扩压器的一侧，轴承支座用于通过径向轴承对主轴进行支撑。
在一些实施例中，离心压缩机还包括壳体和径向轴承，支承组件包括轴承支座，轴承支座的第一端抵靠在扩压器上，第二端与壳体连接，用于通过径向轴承对主轴进行支撑，轴承支座从第一端至第二端径向外廓尺寸逐渐增大。
在一些实施例中，离心压缩机还包括径向轴承，支承组件包括轴承支座，用于通过径向轴承对主轴进行支撑，轴承支座上设有通气孔，用于使径向轴承所在的空间与第一推力轴承和第二推力轴承所在的空间连通。
在一些实施例中，第一推力轴承直接固定在第一凹槽的底部。
在一些实施例中，离心压缩机还包括叶轮和锁紧部件，主轴内设有空腔并在中心处设有轴芯，轴芯的端部伸出主轴的端部；叶轮套设在轴芯的外端，并通过锁紧部件将叶轮锁紧在轴芯上，且叶轮位于扩压器的外侧。
在一些实施例中，推力盘还包括连接部，连接部与推力部连接，且套设在主轴上，第一凹槽的底部设有通孔，连接部嵌入通孔内。
在一些实施例中，离心压缩机还包括密封结构和设在主轴端部的叶轮，叶轮位于扩压器的外侧，密封结构采用如下设置形式中的至少一种：
通孔侧壁设有第一轴向梳齿密封结构；
叶轮朝向扩压器的端部设有径向梳齿密封结构；和
叶轮具有嵌入扩压器内的嵌入部，嵌入部上沿轴向设有第二轴向梳齿密封结构。
在一些实施例中，密封结构同时包括：第一轴向梳齿密封结构、径向梳齿密封结构和第二轴向梳齿密封结构同时设置，且径向梳齿密封结构沿径向位于第一轴向梳齿密封结构和第二轴向梳齿密封结构之间。
在一些实施例中，离心压缩机还包括用于对支撑主轴的径向轴承，第一推力轴承、第二推力轴承和径向轴承中的至少一个为气悬浮轴承。
本公开的实施例另一方面提供了一种空调设备，包括上述实施例的离心压缩机。
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为本公开离心压缩机的一些实施例的结构示意图；
图2为本公开离心压缩机中扩压器、推力盘和固定板的安装结构示意图；
图3为本公开离心压缩机中扩压器、推力盘、固定板和轴承支座的安装结构示意图；
图4为本公开离心压缩机中固定板和轴承支座采用一体化结构的示意图；
图5为本公开离心压缩机中轴承支座与壳体的安装结构示意图；
图6为本公开离心压缩机中密封结构的一些实施例的结构示意图。
附图标记说明
1、主轴；2、叶轮；3、扩压器；4、推力盘；5、支承组件；6、壳体；7、定子组件；8、径向轴承；9、锁紧部件；10、第一推力轴承；10’、第二推力轴承；
11、空腔；12、轴芯；13、磁钢；21、径向梳齿密封结构；22、嵌入部；23、第二轴向梳齿密封结构；24、凸台；31、第一凹槽；32、紧固件；33、定位止口；34、通孔；35、第一轴向梳齿密封结构；36、第三凹槽；41、推力部；42、连接部；51、固定板；511、定位环；512、内壁；52、轴承支座；521、第二凹槽；522、安装孔；523、操作孔；524、减重槽；525、法兰盘；526、通气孔；527、止口；61、第一蜗壳；62、中间壳体；63、第二蜗壳。
具体实施方式
以下详细说明本公开。在以下段落中，更为详细地限定了实施例的不同方面。如此限定的各方面可与任何其他的一个方面或多个方面组合，除非明确指出不可组合。尤其是，被认为是优选的或有利的任何特征可与其他一个或多个被认为是优选的或有利的特征组合。
本公开中出现的“第一”、“第二”等用语仅是为了方便描述，以区分具有相同名称的不同组成部件，并不表示先后或主次关系。
为了在以下实施例中清楚地描述各个方位，采用了“上”、“下”、“顶”、“底”、 “前”、“后”、“内”、“外”、“顶”和“底”等指示的方位或位置关系的描述，这仅是为了便于描述本公开，而不是指示或暗示所指的装置必须具有特定的方位、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。而且，如图1所示，后续提到的“轴向”、“周向”和“径向”均是以主轴1为基准定义的。
本公开的实施例提供了一种离心压缩机及空调设备，能够提高压缩机中推力轴承的装配精度。
为了使本领域技术人员更清楚地了解本公开的改进点，先结合图1对离心压缩机的整体结构进行说明。
如图1所示，以两级离心式压缩机为例，包括第一蜗壳61、第二蜗壳63和中间壳体62，中间壳体62沿轴向的两端分别设置第一蜗壳61和第二蜗壳63，共同形成压缩机壳体6。主轴1设在压缩机壳体6的中心位置，主轴1的两端分别设置一个叶轮2，叶轮2的内端设置扩压器3，叶轮2高速旋转时，气体随着旋转，在离心力作用下，气体被甩到后扩压器3中进行扩压，将叶轮2出口介质的速度能转化为压力能，压力提高后的气体从蜗壳排出。
为了对主轴1进行支撑，主轴1的两端分别设有径向轴承8，径向轴承8通过轴承支座52进行支撑，轴承支座52连接在中间壳体62上。主轴1与中间壳体62之间设有定子组件7。由于叶轮2在工作过程中会产生轴向力，因此在主轴1的一端设置推力轴承，以平衡叶轮2产生的轴向力。
此种压缩机的工作原理为：在压缩机工作过程中主轴1高速旋转，气体通过左侧的叶轮2进入扩压器3中，气体经过一级压缩后进入第一蜗壳61中，第一蜗壳61上的排气通道将压缩气体引导至进入右侧叶轮2中，经过右侧叶轮2的离心作用后进入右侧扩压器3中，气体经过二级压缩后进入第二蜗壳63中，并通过第二蜗壳63上的排气通道排出压缩机。
接下来将对离心压缩机中的轴承支承组件进行详细说明，在一些实施例中，如图2所示，离心压缩机包括：主轴1、叶轮2、扩压器3、推力盘4和支承组件5。
其中，主轴1的沿轴向的中间位置设有磁钢13，扩压器3固定在壳体6上，扩压器3远离扩压面的一端设有第一推力轴承10，扩压面为靠近叶轮2的端面。支承组件5设在扩压器3远离扩压面的一端，其一端与压缩机的壳体6固定，另一端抵靠在扩压器3的端面上，支承组件5朝向扩压器3的一侧设有第二推力轴承10’。推力盘4与主轴1固定，被配置为可与主轴1一起转动，推力盘4具有推力部41，例如采用盘 状结构，且推力部41的两侧与第一推力轴承10和第二推力轴承10’之间的间隙通过扩压器3与支承组件5相互抵靠进行限定。推力部41左右两面与两侧推力轴承形成工作面，可承受双向轴向力，保证压缩机全工况运行和反转时运行稳定可靠性。
例如，第一推力轴承10和第二推力轴承10’为静压或动压气体推力轴承，或者是磁悬浮轴承。
以图2为例，由于推力轴承与推力盘4之间有间隙，气体会在此间隙内形成具有压力的气膜起止推和润滑作用，由于推力轴承本身就在压缩机腔体内，气体就充满腔体环境，在转子旋转过程中，可将气体带入间隙中，形成动压气体推力轴承。
该实施例的离心压缩机中，推力盘与两侧的推力轴承配合，可承受左右两个方向的轴向力，以保证压缩机在全工况运行和反转运行时的稳定性。压缩机运行工况是指压缩机所在系统的蒸发温度和冷凝温度，全工况即指压缩机在一定蒸发温度范围和冷凝温度范围内工作，压缩机停机时，由于排气压力高于吸气压力，会出现停机后反转情况。
而且，由于扩压器3和支承组件5均需要固定在压缩机的壳体6上，因此自身位置固定，通过支承组件5与扩压器3相互抵靠进行组合限位，限定了推力盘4的位置以及与两侧推力轴承之间的间隙，由此可精确保证推力轴承间隙，降低装配难度，提高装配效率和装配精度，并保证推力轴承的工作性能，从而提高压缩机的运行稳定性。
如图2所示，扩压器3远离扩压面的一端设有第一凹槽31，第一凹槽31沿轴向的底部设有第一推力轴承10，推力部41位于第一凹槽31内，且推力部41的两侧与第一推力轴承10和第二推力轴承10’之间均具有间隙。
由于扩压器3与支承组件5相互抵靠，通过第一凹槽31的轴向深度可准确地保证两侧推力轴承的间隙，可提高装配精度，并降低装配难度，提高装配效率，同时还能保证推力轴承的性能，防止间隙控制不准确造成推力轴承性能降低甚至失效，从而提高压缩机的运行稳定性。
如图2所示，第一凹槽31的深度包括：推力部41厚度、两侧推力轴承的厚度和两侧推力轴承的间隙，因此，为了保证两侧推力轴承的间隙，通过提高第一凹槽31深度、推力部41厚度和两侧推力轴承的厚度来控制间隙。具体方法为：根据推力轴承需要达到的间隙范围、推力部41厚度公差范围和推力轴承厚度公差范围，来计算第一凹槽31的设计深度及公差范围。由此，通过提高第一凹槽31深度的加工精度能够保证推力轴承间隙，以提高装配精度，并降低装配难度，从而提高装配效率。
在一些实施例中，如图2和图3所示，离心压缩机还包括壳体6和径向轴承8，用于承载转子的径向力，转子的径向力主要来自转子本身的重力。例如，径向轴承8为静压或动压气体径向轴承，或者是磁悬浮轴承。
支承组件5包括固定板51和轴承支座52。其中，固定板51抵靠在扩压器3上，第二推力轴承10’设在固定板51上朝向扩压器3的一侧；轴承支座52设在固定板51远离扩压器3的一侧，轴承支座52的第一端与固定板51连接，第二端与壳体6连接，用于通过径向轴承8对主轴1进行支撑。
该实施例中的支承组件5采用分体式结构，通过固定板51安装第二推力轴承10’，轴承支座52安装径向轴承8，有利于提高主轴1两端的径向轴承8以及推力轴承的安装位置精度，包括两个径向轴承8的同轴度以及推力轴承的垂直度，可提高转子系统的工作稳定性。
如图5所示，轴承支座52的第二端设有法兰盘525，且在法兰盘525的外端设有止口527，轴承支座52通过法兰盘525安装在中间壳体62内，并通过紧固件固定，同时，轴承支座52依靠止口527进行径向定位。
在加工时，先将两个轴承支座52通过止口527进行第一重定位与中间壳体62配合，接着通过紧固件将法兰盘525与中间壳体62固定，再打销固定。随后，将中间壳体62和两个轴承支座52作为整体组件在加工设备上定位，加工两个轴承支座52与固定板51配合的端面，以保证推力轴承与径向轴承8的垂直度，再从一侧起依次加工两个轴承支座52的安装孔522，以保证两个径向轴承8的同轴度。
在加工完毕后，拆下轴承支座52，并通过热装的方式将径向轴承8装入轴承支座52的安装孔522，再将固定板51安装在轴承支座52的第一端。轴承支座52通过加工时确定的销钉位置固定安装在壳体6上。
由于各个关键的定位部分在一个装夹工序完成加工，因此可保证两个径向轴承8的同轴度以及推力轴承的垂直度，从而提高转子系统的工作稳定性。
如图3所示，固定板51还用于限制径向轴承8沿轴向朝向扩压器3一侧的位移，由此，固定板51既能安装第二推力轴承10’，又能对径向轴承8进行轴向限位，可使轴承支撑组件的结构更加紧凑，且利于通过固定板51两侧的加工平行度保证第二推力轴承10’安装面与径向轴承8轴向限位面的平行度，从而提高推力轴承与径向轴承8的安装精度。
在一些实施例中，固定板51朝向轴承支座52的一端设有定位环511，轴承支座 52上设有环形的第二凹槽521，定位环511嵌入第二凹槽521中，以对固定板51进行径向定位，固定板51与主轴1之间具有间隙。而且，定位环511的内壁与径向轴承8部分长度段的外壁匹配，用于对径向轴承8的部分长度段进行支撑，同时对径向轴承8起到轴向止推的作用。
在一些实施例中，如图2所示，第一推力轴承10通过紧固件32固定在扩压器3上，第二推力轴承10’通过紧固件32固定在固定板51上，固定板51与扩压器3相互抵靠，扩压器3的外周设有定位止口33，以便与壳体6定位安装。
在一些实施例中，如图4所示，固定板51与轴承支座52形成一体结构。支承组件5采用一体式结构可简化结构，降低装配难度，且易于通过支承组件5的加工精度保证径向轴承8与推力轴承的垂直度。
在一些实施例中，参考图4，离心压缩机还包括壳体6和径向轴承8，其中，支承组件5包括轴承支座52，轴承支座52的第一端抵靠在扩压器3上，第二端与壳体6连接，第二推力轴承10’设在轴承支座52上朝向扩压器3的一侧，轴承支座52还用于通过径向轴承8对主轴1进行支撑。轴承支座52在加工安装孔522时预留止推台，以对径向轴承8进行轴向限位。
与图4所示实施例相比，省去了固定板51，可进一步减小轴承支承组件的轴向尺寸，还能简化结构，降低装配难度，且易于通过支承组件5的加工精度保证径向轴承8与推力轴承的垂直度。
如图3和图4所示，离心压缩机还包括壳体6和径向轴承8，支承组件5包括轴承支座52，轴承支座52的第一端抵靠在扩压器3上，第二端与壳体6连接，用于通过径向轴承8对主轴1进行支撑。由于推力轴承的外径小于壳体6内径，相应地，轴承支座52从第一端至第二端在纵向截面上的外廓尺寸逐渐增大，即轴承支座52从第一端至第二端的径向外扩尺寸逐渐增大。为了减重，如图5所示，轴承支座52远离推力轴承的一侧设置减重槽524，例如减重槽524环形设置，减重槽524的内壁与安装孔522的侧壁平行，外壁与轴承支座52的外廓形状一致。
此种V形轴承支座52通过采用横截面积渐变的结构，可提高轴承支座52的整体结构强度，各处受力分布均匀，可优化承载能力，而且外侧壁为斜面易于通过铸造实现，通过模具进行铸造时具有拔模斜度。
如图5所示，轴承支座52上设有通气孔526，用于使径向轴承8所在的空间与第一推力轴承10和第二推力轴承10’所在的空间连通，以使径向轴承8的工作环境与 第一推力轴承10和第二推力轴承10’一致，例如使径向轴承8的工作背压与第一推力轴承10和第二推力轴承10’一致。电机腔内有冷却电机的制冷剂进出，压缩机正常运行时，整体电机腔压力和温度是稳定的，推力轴承与径向轴承工作环境与电机腔相同，也就是保证气体循环，且背压相对稳定，防止由于背压波动太大造成轴承气膜波动，从而提高轴承性能。
如图3所示，轴承支座52上沿径向设有操作孔523，以便通过操作孔523在径向轴承8的外壁上安装振动传感器或者温度传感器，以监测径向轴承8的工作状态。操作孔523沿径向外侧的孔段作为旁通孔，保证推力轴承与径向轴承8和电机腔压力温度都相同，操作孔523沿径向内侧的孔段起到给径向轴承8散热的作用。
在一些实施例中，如图3所示，第一推力轴承10直接固定在扩压器3的第一凹槽31底部。例如，第一推力轴承10采用动压推力轴承，为薄片结构，该动压推力轴承直接固定在第一凹槽31底部。此种结构将扩压器3和推力轴承固定板集成为一个零件，采用第一凹槽31的底部作为第一推力轴承10的固定板，无需额外设置推力轴承固定板，可进一步减小轴承支承组件的轴向尺寸，使结构更加紧凑。
在一些实施例中，如图1所示，离心压缩机还包括叶轮2和锁紧部件9，主轴1内设有空腔11并在中心处设有轴芯12，轴芯12的端部伸出主轴1的端部；叶轮2套设在轴芯12的外端，并通过锁紧部件9将叶轮2锁紧在轴芯12上，且叶轮2位于扩压器3的外侧。
该实施例使叶轮2相对于主轴1可拆卸地设置，可降低叶轮拆装难度，并简化叶轮的装配工艺和所需设备，提高装配效率以及拆检工作及维护的可操作性。而且，此种安装方式既能防止主轴1或叶轮2发生变形，也可保证叶轮2的安装强度，避免产生应力集中，从而提升压缩机的压缩能力。另外，通过在主轴1上设置空腔11，可减轻主轴1重量，以提高主轴1的临界转速，进一步提高了压缩机的极限工作能力。
仍参考图1，轴芯12通过在加工空腔11时直接形成，使轴芯12与主轴1的其余部分加工形成一体，无需将轴芯12额外安装在主轴1的空腔内，可进一步降低装配难度，增加轴芯12与主轴1的连接强度，还可保证轴芯12的位置精度，有效解决转子前端的跳动问题，减少悬臂端长度，从而提高压缩机的工作稳定性和可靠性。例如，空腔11是环槽，或者多个相对于轴线中心对称的孔。
如图3所示，推力盘4还包括连接部42，推力盘4与推力部41连接，且套设在主轴1上，第一凹槽31的底部设有通孔34，连接部42嵌入通孔34内。连接部42与 主轴1过盈配合，以使推力盘4可随主轴1一起转动。扩压器3和固定板51固定设置，且与主轴1之间均具有间隙。例如，推力盘4为圆柱阶梯形结构。
如图6所示，离心压缩机还包括密封结构和设在主轴1端部的叶轮2，叶轮2位于扩压器3的外侧。在一些实施例中，通孔34的侧壁设有第一轴向梳齿密封结构35，与推力盘4形成轴封，可减少制冷剂随着叶轮排气通过扩压器3与推力盘4的间隙进入电机腔。在一些实施例中，叶轮2朝向扩压器3的端部设有径向梳齿密封结构21，可减少制冷剂沿着叶轮2与扩压器3之间的间隙向外周流动。在一些实施例中，叶轮2具有嵌入扩压器3内的嵌入部22，例如，嵌入部22是沿轴向延伸的细长条状结构，嵌入部22上沿自身长度方向在径向内侧设有第二轴向梳齿密封结构23，以可减少制冷剂沿着叶轮2与扩压器3之间的间隙向外周流动。
在一些实施例中，梳齿密封结构包括多个间隔设置的齿，齿呈梯形，齿的其中一个侧壁为垂直面，另一个侧壁为斜面且从高压侧向低压侧倾斜。
该实施例能够减少叶轮2与扩压器3之间、扩压器3与推力盘4之间的制冷剂泄漏量，既能保证主轴1和叶轮2运转时需要的间隙，又能防止因间隙过大导致的制冷剂泄露，有效地解决压缩机密封问题，有利于提升压缩机能效。
而且，此种结构将扩压器3、推力轴承固定板和轴封件集成为一个零件，可简化安装结构，使结构更紧凑，并提高装配效率。如图2所示，扩压器3的外周设有定位止口33，以便与壳体6定位安装，再配合销钉精确定位。由此，扩压器3上轴封部分的同轴度和推力轴承固定面的垂直度都在一个零件上保证，不仅降低了加工难度，同时降低了装配累积误差，将同轴度要求高的轴封和垂直度要求高的推力轴承共用定位止口33和销钉进行定位，统一装配基准，降低装配难度，并提高装配精度，既能提高推力轴承固定面的垂直度，以保证推力轴承的工作性能，还能提高第一轴向梳齿密封结构35的同轴度，防止梳齿发生磨损而影响密封性能。
在材料选择方面扩压器3的材料要比推力盘4的硬度低，一般扩压器3采用选铝，推力盘采用45钢或40Cr等。这样如果扩压器3上的第一轴向梳齿密封结构35与主轴1发生磨损，则梳齿先磨损，以防止主轴1磨损。
仍参考图6，密封结构同时包括第一轴向梳齿密封结构35、径向梳齿密封结构21和第二轴向梳齿密封结构23，且径向梳齿密封结构21沿径向位于第一轴向梳齿密封结构35和第二轴向梳齿密封结构23之间。此种设置方式能够使气流形成迂回的流动路径，优化气流减速降压效果，提高密封性能。
具体地，叶轮2朝向扩压器3的一端设有凸台24，凸台24伸入扩压器3的第三凹槽36内，径向梳齿密封结构21设在凸台24的端部，以便在实现径向密封的同时，进一步延长气体流动路径，优化气流减速降压效果，提高密封性能。
另外，本公开还提供了一种空调设备，包括上述实施例的离心压缩机。本公开离心压缩机可承受两个方向的轴向力，保证压缩机全工况运行和反转时运行稳定性；而且能精确保证推力轴承的装配间隙，保证推力轴承的性能，从而提高压缩机的运行稳定性。这两个因素均能提高空调设备工作的稳定性和可靠性。
以上对本公开所提供的一种离心压缩机及空调设备进行了详细介绍。本文中应用了具体的实施例对本公开的原理及实施方式进行了阐述，以上实施例的说明只是用于帮助理解本公开的方法及其核心思想。应当指出，对于本技术领域的普通技术人员来说，在不脱离本公开原理的前提下，还可以对本公开进行若干改进和修饰，这些改进和修饰也落入本公开权利要求的保护范围内。

Claims (16)

  1. 一种离心压缩机，包括：
    主轴(1)；
    扩压器(3)，所述扩压器(3)远离扩压面的一端设有第一推力轴承(10)；
    支承组件(5)，所述支承组件(5)朝向所述扩压器(3)的一端设有第二推力轴承(10’)；以及
    推力盘(4)，被配置为与所述主轴(1)一起可转动，且沿轴向位于所述扩压器(3)与所述支承组件(5)之间，所述推力盘(4)具有推力部(41)，所述推力部(41)两侧与所述第一推力轴承(10)和第二推力轴承(10’)之间的间隙通过所述扩压器(3)与支承组件(5)相互抵靠进行限定。
  2. 根据权利要求1所述的离心压缩机，其中所述扩压器(3)远离扩压面的一端设有第一凹槽(31)，所述第一推力轴承(10)设在所述第一凹槽(31)沿轴向的底部，所述推力部(41)位于所述第一凹槽(31)内。
  3. 根据权利要求1所述的离心压缩机，还包括壳体(6)和径向轴承(8)，其中，所述支承组件(5)包括：
    固定板(51)，所述固定板(51)上朝向所述扩压器(3)的一侧设置所述第二推力轴承(10’)；和
    轴承支座(52)，设在所述固定板(51)远离所述扩压器(3)的一侧，所述轴承支座(52)的第一端与所述固定板(51)连接，第二端与所述壳体(6)连接，用于通过所述径向轴承(8)对所述主轴(1)进行支撑。
  4. 根据权利要求3所述的离心压缩机，其中所述固定板(51)与所述轴承支座(52)形成一体结构。
  5. 根据权利要求3所述的离心压缩机，其中所述固定板(51)用于限制所述径向轴承(8)沿轴向朝向所述扩压器(3)一侧的位移。
  6. 根据权利要求5所述的离心压缩机，其中所述固定板(51)朝向所述轴承支座(52)的一端设有定位环(511)，所述轴承支座(52)上设有环形的第二凹槽(521)，所述定位环(511)嵌入所述第二凹槽(521)中，且所述定位环(511)的内壁(512)与所述径向轴承(8)部分长度段的外壁配合。
  7. 根据权利要求1所述的离心压缩机，还包括壳体(6)和径向轴承(8)，其 中，所述支承组件(5)包括：
    轴承支座(52)，与所述壳体(6)连接，所述第二推力轴承(10’)设在所述轴承支座(52)上朝向扩压器(3)的一侧，所述轴承支座(52)用于通过所述径向轴承(8)对所述主轴(1)进行支撑。
  8. 根据权利要求1所述的离心压缩机，还包括壳体(6)和径向轴承(8)，所述支承组件(5)包括轴承支座(52)，所述轴承支座(52)的第一端抵靠在所述扩压器(3)上，第二端与所述壳体(6)连接，用于通过所述径向轴承(8)对所述主轴(1)进行支撑，所述轴承支座(52)从第一端至第二端径向外廓尺寸逐渐增大。
  9. 根据权利要求1所述的离心压缩机，还包括径向轴承(8)，所述支承组件(5)包括轴承支座(52)，用于通过所述径向轴承(8)对所述主轴(1)进行支撑，所述轴承支座(52)上设有通气孔(526)，用于使所述径向轴承(8)所在的空间与所述第一推力轴承(10)和第二推力轴承(10’)所在的空间连通。
  10. 根据权利要求1所述的离心压缩机，还包括叶轮(2)和锁紧部件(9)，所述主轴(1)内设有空腔(11)并在中心处设有轴芯(12)，所述轴芯(12)的端部伸出所述主轴(1)的端部；所述叶轮(2)套设在所述轴芯(12)的外端，并通过所述锁紧部件(9)将所述叶轮(2)锁紧在所述轴芯(12)上，且所述叶轮(2)位于所述扩压器(3)的外侧。
  11. 根据权利要求2所述的离心压缩机，其中所述第一推力轴承(10)直接固定在所述第一凹槽(31)的底部。
  12. 根据权利要求2所述的离心压缩机，其中所述推力盘(4)还包括连接部(42)，所述连接部(42)与所述推力部(41)连接，且套设在所述主轴(1)上，所述第一凹槽(31)的底部设有通孔(34)，所述连接部(42)嵌入所述通孔(34)内。
  13. 根据权利要求12所述的离心压缩机，还包括密封结构和设在所述主轴(1)端部的叶轮(2)，所述叶轮(2)位于所述扩压器(3)的外侧，所述密封结构采用如下设置形式中的至少一种：
    所述通孔(34)侧壁设有第一轴向梳齿密封结构(35)；
    所述叶轮(2)朝向所述扩压器(3)的端部设有径向梳齿密封结构(21)；和
    所述叶轮(2)具有嵌入所述扩压器(3)内的嵌入部(22)，所述嵌入部(22)上沿所述轴向设有第二轴向梳齿密封结构(23)。
  14. 根据权利要求13所述的离心压缩机，其中所述密封结构同时包括：所述第 一轴向梳齿密封结构(35)、径向梳齿密封结构(21)和第二轴向梳齿密封结构(23)，且所述径向梳齿密封结构(21)沿径向位于所述第一轴向梳齿密封结构(35)和第二轴向梳齿密封结构(23)之间。
  15. 根据权利要求1所述的离心压缩机，还包括用于对支撑所述主轴(1)的径向轴承(8)，所述第一推力轴承(10)、第二推力轴承(10’)和所述径向轴承(8)中的至少一个为气悬浮轴承。
  16. 一种空调设备，包括权利要求1～15任一所述的离心压缩机。
PCT/CN2019/113018 2018-12-25 2019-10-24 离心压缩机及空调设备 Ceased WO2020134433A1 (zh)

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