WO2023087731A1 - 压缩机及制冷系统 - Google Patents

压缩机及制冷系统 Download PDF

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Publication number
WO2023087731A1
WO2023087731A1 PCT/CN2022/102794 CN2022102794W WO2023087731A1 WO 2023087731 A1 WO2023087731 A1 WO 2023087731A1 CN 2022102794 W CN2022102794 W CN 2022102794W WO 2023087731 A1 WO2023087731 A1 WO 2023087731A1
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WIPO (PCT)
Prior art keywords
bearing
air
axial
rotor
bearings
Prior art date
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PCT/CN2022/102794
Other languages
English (en)
French (fr)
Inventor
张晓锐
张捷
邓善营
王书森
毛守博
Original Assignee
青岛海尔空调电子有限公司
青岛海尔空调器有限总公司
海尔智家股份有限公司
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Application filed by 青岛海尔空调电子有限公司, 青岛海尔空调器有限总公司, 海尔智家股份有限公司 filed Critical 青岛海尔空调电子有限公司
Publication of WO2023087731A1 publication Critical patent/WO2023087731A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/051—Axial thrust balancing
    • F04D29/0513—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/003—Couplings; Details of 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
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K11/00—Structural association of dynamo-electric machines with electric components or with devices for shielding, monitoring or protection
    • H02K11/20—Structural association of dynamo-electric machines with electric components or with devices for shielding, monitoring or protection for measuring, monitoring, testing, protecting or switching
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K11/00—Structural association of dynamo-electric machines with electric components or with devices for shielding, monitoring or protection
    • H02K11/20—Structural association of dynamo-electric machines with electric components or with devices for shielding, monitoring or protection for measuring, monitoring, testing, protecting or switching
    • H02K11/21—Devices for sensing speed or position, or actuated thereby
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H02K5/161—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields radially supporting the rotary shaft at both ends of the rotor
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/04—Balancing means
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/083—Structural association with bearings radially supporting the rotary shaft at both ends of the rotor
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K2213/00—Specific aspects, not otherwise provided for and not covered by codes H02K2201/00 - H02K2211/00
    • H02K2213/03—Machines characterised by numerical values, ranges, mathematical expressions or similar information
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present application relates to the technical field of compressors, for example, to a compressor and a refrigeration system.
  • the centrifugal compressor is a key component in the field of air conditioning and refrigeration.
  • the bearings of the compressor include oil-lubricated bearings and suspension bearings, and the suspension bearings include magnetic suspension bearings and air suspension bearings.
  • Compressors with air suspension bearings do not need to use lubricating oil to lubricate the bearings, which avoids the mixing of lubricating oil and refrigerant to reduce the heat exchange efficiency of the air conditioning system.
  • the air bearing has no friction loss and can operate with ultra-low noise, and has great application prospects in the field of air conditioning and refrigeration.
  • the use of air bearings will inevitably cause axial or radial offset of the rotor. Once the offset is too large, the rotor and bearing will be worn, the bearing and rotor will be damaged, and the service life of the compressor will be affected.
  • the prior art discloses a compressor in which a thrust disc is sheathed on the shaft of the rotor, and air bearings are arranged on both sides of the thrust disc.
  • the axial force generated by the rotor is transmitted to the thrust disc, and the thrust disc transmits the axial force to the air bearing, and finally the axial force is balanced by the air bearing.
  • the embodiments of the present disclosure provide a compressor and a refrigeration system, which solve the problem that the critical speed of the rotor is reduced by setting a thrust plate to balance the axial offset of the rotor.
  • the compressor includes:
  • the rotor includes an intermediate shaft body and two end shaft bodies; the two end shaft bodies are respectively arranged at both ends of the intermediate shaft body, and the diameter of the end shaft body is smaller than that of the intermediate shaft body diameter;
  • the adjustment assembly includes an axial adjustment part, and the axial adjustment part includes two air bearings; The two ends of the intermediate shaft body;
  • the two air-bearing axial bearings are used to balance the axial offset of the rotor.
  • the axial adjustment part further includes:
  • an axial monitoring device for monitoring the axial offset of the rotor
  • a flow regulating device used to adjust the air supply volume of the two air-bearing axial bearings
  • a first controller electrically connected to the axial monitoring device and the flow regulating device, is used to control the flow regulating device according to the axial offset.
  • an identification ring is sheathed on the intermediate shaft
  • the axial monitoring device includes:
  • One or more displacement sensors are used to monitor the axial displacement of the marking ring.
  • the compressor also includes:
  • the installation assembly includes two bearing supports; the two bearing supports are respectively used to install the two air-bearing axial bearings, and each bearing support is provided with a first flow channel for The corresponding air-bearing axial bearing is supplied with lubricating medium.
  • each bearing support is provided with a pressure equalizing assembly, and the pressure equalizing assembly includes:
  • the pressure equalizing groove is arranged around the bearing support; one end of the first flow channel is connected to the bottom of the pressure equalizing groove, and the other end is connected to the air bearing axial bearing; the external supply device supplies lubricating medium into the pressure equalizing groove .
  • each bearing support is also provided with a sealing assembly, and the sealing assembly includes:
  • Two sealing rings are sheathed on the bearing support and are respectively located on both sides of the pressure equalizing groove for sealing the gap on both sides of the pressure equalizing groove.
  • the compressor also includes:
  • the support assembly includes two air bearing radial bearings; the two air bearing radial bearings are respectively sleeved on the two end shafts to support the rotor, and each of the air bearing radial bearings is located at One side of the air-bearing axial bearing is away from the other air-bearing axial bearing.
  • the two air-bearing radial bearings are respectively installed in the two bearing supports, and each bearing support is provided with a second flow channel;
  • One end of the second flow channel communicates with the bottom of the pressure equalizing groove, and the other end communicates with the corresponding air-bearing radial bearing, so as to supply lubricating medium to the corresponding air-bearing radial bearing.
  • each bearing support is also provided with a shaft end cover
  • the adjustment assembly also includes:
  • the radial adjustment part includes a plurality of auxiliary air passages; the plurality of auxiliary air passages are arranged around the shaft cover, and each of the auxiliary air passages corresponds to one or more radial offset directions of the rotor;
  • each of the auxiliary air passages communicates with the gap between the end shaft body and the air-bearing radial bearing, so as to supply air to the gap so as to balance the radial deviation of the rotor.
  • the refrigeration system includes the compressor described in any of the above embodiments.
  • the diameter of the middle shaft body is larger than that of the end shaft body to form a thick middle shaft design with thin ends, and two air-bearing axial bearings are sleeved on the two end shafts respectively.
  • the body is used to balance the axial offset of the rotor. In this way, there is no need to set a thrust disc on the shaft body of the rotor, which reduces the load on the rotor, shortens the length of the rotor, optimizes the layout of the bearing-rotor system, and effectively increases the critical speed of the rotor.
  • Fig. 1 is a schematic structural diagram of a compressor provided by an embodiment of the present disclosure
  • Fig. 2 is an enlarged view of part A of Fig. 1;
  • Fig. 3 is an enlarged view of part B of Fig. 1;
  • Fig. 4 is a schematic structural diagram of a rotor provided by an embodiment of the present disclosure.
  • Fig. 5 is a schematic structural diagram of another compressor provided by an embodiment of the present disclosure.
  • Fig. 6 is an enlarged view of part C of Fig. 5;
  • Fig. 7 is a schematic structural diagram of a sealing assembly provided by an embodiment of the present disclosure.
  • Fig. 8 is a schematic structural diagram of a shaft end cover provided by an embodiment of the present disclosure.
  • Fig. 9 is a schematic structural diagram of different flow channels provided by an embodiment of the present disclosure.
  • Fig. 10 is a schematic structural diagram of an auxiliary airway provided by an embodiment of the present disclosure.
  • 100 compressor; 110: rotor; 111: intermediate shaft body; 112: end shaft body; 113: logo ring; 120: stator; 130: motor chamber; 140: casing;
  • 200 Air-bearing axial bearing
  • 201 Displacement sensor
  • 210 Bearing support
  • 211 Pressure equalizing groove
  • 212 Sealing ring
  • 220 Shaft cover
  • 221 Auxiliary air passage
  • 230 Air-bearing radial bearing
  • 300 the first flow channel; 310: the second flow channel; 320: the third flow channel; 330: the fourth flow channel.
  • orientations or positional relationships indicated by the terms “upper”, “lower”, “inner”, “middle”, “outer”, “front”, “rear” etc. are based on the orientations or positional relationships shown in the drawings. Positional relationship. These terms are mainly used to better describe the embodiments of the present disclosure and their implementations, and are not used to limit that the indicated devices, elements or components must have a specific orientation, or be constructed and operated in a specific orientation. Moreover, some of the above terms may be used to indicate other meanings besides orientation or positional relationship, for example, the term “upper” may also be used to indicate a certain attachment relationship or connection relationship in some cases. Those skilled in the art can understand the specific meanings of these terms in the embodiments of the present disclosure according to specific situations.
  • connection can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection, or an electrical connection; it can be a direct connection, or an indirect connection through an intermediary, or two devices, components or Internal connectivity between components.
  • A/B means: A or B.
  • a and/or B means: A or B, or, A and B, these three relationships.
  • the compressor 100 is a key component in the refrigeration system, and the support assembly of the bearing-rotor 110 system does not need to be lubricated with lubricating oil when the air suspension bearing is used, which avoids the mixing of the lubricating oil and the refrigerant in the air-conditioning system and prevents lubrication. Oil deposits on the heat exchange tube wall of the evaporator or condenser, affecting the heat exchange efficiency.
  • an external air supply device is required to continuously and stably supply air to the air suspension bearing.
  • the rotor 110 will have axial movement and radial displacement due to unstable gas supply or external force, which will lead to the imbalance of the bearing-rotor 110 system and seriously affect the service life of the compressor 100 .
  • an embodiment of the present disclosure provides a compressor 100 , including a rotor 110 and an adjustment assembly.
  • the rotor 110 includes an intermediate shaft body 111 and two end shaft bodies 112; the two end shaft bodies 112 are respectively arranged at the two ends of the intermediate shaft body 111, and the diameter of the end shaft body 112 is smaller than that of the intermediate shaft body 111.
  • the adjustment assembly includes an axial adjustment part, and the axial adjustment part includes two air-bearing axial bearings 200; the two air-bearing axial bearings 200 are respectively sleeved on the two end shaft bodies 112, and are respectively close to the middle shaft body 111 at both ends; wherein, two air-bearing axial bearings 200 are used to balance the axial offset of the rotor 110 .
  • the diameter of the middle shaft body 111 is larger than the diameter of the end shaft body 112 to form a shaft body design with a thick middle and thin ends, and two air-bearing axial bearings 200 are respectively sleeved on the two ends.
  • the shaft 112 at one end is used to balance the axial deflection of the rotor 110. In this way, there is no need to install a thrust plate on the shaft of the rotor 110, which reduces the load on the rotor 110, shortens the length of the rotor 110, optimizes the layout of the bearing-rotor 110 system, and effectively increases the critical speed of the rotor 110.
  • the stator 120 is arranged in the motor chamber 130 and bounded by the stator 120, the end shaft body 112 located in front of the stator 120 becomes the front shaft body,
  • the end shaft 112 is called the rear shaft.
  • Two air-bearing axial bearings 200 are sleeved on the two end shafts 112, among which the one sleeved on the front shaft is called the front air bearing, and the one sleeved on the rear shaft is called the rear air bearing.
  • Floating shaft bearing is used to Floating shaft bearing.
  • the compressor 100 further includes a mounting assembly, and the mounting assembly includes two bearing supports 210 .
  • the two bearing supports 210 are used to install the two air-bearing axial bearings 200, wherein the front air-bearing axial bearing is installed as the front bearing support, and the rear air-bearing axial bearing is installed as the rear bearing support.
  • a first flow channel 300 is opened on each bearing support 210 , and the external supply equipment supplies air to the corresponding air bearing axial bearing 200 through the first flow channel 300 .
  • an accommodating space is provided on opposite sides of the two bearing supports 210 , and the parts of the intermediate shaft body 111 respectively connecting the front end shaft body and the rear end shaft body are disposed in the accommodating space.
  • the radial displacement of the intermediate shaft body 111 is limited to a certain extent by the bearing support 210 , which improves the stability of the rotor 110 .
  • the axial regulating part further includes an axial monitoring device, a flow regulating device and a first controller.
  • the axial monitoring device is used to monitor the axial displacement of the rotor 110;
  • the flow regulating device is used to adjust the air supply volume of the two air bearing axial bearings 200;
  • the first controller is electrically connected to the axial monitoring device and the flow rate
  • a regulating device is used to control the flow regulating device according to the axial offset.
  • the axial monitoring device includes one or more displacement sensors 201 .
  • the part of the intermediate shaft body 111 close to the rear end shaft body is provided with a marking ring 113, which is located in the motor cavity 130 and in front of the rear bearing support; the position of the displacement sensor 201 corresponding to the marking ring 113 is set at the rear
  • the bearing seat faces to the side wall of the motor cavity 130 .
  • the motor cavity 130 has a relatively large space, and the axial displacement of the rotor 110 can be detected sensitively by setting the marking ring 113 and the displacement sensor 201 .
  • the marking ring 113 is made of light material and has a diameter slightly larger than that of the intermediate shaft body 111 , so as to reduce the influence of the marking ring 113 on the critical speed of the rotor 110 .
  • the direction of axial deviation includes forward deviation and rear deviation.
  • the gap between the marking ring 113 and the rear bearing seat becomes smaller, the rotor 110 is deflected backward; when the gap between the marking ring 113 and the rear bearing seat becomes larger, the rotor 110 is deflecting forward.
  • the flow regulating device includes two first solenoid valves respectively arranged in the two first flow channels 300 .
  • the opening degree of the first solenoid valve By changing the opening degree of the first solenoid valve, the air supply volume of the corresponding air-bearing axial bearing 200 is adjusted, and then the pressure of the air-bearing axial bearing 200 is adjusted, so as to balance the offset of the rotor 110 in different axial offset directions.
  • the rotor 110 deviates forward, increase the air supply volume of the front air bearing axial bearing and decrease the air supply volume of the rear air bearing axial bearing; The air supply to the bearing reduces the air supply to the front air bearing axial bearing.
  • the axial offset of the rotor 110 is denoted as a.
  • a at this time is recorded as 0.
  • the two first solenoid valves both supply air to the corresponding air bearing axial bearing 200 with an opening of 45°.
  • the first controller controls the first electromagnetic valve corresponding to the front air-bearing axial bearing to supply air at an opening of 90°, and controls the first electromagnetic valve corresponding to the rear air-bearing axial bearing.
  • a solenoid valve supplies air with an opening of 20°. Therefore, the pressure exerted by the front air-bearing axial bearing on the intermediate shaft body 111 is increased, the pressure exerted by the rear air-bearing axial bearing on the intermediate shaft body 111 is reduced, and the axial force generated by the rotor 110 in the front deflection direction is quickly balanced .
  • the first controller controls the first electromagnetic valve corresponding to the front air bearing axial bearing to supply air at an opening of 20°, and controls the first electromagnetic valve corresponding to the rear air bearing axial bearing.
  • a solenoid valve supplies air with a 90° opening. Therefore, the pressure exerted by the rear air-bearing axial bearing on the intermediate shaft body 111 is increased, the pressure exerted by the front air-bearing axial bearing on the intermediate shaft body 111 is reduced, and the axial force generated by the rotor 110 in the rear deflection direction is quickly balanced .
  • each bearing support 210 is provided with a pressure equalizing assembly, and the pressure equalizing assembly includes a pressure equalizing groove 211 arranged around the bearing support 210; one end of the first flow channel 300 communicates with At the bottom of the pressure equalizing groove 211 , the other end communicates with the air bearing axial bearing 200 ; the external supply device supplies lubricating medium into the pressure equalizing groove 211 .
  • the casing 140 of the compressor 100 is configured in a cylindrical shape. After the bearing support 210 is installed in the casing 140 , the notch of the pressure equalizing groove 211 abuts against the inner surface of the casing 140 .
  • the pressure equalizing groove 211 and the inner surface of the housing 140 enclose a medium loop.
  • a third flow channel 320 is defined above the casing 140 , one end of the third flow channel 320 communicates with the external supply device, and the other end communicates with the pressure equalizing tank 211 .
  • the external supply device supplies lubricating medium to the pressure equalizing groove 211 through the third flow channel 320 , and after the lubricating medium fills the medium ring, the first solenoid valve corresponding to the first flow channel 300 is opened to supply the lubricating medium to the air-bearing axial bearing 200 .
  • the lubricating medium here includes gaseous refrigerant or gas-liquid mixed refrigerant.
  • the external supply device Limited by the performance of the external supply device itself, the instability of the gas medium or gas-liquid mixed medium, the pressure loss of the medium in the pipeline, etc., if the external supply device directly supplies the first flow channel 300 through the third flow channel 320 After the gas is released, the lubricating medium entering the air-bearing axial bearing 200 is extremely unstable, which seriously affects the function of the air-bearing axial bearing 200 to balance the axial force.
  • the external supply device first supplies the lubricating medium to the pressure equalizing groove 211 through the third flow channel 320, and the pressure equalizing groove 211 provides a buffer space for the lubricating medium, as the lubricating medium flows in the pressure equalizing groove 211 After its own heat exchange, the pressure and temperature gradually become uniform. The uniform lubricating medium is then supplied to the air bearing axial bearing 200 , which ensures the stability of the lubricating medium in the air bearing axial bearing 200 .
  • the voltage equalizing assembly further includes a plurality of heating resistors arranged around the pressure equalizing groove 211 , and each heating resistor can be individually controlled.
  • the pressure equalizing groove 211 is divided into four equal parts, and a heating resistor and a temperature sensor are arranged in each equalized area.
  • the temperature sensor in a certain equal-division area monitors that the temperature of the lubricating medium in this area is lower than the average temperature monitored by the temperature sensors in four equal-division areas, start the heating resistance in this equal-division area, thereby Quickly balance the temperature and pressure of the lubricating medium in the equalizing groove 211.
  • each bearing support 210 is also provided with a sealing assembly, the sealing assembly includes two sealing rings 212, and the two sealing rings 212 are sleeved on the bearing support 210 and respectively located in the pressure equalization groove 211
  • the two sides are used to seal the gap on both sides of the pressure equalizing groove 211.
  • a front sealing ring groove and a rear sealing ring groove are arranged around the bearing support 210 , wherein the front sealing groove is located in front of the pressure equalizing groove 211 , and the rear sealing groove is located behind the pressure equalizing groove 211 .
  • the two sealing rings 212 are set respectively in the front sealing ring groove and the rear sealing ring groove.
  • the support assembly of the compressor 100 includes two air bearings 230 , and the two air bearings 230 are sleeved on the two end shafts 112 respectively. to support the rotor 110 and are installed in two bearing supports 210 respectively.
  • each air bearing radial bearing 230 is located on a side of one air bearing axial bearing 200 away from the other air bearing axial bearing 200 .
  • each bearing support 210 is provided with a second flow channel 310 .
  • One end of the second channel 310 communicates with the bottom of the pressure equalizing groove 211, and the other end communicates with the corresponding air bearing radial bearing 230.
  • the external supply device first supplies the lubricating medium to the pressure equalizing groove 211 through the third flow channel 320, and the lubricating medium is buffered in the pressure equalizing groove 211. As the lubricating medium flows in the pressure equalizing groove 211, its pressure and temperature gradually become uniform. The final lubricating medium flows to the air bearing radial bearing 230 .
  • a second solenoid valve is provided in each second flow channel 310 , and the air supply volume of the corresponding air bearing radial bearing 230 is adjusted by changing the opening degree of the second solenoid valve.
  • the diameter of the first flow channel 300 is marked as d1
  • the diameter of the second flow channel 310 is marked as d2
  • the diameter of the third flow channel 320 is marked as d3.
  • the diameters of the three flow channels are set to satisfy d32>d12+d22.
  • each bearing support 210 is also provided with a shaft end cover 220; the adjustment assembly further includes a radial adjustment part, and the radial adjustment part includes a plurality of auxiliary air passages 221; A plurality of auxiliary air passages 221 are arranged around the shaft end cover 220, and each auxiliary air passage 221 corresponds to one or more radial offset directions of the rotor 110; wherein, each auxiliary air passage 221 is connected to the end shaft body 112 and the gap between the air bearing radial bearing 230 to supply air to the gap to balance the rotor 110 .
  • the center of the shaft end cover 220 is provided with an inner hole, and the air-floating axial bearing 200 and the air-floating radial bearing 230 are sequentially sleeved on the end shaft body 112 and then installed in the corresponding bearing support 210.
  • the shaft end cover 220 is mounted on a side of the bearing support 210 away from the motor cavity 130 .
  • the shaft bodies 112 at the two ends protrude outward through the inner holes of the shaft end covers 220 at the corresponding ends respectively, and are used for installing components such as impellers.
  • the radial deflection directions of the rotor 110 at least include upward deflection, downward deflection, left deflection and right deflection.
  • the four auxiliary air passages 221 are arranged around the inner hole of the shaft end cover 220 corresponding to the upper, lower, left and right directions respectively.
  • the channel 221 corresponds to the left deviation
  • the right auxiliary air channel 221 corresponds to the right deviation.
  • the upper auxiliary air channel 221 is used to supply air to the upper direction of the rotor 110, thereby supporting the rotor 110 in the upper direction;
  • the lower auxiliary air channel 221 is used to supply air to the lower direction of the rotor 110, thereby supporting the rotor 110 in the lower direction ;
  • the left auxiliary air channel 221 is used to supply air to the left direction of the rotor 110, thereby supporting the rotor 110 in the left direction;
  • the right auxiliary air channel 221 is used to supply air to the right direction of the rotor 110, thereby supporting the rotor 110 in the right direction .
  • the auxiliary air channel 221 corresponding to the radial deflection direction is opened to support the rotor 110 in the radial deflection direction, thereby balancing the rotor 110 .
  • each auxiliary air channel 221 is provided with a third solenoid valve.
  • the opening of the solenoid valve to increase the air supply of the corresponding auxiliary air channel 221, thereby increasing the radial offset Directional bearing force to quickly balance the rotor 110.
  • a fourth flow channel 330 is opened on the bearing support 210 .
  • One end of the fourth channel 330 communicates with the side wall of the pressure equalizing tank 211 , and the other end communicates with the inlet of the auxiliary air channel 221 .
  • the outlet of the auxiliary air channel 221 communicates with the gap between the end shaft body 112 and the air bearing radial bearing 230 .
  • the lubricating medium is supplied to the auxiliary air channel 221 through the fourth flow channel 330 after the temperature and pressure of the lubricating medium are equalized under the action of the pressure equalizing groove 211 .
  • the pressure equalizing groove 211 is used to supply the lubricating medium to the air bearing radial bearing 230 and the auxiliary air channel 221 respectively, which ensures the consistency of the gas entering the gap from the air bearing radial bearing 230 and the auxiliary air channel 221 respectively, and avoids two different Gases of different temperatures and pressures exchange heat in this gap, affecting the stability of the gas in the gap.
  • the lubricating medium is respectively supplied to the air-bearing radial bearing 230 used to support the rotor 110 and used to adjust the axial offset of the rotor 110 through a reasonable flow channel design.
  • the air-bearing axial bearing 200 and the auxiliary air channel 221 for adjusting the radial offset of the rotor 110 have a reasonable and compact overall structure, which simplifies the structure of the compressor 100 .
  • An embodiment of the present disclosure also provides a refrigeration system, including the compressor 100 described in any of the foregoing embodiments.
  • the refrigeration system further includes an air supply tank, which is connected to the third flow channel 320 .
  • the gas supply tank supplies gaseous refrigerant or gas-liquid mixed refrigerant into the pressure equalizing tank 211 through the third flow channel 320 , and the gaseous refrigerant or gas-liquid mixed refrigerant in the pressure equalizing tank 211 is supplied through the first flow channel 300 after the pressure and temperature of the equalizing tank 211 are balanced.
  • To the air bearing axial bearing 200 it is supplied to the air bearing radial bearing 230 through the second channel 310 , and is supplied to the auxiliary air channel 221 through the fourth channel 330 .
  • the refrigeration system further includes an evaporator.
  • the bottom of the casing 140 is respectively provided with a cooling inlet and an air return port.
  • the refrigerant passes through the cooling inlet into the casing and exchanges heat with the stator 120 to cool it.
  • the gaseous refrigerant that absorbs heat and becomes medium-temperature and medium-pressure is discharged into the evaporator from the air return port.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Microelectronics & Electronic Packaging (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)

Abstract

提供了一种压缩机，包括：转子(110)，包括中间轴身(111)和两个端部轴身(112)；两个端部轴身(112)分别设置于中间轴身(111)的两端，且端部轴身(112)的直径小于中间轴身(111)的直径；调节组件，包括轴向调节部，轴向调节部包括两个气浮轴向轴承(200)；两个气浮轴向轴承(200)分别套设于两个端部轴身(112)，且分别靠近中间轴身(111)的两端；其中，两个气浮轴向轴承(200)用以平衡转子(110)的轴向偏移。两个气浮轴向轴承(200)分别套设在两个端部轴身(112)上用以平衡转子(110)的轴向偏移，无需在转子(110)的轴身上设置推力盘，减轻了转子(110)的负载，减短了转子(110)的长度，有效提升了转子(110)的临界速度。

Description

压缩机及制冷系统
本申请基于申请号为202111390245.6、申请日为2021年11月19日的中国专利申请提出，并要求该中国专利申请的优先权，该中国专利申请的全部内容在此引入本申请作为参考。
技术领域
本申请涉及压缩机技术领域，例如涉及一种压缩机及制冷系统。
背景技术
离心式压缩机是空调制冷领域的关键构件，压缩机的轴承包括油润滑轴承和悬浮轴承，悬浮轴承又包括磁悬浮轴承和气悬浮轴承。采用气悬浮轴承的压缩机无需使用润滑油润滑轴承，避免了润滑油和冷媒混合降低空调系统的换热效率。并且气浮轴承没有摩擦损失、可以超低噪音运行，在空调制冷领域具有重大应用前景。但是，采用气浮轴承不可避免地会出现转子发生轴向偏移或径向偏移，一旦偏移量过大会导致转子和轴承发生磨损，损坏轴承和转子，影响压缩机的使用寿命。
现有技术公开了一种压缩机，在转子的轴身上套设推力盘，在推力盘的两侧设置气浮轴向轴承。转子产生的轴向力传递至推力盘，推力盘将轴向力传递至气浮轴向轴承，最后通过气浮轴向轴承平衡该轴向力。
在实现本公开实施例的过程中，发现上述相关技术中至少存在如下问题：为了布置推力盘和两个气浮轴向轴承，转子的长度较长；且设置推力盘后使转子的负载增大，推力盘增大了转子的外径，以上原因降低了转子的临界速度，影响了压缩机的性能。
发明内容
为了对披露的实施例的一些方面有基本的理解，下面给出了简单的概括。所述概括不是泛泛评述，也不是要确定关键/重要组成元素或描绘这些实施例的保护范围，而是作为后面的详细说明的序言。
本公开实施例提供一种压缩机及制冷系统，解决了为了平衡转子的轴向偏移而设置推力盘导致降低转子临界速度降低的问题。
在一些实施例中，所述压缩机包括：
转子，包括中间轴身和两个端部轴身；两个所述端部轴身分别设置于所述中间轴身的 两端，且所述端部轴身的直径小于所述中间轴身的直径；
调节组件，包括轴向调节部，所述轴向调节部包括两个气浮轴向轴承；两个所述气浮轴向轴承分别套设于两个所述端部轴身，且分别靠近所述中间轴身的两端；
其中，两个所述气浮轴向轴承用以平衡所述转子的轴向偏移。
可选地，所述轴向调节部还包括：
轴向监测装置，用以监测所述转子的轴向偏移量；
流量调节装置，用以调节两个所述气浮轴向轴承的供气量；
第一控制器，电连接于所述轴向监测装置和所述流量调节装置，用以根据所述轴向偏移量控制所述流量调节装置。
可选地，所述中间轴身上套设有标识圆环；
所述轴向监测装置包括：
一个或多个位移传感器，用于监测所述标识圆环的轴向偏移量。
可选地，所述压缩机还包括：
安装组件，包括两个轴承支座；两个所述轴承支座分别用以安装两个所述气浮轴向轴承，且每一所述轴承支座上设有一个第一流道，用以向对应的所述气浮轴向轴承供给润滑介质。
可选地，每一所述轴承支座设有一均压组件，所述均压组件包括：
均压槽，环绕所述轴承支座设置；所述第一流道的一端连通于所述均压槽的底部，另一端连通于气浮轴向轴承；外部供给装置向均压槽内供给润滑介质。
可选地，每一所述轴承支座还设有一密封组件，所述密封组件包括：
两个密封圈，套设于所述轴承支座且分别位于所述均压槽的两侧，用以密封所述均压槽两侧的间隙。
可选地，所述压缩机还包括：
支撑组件，包括两个气浮径向轴承；两个所述气浮径向轴承分别套设于两个所述端部轴身以支撑所述转子，且每一所述气浮径向轴承位于一个所述气浮轴向轴承远离另一个所述气浮轴向轴承的一侧。
可选地，两个所述气浮径向轴承分别安装于两个所述轴承支座内，且每一所述轴承支座上设有一个第二流道；
所述第二流道的一端连通于所述均压槽的底部，另一端连通于对应的所述气浮径向轴承，用以向对应的所述气浮径向轴承供给润滑介质。
可选地，每一所述轴承支座还设有一轴端盖；
所述调节组件还包括：
径向调节部，包括多条辅助气道；所述多条辅助气道环绕所述轴端盖设置，且每一所述辅助气道对应所述转子的一个或多个径向偏移方向；
其中，每一所述辅助气道均连通于所述端部轴身和所述气浮径向轴承之间的间隙，以向所述间隙供气从而平衡所述转子的径向偏移。
在一些实施例中，所述制冷系统包括上述任一实施例中所述的压缩机。
本公开实施例提供的压缩机及制冷系统，可以实现以下技术效果：
采用本公开实施例提供的压缩机，中间轴身的直径大于端部轴身的直径形成中间粗两端细的轴身设计，并且两个气浮轴向轴承分别套设在两个端部轴身上用以平衡转子的轴向偏移。这样无需在转子的轴身上设置推力盘，减轻了转子的负载，减短了转子的长度，优化了轴承-转子系统的布局，进而有效提升了转子的临界速度。
以上的总体描述和下文中的描述仅是示例性和解释性的，不用于限制本申请。
附图说明
一个或多个实施例通过与之对应的附图进行示例性说明，这些示例性说明和附图并不构成对实施例的限定，附图中具有相同参考数字标号的元件示为类似的元件，附图不构成比例限制，并且其中：
图1是本公开实施例提供的压缩机的结构示意图；
图2是图1的A部放大图；
图3是图1的B部放大图；
图4是本公开实施例提供的转子的结构示意图；
图5是本公开实施例提供的另一压缩机的结构示意图；
图6是图5的C部放大图；
图7是本公开实施例提供的密封组件的结构示意图；
图8是本公开实施例提供的轴端盖的结构示意图；
图9是本公开实施例提供的不同流道的结构示意图；
图10是本公开实施例提供的辅助气道的结构示意图。
附图标记：
100：压缩机；110：转子；111：中间轴身；112：端部轴身；113：标识圆环；120：定子；130：电机腔；140：机壳；
200：气浮轴向轴承；201：位移传感器；210：轴承支座；211：均压槽；212：密封 圈；220：轴端盖；221：辅助气道；230：气浮径向轴承；
300：第一流道；310：第二流道；320：第三流道；330：第四流道。
具体实施方式
为了能够更加详尽地了解本公开实施例的特点与技术内容，下面结合附图对本公开实施例的实现进行详细阐述，所附附图仅供参考说明之用，并非用来限定本公开实施例。在以下的技术描述中，为方便解释起见，通过多个细节以提供对所披露实施例的充分理解。然而，在没有这些细节的情况下，一个或多个实施例仍然可以实施。在其它情况下，为简化附图，熟知的结构和装置可以简化展示。
本公开实施例的说明书和权利要求书及上述附图中的术语“第一”、“第二”等是用于区别类似的对象，而不必用于描述特定的顺序或先后次序。应该理解这样使用的数据在适当情况下可以互换，以便这里描述的本公开实施例的实施例。此外，术语“包括”和“具有”以及他们的任何变形，意图在于覆盖不排他的包含。
本公开实施例中，术语“上”、“下”、“内”、“中”、“外”、“前”、“后”等指示的方位或位置关系为基于附图所示的方位或位置关系。这些术语主要是为了更好地描述本公开实施例及其实施例，并非用于限定所指示的装置、元件或组成部分必须具有特定方位，或以特定方位进行构造和操作。并且，上述部分术语除了可以用于表示方位或位置关系以外，还可能用于表示其他含义，例如术语“上”在某些情况下也可能用于表示某种依附关系或连接关系。对于本领域普通技术人员而言，可以根据具体情况理解这些术语在本公开实施例中的具体含义。
另外，术语“设置”、“连接”、“固定”应做广义理解。例如，“连接”可以是固定连接，可拆卸连接，或整体式构造；可以是机械连接，或电连接；可以是直接相连，或者是通过中间媒介间接相连，又或者是两个装置、元件或组成部分之间内部的连通。对于本领域普通技术人员而言，可以根据具体情况理解上述术语在本公开实施例中的具体含义。
除非另有说明，术语“多个”表示两个或两个以上。
本公开实施例中，字符“/”表示前后对象是一种“或”的关系。例如，A/B表示：A或B。
术语“和/或”是一种描述对象的关联关系，表示可以存在三种关系。例如，A和/或B，表示：A或B，或，A和B这三种关系。
需要说明的是，在不冲突的情况下，本公开实施例中的实施例及实施例中的特征可以 相互组合。
压缩机100作为制冷系统中的关键构件，在其轴承-转子110系统的支撑组件在采用气悬浮轴承的情况下无需采用润滑油进行润滑，避免了润滑油和空调系统中的冷媒混合，防止润滑油沉积于蒸发器或冷凝器的换热管管壁，影响换热效率。为了保证压缩机100的稳定运行，需要外置的供气装置持续稳定地向气悬浮轴承供气。同时转子110会由于供气不稳定或者外力作用等原因发生轴向窜动和径向偏移，进而导致轴承-转子110系统失衡严重影响压缩机100的使用寿命。
结合图1-10所示，本公开实施例提供了一种压缩机100，包括转子110和调节组件。其中，转子110包括中间轴身111和两个端部轴身112；两个端部轴身112分别设置于中间轴身111的两端，且端部轴身112的直径小于中间轴身111的直径；调节组件包括轴向调节部，轴向调节部包括两个气浮轴向轴承200；两个气浮轴向轴承200分别套设于两个端部轴身112，且分别靠近中间轴身111的两端；其中，两个气浮轴向轴承200用以平衡转子110的轴向偏移。
采用本公开实施例提供的压缩机100，中间轴身111的直径大于端部轴身112的直径形成中间粗两端细的轴身设计，并且两个气浮轴向轴承200分别套设在两个端部轴身112上用以平衡转子110的轴向偏移。这样无需在转子110的轴身上设置推力盘，减轻了转子110的负载，减短了转子110的长度，优化了轴承-转子110系统的布局，进而有效提升了转子110的临界速度。
在一些实施例中，压缩机100内具有电机腔130，电机腔130内设有定子120且以定子120为界限，位于定子120前方的端部轴身112成为前端轴身，位于定子120后方的端部轴身112称为后端轴身。两个气浮轴向轴承200分别套设于两个端部轴身112，其中套设于前端轴身的称为前气浮轴向轴承，其中套设于后端轴身的称为后气浮轴向轴承。
可选地，压缩机100还包括安装组件，安装组件包括两个轴承支座210。两个轴承支座210用于安装两个气浮轴向轴承200，其中安装前气浮轴向轴承的称为前轴承支座，安装后气浮轴向轴承的称为后轴承支座。如图6所示，每一轴承支座210上开设有第一流道300，外部供给设备通过第一流道300向对应的气浮轴向轴承200供气。
进一步地，可选地，两个轴承支座210相对的一侧开设有容纳空间，中间轴身111分别连接前端轴身和后端轴身的部分设置于容纳空间内。通过轴承支座210在一定程度上限定了中间轴身111的径向位移，提高了转子110的稳定性。
在一些实施例中，轴向调节部还包括轴向监测装置、流量调节装置和第一控制器。其中，轴向监测装置用以监测转子110的轴向偏移量；流量调节装置用以调节两个气浮轴向 轴承200的供气量；第一控制器电连接于轴向监测装置和流量调节装置，用以根据轴向偏移量控制流量调节装置。
可选地，如图3所示，轴向监测装置包括一个或多个位移传感器201。中间轴身111靠近后端轴身的部分套设有标识圆环113，标识圆环113位于电机腔130内且位于后轴承支座的前方；位移传感器201对应标识圆环113的位置设置在后轴承支座朝向电机腔130的侧壁上。当转子110发生轴向偏移时，标识圆环113同步移动，标识圆环113发生的轴向偏移量也即转子110的轴向偏移量。电机腔130内的空间较大，通过设置标识圆环113和位移传感器201能够灵敏地检测到转子110的轴向位移。标识圆环113采用轻盈的材料制作且直径略大于中间轴身111的直径，减小标识圆环113对转子110的临界速度的影响。
进一步地，可选地，轴向偏移方向包括前偏向和后偏向。当标识圆环113和后轴承座之间的间隙变小时，转子110发生后偏向；当标识圆环113和后轴承座之间的间隙变大时，转子110发生前偏向。
可选地，流量调节装置包括两个分别设置于两个第一流道300内的第一电磁阀。通过改变第一电磁阀的开度调节对应的气浮轴向轴承200的供气量，进而调节气浮轴向轴承200的压力，从而平衡转子110在不同轴向偏移方向发生的偏移。当转子110发生前偏移时，增大前气浮轴向轴承的供气量，减小后气浮轴向轴承的供气量；当转子110发生后偏移时，增大后气浮轴向轴承的供气量，减小前气浮轴向轴承的供气量。
示例性地，为了说明轴向调节部的工作过程，将转子110的轴向偏移量记为a。在轴承-转子110系统稳定的情况下，将此时的a记为0，该状态下两个第一电磁阀均以45°的开度向对应的气浮轴向轴承200正常供气。转子110发生前偏向时，a大于零；转子110发生后偏向时，a小于零。
在轴承-转子110系统发生轴向偏移的情况下：
若a>0，转子110发生前偏向，此时第一控制器控制前气浮轴向轴承对应的第一电磁阀以90°的开度供气，并控制后气浮轴向轴承对应的第一电磁阀以20°的开度供气。从而增大前气浮轴向轴承施加在中间轴身111上的压力，减小后气浮轴向轴承施加在中间轴身111上的压力，快速平衡转子110在前偏向上产生的轴向力。
若a<0，转子110发生后偏向，此时第一控制器控制前气浮轴向轴承对应的第一电磁阀以20°的开度供气，并控制后气浮轴向轴承对应的第一电磁阀以90°的开度供气。从而增大后气浮轴向轴承施加在中间轴身111上的压力，减小前气浮轴向轴承施加在中间轴身111上的压力，快速平衡转子110在后偏向上产生的轴向力。
在一些实施例中，如图5和图6所示，每一轴承支座210设有一均压组件，均压组件 包括环绕轴承支座210设置的均压槽211；第一流道300的一端连通于均压槽211的底部，另一端连通于气浮轴向轴承200；外部供给装置向均压槽211内供给润滑介质。压缩机100的机壳140被构造为筒体形，轴承支座210安装在机壳140内后，均压槽211的槽口抵靠于机壳140的内表面。均压槽211和机壳140的内表面围限构成介质环道。机壳140的上方开设有第三流道320，第三流道320的一端连通于外部供给装置，另一端连通于均压槽211。外部供给装置通过第三流道320向均压槽211内供给润滑介质，润滑介质充满介质环道后，打开第一流道300对应的第一电磁阀向气浮轴向轴承200供给润滑介质。这里润滑介质包括气态冷媒或者气液混合冷媒。
受限于外部供给装置自身的性能以及气体介质或气液混合介质的不稳定性质、介质在管路中的压力损失等因素，如果外部供给装置通过第三流道320直接向第一流道300供给气体后，进入气浮轴向轴承200的润滑介质极不稳定，严重影响气浮轴向轴承200平衡轴向力的作用。通过均压槽211设计，外部供给装置首先通过第三流道320将润滑介质供给至均压槽211，均压槽211给润滑介质提供了缓冲空间，随着润滑介质在均压槽211内流动其自身发生热交换后压力和温度逐渐均匀。均匀后的润滑介质再供给至气浮轴向轴承200，保证了气浮轴向轴承200内润滑介质的稳定性。
可选地，均压组件还包括多个加热电阻，多个加热电阻环绕均压槽211设置，每一加热电阻均可单独控制。例如将均压槽211四等分，每一等分区域内设置一加热电阻和温度传感器。当某一等分区域内的温度传感器监测到本区域内的润滑介质的温度低于四个等分区域内的温度传感器监测到的温度平均值时，启动该等分区域内的加热电阻，从而快速平衡均压槽211内的润滑介质温度和压力。
可选地，如图7所示，每一轴承支座210还设有一密封组件，密封组件包括两个密封圈212，两个密封圈212套设于轴承支座210且分别位于均压槽211的两侧，用以密封均压槽211两侧的间隙。环绕轴承支座210设置有前密封环槽和后密封环槽，其中前密封槽位于均压槽211的前方，后密封槽位于均压槽211的后方。两个密封圈212分别套设于前密封环槽和后密封环槽，当轴承支座210安装在机壳140内后，起到密封均压槽211前后两侧和机壳140之间的间隙的作用，防止润滑介质泄露、保障均压槽211内的压力。
在一些实施例中，如图1和图2所示，压缩机100的支撑组件包括两个气浮径向轴承230，两个气浮径向轴承230分别套设于两个端部轴身112以支撑转子110，且分别安装于两个轴承支座210内。其中，每一气浮径向轴承230位于一个气浮轴向轴承200远离另一个气浮轴向轴承200的一侧。
可选地，如图6所示，每一轴承支座210设置有一个第二流道310。第二流道310的 一端连通于均压槽211的底部，另一端连通于对应的气浮径向轴承230。外部供给装置首先通过第三流道320将润滑介质供给至均压槽211，润滑介质在均压槽211内得到缓冲，随着润滑介质在均压槽211内流动其压力和温度逐渐均匀，均匀后的润滑介质流向气浮径向轴承230。无需增设外部供给装置单独向气浮径向轴承230供给润滑介质，采用一套外部供给装置向均压槽211内供给润滑介质，再将润滑介质通过不同的流道通入气浮轴向轴承200和气浮径向轴承230，简化了压缩机100的结构。
进一步地，可选地，每一第二流道310内设有一个第二电磁阀，通过改变第二电磁阀的开度调节对应的气浮径向轴承230的供气量。
更进一步地，可选地，第一流道300的直径记为d1，第二流道310的直径记为d2，第三流道320的直径记为d3。为了满足供气需求，三条流道的直径设置满足d32>d12+d22。
在一些实施例中，如图8和图9所示，每一轴承支座210还设有一轴端盖220；调节组件还包括径向调节部，径向调节部包括多条辅助气道221；多条辅助气道221环绕轴端盖220设置，且每一辅助气道221对应转子110的一个或多个径向偏移方向；其中，每一辅助气道221均连通于端部轴身112和气浮径向轴承230之间的间隙，以向该间隙供气从而平衡转子110。
可选地，轴端盖220的中心设有内孔，气浮轴向轴承200和气浮径向轴承230依次套设于端部轴身112上后安装于对应的轴承支座210内，再将轴端盖220安装于轴承支座210的远离电机腔130的一侧。两个端部轴身112分别通过对应端的轴端盖220的内孔向外伸出，用以安装叶轮等构件。
进一步地，可选地，如图10所示，转子110的径向偏移方向至少包括上偏向、下偏向、左偏向和右偏向。4个辅助气道221分别对应上偏向、下偏向、左偏向和右偏向环绕轴端盖220的内孔设置，上辅助气道221对应上偏向，下辅助气道221对应下偏向，左辅助气道221对应左偏向，右辅助气道221对应右偏向。其中，上辅助气道221用于向转子110的上偏向供气，从而在上偏向承托转子110；下辅助气道221用于向转子110的下偏向供气，从而在下偏向承托转子110；左辅助气道221用于向转子110的左偏向供气，从而在左偏向承托转子110；右辅助气道221用于向转子110的右偏向供气，从而在右偏向承托转子110。当转子110在某一径向方向发生偏移时，开启该径向偏移方向对应的辅助气道221，进而在该径向偏移方向上承托转子110，从而平衡转子110。
更进一步地，可选地，每一辅助气道221设有一第三电磁阀。当转子110在某一径向偏移方向上出现较大的偏移量时，增大电磁阀的开度进而增大对应的辅助气道221的供气量，从而增大该径向偏移方向的承托力以快速平衡转子110。
更进一步地，可选地，如图9所示，轴承支座210上开设有第四流道330。第四流道330的一端连通于均压槽211的侧面槽壁，另一端连通于辅助气道221的进口。辅助气道221的出口连通于端部轴身112和气浮径向轴承230之间的间隙。润滑介质在均压槽211的作用下其温度和压力均匀后，通过第四流道330供给至辅助气道221。采用均压槽211分别向气浮径向轴承230和辅助气道221供给润滑介质，保证了分别从气浮径向轴承230和辅助气道221进入该间隙的气体的一致性，避免两种不同温度和不同压力的气体在该间隙内热交换，影响间隙内气体的稳定性。外部供给装置将润滑介质供给至均压槽211后，再通过合理的流道设计将润滑介质分别供给至用于承托转子110的气浮径向轴承230、用于调节转子110轴向偏移的气浮轴向轴承200和用于调节转子110径向偏移的辅助气道221，整体结构布局合理且紧凑，简化了压缩机100的结构。
本公开实施例还提供了一种制冷系统，包括上述任一实施例所描述的压缩机100。制冷系统还包括供气罐，供气罐连通于第三流道320。供气罐通过第三流道320向均压槽211内供给气态冷媒或者气液混合冷媒，均压槽211内的气态冷媒或者气液混合冷媒的压力和温度平衡后，通过第一流道300供给至气浮轴向轴承200，通过第二流道310供给至气浮径向轴承230成，通过第四流道330供给至辅助气道221。
可选地，制冷系统还包括蒸发器。机壳140的底部分别设有冷却入口和回气口，冷媒通过冷却入口通入机壳内和定子120热交换将其冷却，吸收热量变为中温中压的气态冷媒从回气口排入蒸发器。
以上描述和附图充分地示出了本公开的实施例，以使本领域的技术人员能够实践它们。其他实施例可以包括结构的以及其他的改变。实施例仅代表可能的变化。除非明确要求，否则单独的部件和功能是可选的，并且操作的顺序可以变化。一些实施例的部分和特征可以被包括在或替换其他实施例的部分和特征。本公开的实施例并不局限于上面已经描述并在附图中示出的结构，并且可以在不脱离其范围进行各种修改和改变。本公开的范围仅由所附的权利要求来限制。

Claims (10)

  1. 一种压缩机，其特征在于，包括：
    转子(110)，包括中间轴身(111)和两个端部轴身(112)；两个所述端部轴身(112)分别设置于所述中间轴身(111)的两端，且所述端部轴身(112)的直径小于所述中间轴身(111)的直径；
    调节组件，包括轴向调节部，所述轴向调节部包括两个气浮轴向轴承(200)；两个所述气浮轴向轴承(200)分别套设于两个所述端部轴身(112)，且分别靠近所述中间轴身(111)的两端；
    其中，两个所述气浮轴向轴承(200)用以平衡所述转子(110)的轴向偏移。
  2. 根据权利要求1所述的压缩机，其特征在于，所述轴向调节部还包括：
    轴向监测装置，用以监测所述转子(110)的轴向偏移量；
    流量调节装置，用以调节两个所述气浮轴向轴承(200)的供气量；
    第一控制器，电连接于所述轴向监测装置和所述流量调节装置，用以根据所述轴向偏移量控制所述流量调节装置。
  3. 根据权利要求2所述的压缩机，其特征在于，所述中间轴身(111)上套设有标识圆环(113)；
    所述轴向监测装置包括：
    一个或多个位移传感器(201)，用于监测所述标识圆环(113)的轴向偏移量。
  4. 根据权利要求1至3任一项所述的压缩机，其特征在于，还包括：
    安装组件，包括两个轴承支座(210)；两个所述轴承支座(210)分别用以安装两个所述气浮轴向轴承(200)，且每一所述轴承支座(210)上设有一个第一流道(300)，用以向对应的所述气浮轴向轴承(200)供给润滑介质。
  5. 根据权利要求4所述的压缩机，其特征在于，每一所述轴承支座(210)设有一均压组件，所述均压组件包括：
    均压槽(211)，环绕所述轴承支座(210)设置；所述第一流道(300)的一端连通于所述均压槽(211)的底部，另一端连通于气浮轴向轴承(200)；
    外部供给装置向均压槽(211)内供给润滑介质。
  6. 根据权利要求5所述的压缩机，其特征在于，每一所述轴承支座(210)还设有一密封组件，所述密封组件包括：
    两个密封圈(212)，套设于所述轴承支座(210)且分别位于所述均压槽(211)的两侧，用以密封所述均压槽(211)两侧的间隙。
  7. 根据权利要求5或6所述的压缩机，其特征在于，还包括：
    支撑组件，包括两个气浮径向轴承(230)；两个所述气浮径向轴承(230)分别套设于两个所述端部轴身(112)以支撑所述转子(110)，且每一所述气浮径向轴承(230)位于一个所述气浮轴向轴承(200)远离另一个所述气浮轴向轴承(200)的一侧。
  8. 根据权利要求7所述的压缩机，其特征在于，两个所述气浮径向轴承(230)分别安装于两个所述轴承支座(210)内，且每一所述轴承支座(210)上设有一个第二流道(310)；
    所述第二流道(310)的一端连通于所述均压槽(211)的底部，另一端连通于对应的所述气浮径向轴承(230)，用以向对应的所述气浮径向轴承(230)供给润滑介质。
  9. 根据权利要求7所述的压缩机，其特征在于，每一所述轴承支座(210)还设有一轴端盖(220)；
    所述调节组件还包括：
    径向调节部，包括多条辅助气道(221)；所述多条辅助气道(221)环绕所述轴端盖(220)设置，且每一所述辅助气道(221)对应所述转子(110)的一个或多个径向偏移方向；
    其中，每一所述辅助气道(221)均连通于所述端部轴身(112)和所述气浮径向轴承(230)之间的间隙，以向所述间隙供气从而平衡所述转子(110)的径向偏移。
  10. 一种制冷系统，其特征在于，包括如权利要求1至9任一项所述的压缩机。
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