WO2024104238A1 - 一种用于制冷系统的磁悬浮电机密封-冷却装置及方法 - Google Patents

一种用于制冷系统的磁悬浮电机密封-冷却装置及方法 Download PDF

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Publication number
WO2024104238A1
WO2024104238A1 PCT/CN2023/130575 CN2023130575W WO2024104238A1 WO 2024104238 A1 WO2024104238 A1 WO 2024104238A1 CN 2023130575 W CN2023130575 W CN 2023130575W WO 2024104238 A1 WO2024104238 A1 WO 2024104238A1
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WIPO (PCT)
Prior art keywords
magnetic levitation
stage compressor
cooling
sealing
motor
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/CN2023/130575
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English (en)
French (fr)
Inventor
张严
金圻烨
冯静娅
汪娉婷
鲍宇
李晓波
李悦
涂世恩
冀青鹏
陈伟
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Shanghai Marine Diesel Engine Research Institute
Original Assignee
Shanghai Marine Diesel Engine Research Institute
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Filing date
Publication date
Application filed by Shanghai Marine Diesel Engine Research Institute filed Critical Shanghai Marine Diesel Engine Research Institute
Priority to US19/130,169 priority Critical patent/US20260012061A1/en
Priority to EP23890674.7A priority patent/EP4622074A4/en
Priority to KR1020257019728A priority patent/KR102930071B1/ko
Publication of WO2024104238A1 publication Critical patent/WO2024104238A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/10—Arrangements for cooling or ventilating by gaseous cooling medium flowing in closed circuit, a part of which is external to the machine casing
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/19—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil
    • 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
    • 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
    • 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
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/102—Shaft 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • 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
    • H02K5/12—Casings or enclosures characterised by the shape, form or construction thereof specially adapted for operating in liquid or gas
    • 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
    • H02K5/20—Casings or enclosures characterised by the shape, form or construction thereof with channels or ducts for flow of cooling medium
    • H02K5/207—Casings or enclosures characterised by the shape, form or construction thereof with channels or ducts for flow of cooling medium with openings in the casing specially adapted for ambient air
    • 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
    • F04D29/058—Bearings magnetic; electromagnetic

Definitions

  • the present invention belongs to the field of magnetic levitation motors, and specifically, relates to a magnetic levitation motor sealing-cooling device and method for a refrigeration system.
  • CN108895025A discloses a blower shaft end seal that can balance part of the axial force. In addition to balancing the axial force, its main function is to provide a good shaft end seal.
  • this invention cannot completely solve the problem of low-temperature fluid leakage threatening the safety of the motor.
  • the impeller back has a stepped design, which is prone to scratches when rotating at high speeds.
  • CN112583185A discloses a sealing structure for a magnetic levitation motor and a magnetic levitation motor.
  • the motor seal is formed by introducing nitrogen through structural sealing to form a positive pressure.
  • the introduced high-pressure nitrogen will form a counterflow disturbance with the working fluid in the volute, which will reduce the aerodynamic performance of the fluid machinery to a certain extent.
  • the sealing design structure is relatively complex and has many internal parts.
  • CN112833103A discloses a magnetic levitation sealed bearing, in which magnetic fluid is filled between the gaps between the inner and outer ring grooves corresponding to the stator and rotor, and the magnetic fluid is gathered in the grooves through the magnetic pole action of the permanent magnet to form a sealing belt.
  • the magnetic fluid sealing method disclosed in this invention has high requirements for the magnetic fluid and the additional permanent magnets. If it is used to seal low-temperature working fluids, the influence of low temperature makes it difficult to ensure the sealing performance.
  • the design of the third permanent magnet will affect the magnetic field of the magnetic levitation bearing to a certain extent, and the entire sealing structure is also relatively complicated.
  • CN112096467A discloses a cooling system and method for a magnetic levitation motor applied to an organic Rankine cycle, which uses the working fluid of an organic Rankine cycle unit to cool the magnetic levitation motor, thereby improving the system's performance and power generation efficiency.
  • This cooling method completely relies on the working fluid of the circulation system to cool the motor, and consumes a large amount of cooling gas. If used in a refrigeration system, the large consumption of refrigerant will reduce the system's refrigeration capacity.
  • the present invention provides a magnetic levitation motor sealing-cooling device and cooling method for a refrigeration system, which is convenient for matching the cooling gas pressure, making full use of the cooling gas, and reducing the consumption of the cooling gas.
  • the low-temperature working fluid at the expansion end is prevented from leaking into the interior of the motor, fully ensuring the stable and safe operation of the motor.
  • the motor can also be fully cooled by combining air cooling and water cooling.
  • a magnetic levitation motor sealing-cooling device for a refrigeration system comprises a magnetic levitation first-stage compressor, a magnetic levitation second-stage compressor, a magnetic levitation expander, a main heat exchanger and a cooling gas regulating valve; the magnetic levitation first-stage compressor and the magnetic levitation expander are coaxially arranged, and the magnetic levitation first-stage compressor, the magnetic levitation second-stage compressor, the magnetic levitation expander and the main heat exchanger are connected in sequence; the cooling gas in the magnetic levitation motor cavity of the magnetic levitation second-stage compressor is taken from the working fluid cooled at the outlet of the magnetic levitation first-stage compressor; the cooling gas in the magnetic levitation motor cavity of the magnetic levitation first-stage compressor is taken from the cooling gas at the outlet of the magnetic levitation motor cavity of the magnetic levitation second-stage compressor, and the flow rate and pressure are adjusted by the cooling gas regulating valve to be slightly lower than the working fluid pressure at the wheel back of the magnetic levit
  • the magnetic levitation motor of the magnetic levitation first-stage compressor and the magnetic levitation second-stage compressor is cooled by a combination of air cooling and water cooling; the magnetic levitation motor casing of the magnetic levitation first-stage compressor and the magnetic levitation second-stage compressor is provided with a cooling water loop.
  • the cooling water flows into the cooling water loop of the motor casing, it flows circumferentially and axially along the motor casing.
  • the magnetic levitation first-stage compressor, the magnetic levitation second-stage compressor and the magnetic levitation expander are respectively provided with a wheel back sealing structure and a shaft sealing structure.
  • the wheel back sealing structure is arranged in the gap between the impeller and the wheel back, including impeller sealing teeth and wheel back sealing teeth, which form a labyrinth-like structure.
  • the shaft sealing structure is arranged at the shaft end of the magnetic levitation motor, including stator sealing teeth at the shaft end and rotor sealing teeth at the shaft end, which form a labyrinth-staggered structure.
  • short sealing teeth are arranged between adjacent wheel back sealing teeth, and the short sealing teeth are arranged opposite to the top ends of the impeller sealing teeth; short sealing teeth are arranged between adjacent shaft end stator sealing teeth, and the short sealing teeth are arranged opposite to the top ends of the shaft end rotor sealing teeth.
  • sealing gas regulating valve As sealing gas.
  • a sealing gas through hole is opened at the shaft end of the magnetic levitation expander for introducing sealing gas.
  • the pressure and flow of the sealing gas are adjusted by the sealing gas regulating valve.
  • the pressure of the sealing gas is adjusted to be equivalent to the pressure at the back of the expander wheel.
  • a first cooler is provided downstream of the outlet of the magnetic levitation motor cavity of the suspended second-stage compressor. Part of the cooling gas cooled by the second cooler is led to the magnetic levitation motor cavity of the magnetic levitation first-stage compressor, and the other part is led to the upstream pipeline of the working medium inlet of the magnetic levitation first-stage compressor.
  • a second cooler is provided downstream of the outlet of the magnetic levitation motor cavity of the magnetic levitation first-stage compressor, and the cooling gas cooled by the second cooler is led to the upstream pipeline of the working medium inlet of the magnetic levitation first-stage compressor through a pipeline.
  • a cooling method for a magnetic levitation motor sealing-cooling device for a refrigeration system which comprises the following steps: introducing a portion of the cooled working fluid at the outlet of a magnetic levitation first-stage compressor as cooling gas into the magnetic levitation motor cavity of a magnetic levitation second-stage compressor through a pipeline to cool the magnetic levitation motor of the magnetic levitation second-stage compressor; a portion of the cooling gas downstream of the outlet of the magnetic levitation motor cavity of the magnetic levitation second-stage compressor is led to the magnetic levitation motor cavity of the magnetic levitation first-stage compressor to cool the magnetic levitation motor of the magnetic levitation first-stage compressor, and the other portion is led to the upstream pipeline of the working fluid inlet of the magnetic levitation first-stage compressor to re-enter the circulation of the magnetic levitation first-stage compressor; the cooling gas downstream of the outlet of the magnetic levitation motor cavity of the magnetic levitation first-stage compressor is led to the upstream pipeline of the working fluid inlet of the magnetic levit
  • a portion of the cooled working fluid at the outlet of the first-stage magnetic levitation compressor is introduced into the cavity of the magnetic levitation motor of the second-stage magnetic levitation compressor as cooling gas; a portion of the cooling gas downstream of the cavity outlet of the magnetic levitation motor of the second-stage magnetic levitation compressor is introduced into the cavity of the magnetic levitation motor of the first-stage magnetic levitation compressor to facilitate matching of the cooling gas pressure and fully utilize the cooling gas to reduce the consumption of cooling gas.
  • the motor adopts a combination of air cooling and water cooling.
  • the heat generated by the motor rotor is fully removed by air cooling, and the heat of the motor stator is fully removed by the design of the water cooling loop.
  • the consumption of cooling gas is effectively reduced, that is, the additional consumption of the system refrigerant, ensuring the cooling capacity of the system.
  • sealing and cooling Through the design of sealing and cooling, the temperature and pressure coordination of sealing gas and cooling gas is achieved.
  • the two complement each other and are inseparable, forming a synergistic solution for motor sealing and cooling.
  • the combination of the wheel back seal and the shaft seal and the staggered design of the sealing structure greatly reduce the leakage of the working fluid at the wheel back of the first and second stage compressors, ensuring the refrigeration capacity of the system.
  • the temperature and pressure coordination of the sealing gas and the cooling gas are achieved through the design of sealing and cooling.
  • the two complement each other to form a synergistic solution for motor sealing and cooling.
  • Figure 1 is the overall process flow chart of the refrigeration system
  • Figure 2 is a schematic diagram of the sealing and cooling synergistic solution for the magnetic levitation first-stage compressor-magnetic levitation expander
  • Figure 3 is a schematic diagram of the sealing and cooling synergistic solution for the magnetically suspended two-stage compressor
  • Figure 4 is a schematic diagram of the cooling water loop
  • Figure 5 is a schematic diagram of another implementation scheme of the sealing structure.
  • the magnetic levitation motor sealing-cooling device for a refrigeration system of the present invention is shown in Figure 1.
  • the refrigeration system includes a magnetic levitation first-stage compressor 1, a magnetic levitation second-stage compressor 2, a magnetic levitation expander 3, a main heat exchanger 4, a regenerator 5, a first aftercooler 61, a second aftercooler 62, a first cooler 71, a second cooler 72, a sealing gas regulating valve 8 and a cooling gas regulating valve 9.
  • the magnetic levitation first-stage compressor 1 and the magnetic levitation expander 3 are coaxially arranged, and the magnetic levitation first-stage compressor 1, the magnetic levitation second-stage compressor 2, the regenerator 5, the magnetic levitation expander 3 and the main heat exchanger 4 are connected in sequence.
  • the working fluid outlet of the magnetic levitation first-stage compressor 1 is connected to the working fluid inlet of the magnetic levitation second-stage compressor 2 via the first working fluid pipeline S1, the first aftercooler 61 and the second working fluid pipeline S2 in sequence;
  • the working fluid outlet of the magnetic levitation second-stage compressor 2 is connected to the working fluid inlet of the magnetic levitation expander 3 via the third working fluid pipeline S3, the second aftercooler 62, the fourth working fluid pipeline S4, the regenerator 5 and the fifth working fluid pipeline S5 in sequence;
  • the working fluid outlet of the magnetic levitation expander 3 is connected to the working fluid inlet of the magnetic levitation first-stage compressor 1 via the sixth working fluid pipeline S6, the main heat exchanger 4 and the seventh working fluid pipeline S7 in sequence.
  • the refrigeration system can adopt a closed cycle.
  • the specific process is: the refrigerant enters the magnetic suspension first-stage compressor 1 and is compressed, and the first aftercooler 61 cools the compressor outlet refrigerant; the cooled refrigerant enters the second-stage compressor 2 for compression, and then passes through the second aftercooler 62 for cooling, and the cooled refrigerant enters the regenerator 5 for pre-cooling, and then the refrigerant enters the magnetic suspension expander 3 to expand and do work, recovering part of the power; the expanded refrigerant enters the main heat exchanger 4 to provide cooling to the outside world, and the refrigerant still has a certain amount of cooling after passing through the main heat exchanger 4, and enters the regenerator 5 to pre-cool the refrigerant compressed by the second-stage compressor 2, and the refrigerant at the outlet of the regenerator enters the first-stage compressor to complete the closed cycle.
  • the magnetic levitation motor cavity of the magnetic levitation first-stage compressor 1 and the magnetic levitation second-stage compressor 2 is filled with cooling air.
  • the cooling air pressure In order to prevent the cooling air from flowing back to the back of the impeller, the cooling air pressure must be lower than the working fluid pressure at the back of the impeller.
  • the cooling gas in the magnetic levitation motor cavity of the magnetic levitation secondary compressor 2 is taken from the working fluid cooled at the outlet of the primary compressor.
  • the cooling gas inlet of the magnetic levitation motor cavity of the magnetic levitation secondary compressor 2 is connected to the second working fluid pipeline S2 via the ninth working fluid pipeline S9, which is used to introduce the working fluid cooled at the outlet of the primary compressor into the magnetic levitation motor cavity of the magnetic levitation secondary compressor 2.
  • the cooling gas outlet of the magnetic levitation motor cavity of the magnetic levitation secondary compressor 2 is connected to the seventh working fluid pipeline S7 via the tenth working fluid pipeline S10, the first cooler 71, the eleventh working fluid pipeline S11, and the thirteenth working fluid pipeline S13; the cooling gas inlet of the magnetic levitation motor cavity of the magnetic levitation primary compressor 1 is connected to between the eleventh working fluid pipeline S11 and the thirteenth working fluid pipeline S13 via the twelfth working fluid pipeline S12 and the cooling gas regulating valve 9; the cooling gas outlet of the magnetic levitation motor cavity of the magnetic levitation primary compressor 1 is connected to the seventh working fluid pipeline S7 via the fourteenth working fluid pipeline S14 and the second cooler 72.
  • the sealing gas inlet of the magnetic suspension motor cavity of the magnetic suspension first-stage compressor 1 is connected to the fourth working medium pipeline S4 through the eighth working medium pipeline S8 and the sealing gas regulating valve 8.
  • the pressure of the cooling gas in the magnetic levitation motor cavity of the magnetic levitation first-stage compressor 1 and the magnetic levitation second-stage compressor 2 can be made lower than the working medium pressure at the back of the impeller, which effectively prevents the cooling gas from flowing back to the back of the impeller.
  • the magnetic levitation motor casing of the magnetic levitation first-stage compressor 1 and the magnetic levitation second-stage compressor 2 is also provided with a cooling water loop, and the cooling water cools the magnetic levitation motor through the motor casing cooling water loop.
  • the cooling method of the motor of the magnetic levitation two-stage compressor 2 is as follows: the outlet working fluid of the first-stage compressor 1 is cooled by the first aftercooler 61 (preferably, the temperature after cooling can be set to about 39°C, adjusted according to the actual supply cooling water temperature), and then enters the motor cavity of the magnetic levitation two-stage compressor 2 through the ninth working fluid pipeline S9, taking away the heat generated by the operation of the motor rotor.
  • the cooling water flows into the cooling water loop of the motor casing through the first cooling water pipeline S15, flows circumferentially and axially along the motor casing, and fully takes away the heat of the motor stator through the cooling water loop.
  • the cooling water is discharged from the pipeline at the motor casing through the second cooling water outlet pipeline S16.
  • the cooling water is discharged from the pipeline at the motor casing through the second cooling water outlet pipeline S16.
  • the cooling method of the magnetic suspension first-stage compressor 1 is as follows: the cooler at the cooling gas outlet of the magnetic suspension second-stage compressor 2 is cooled by the first cooler 71, and then introduced into the motor cavity of the magnetic suspension first-stage compressor 1 through the twelfth working fluid pipeline S12 as cooling gas.
  • the flow rate and pressure of the cooling gas in the twelfth working fluid pipeline S12 are adjusted by the cooling gas regulating valve 9 to be slightly lower than the working fluid pressure at the back of the magnetic suspension first-stage compressor 1, and then flow into the motor cavity of the magnetic suspension first-stage compressor 1; the excess cooling gas can be led out to the seventh working fluid pipeline S7 through the thirteenth working fluid pipeline S13.
  • the cooling gas entering the motor cavity of the magnetic suspension first-stage compressor 1 fully cools the motor rotor M37 and is discharged from the motor housing.
  • the cooling gas with the heat of the motor is cooled by the fourteenth working fluid pipeline S14 and the second cooler 72, and then re-enters the seventh working fluid pipeline S7 to enter the magnetic suspension first-stage compressor 1 for circulation.
  • the water cooling method of the magnetic suspension first-stage compressor 1 is the same as that of the magnetic suspension second-stage compressor 2, and will not be repeated.
  • the third embodiment is the third embodiment.
  • the sealing method of the magnetic levitation two-stage compressor 2 is as follows: in the gap between the impeller M21 and the wheel back of the secondary compressor, impeller sealing teeth M23 and wheel back sealing teeth M22 are arranged, and the two form a labyrinth-staggered structure; at the shaft end, shaft end stator sealing teeth M24 and shaft end rotor sealing teeth M25 are arranged, and the two form a labyrinth-staggered structure. Due to the pressure difference between the working fluid at the outlet of the impeller M21 and the cooling air in the motor cavity, a small amount of leakage will occur at the impeller wheel back.
  • the two-way labyrinth-staggered structure design on the wheel back and the shaft end and the flow dead zone formed between the two sealing structures will greatly reduce the leakage of the working fluid and ensure the cooling capacity of the system. A small amount of leaked working fluid will merge with the cooling air in the motor cavity into one path and be discharged through the tenth working fluid pipeline S10.
  • the sealing method of the magnetic levitation first-stage compressor 1 is similar to that of the magnetic levitation second-stage compressor 2. Due to the pressure difference between the working fluid at the back of the first-stage compressor impeller and the cooling air in the motor cavity of the integrated machine, a small amount of leakage will occur.
  • the labyrinth staggered sealing design between the wheel back and the shaft end and the flow dead zone formed between the two sealing structures will greatly reduce the leakage of the working fluid, reduce the consumption of circulating working fluid in the system, and ensure the refrigeration capacity of the system. A small amount of leaked working fluid will be discharged through the fourteenth working fluid pipeline S14.
  • FIG. 5 Another embodiment of the wheel back and shaft end sealing structure of the magnetic levitation first-stage compressor 1, the magnetic levitation second-stage compressor 2, and the magnetic levitation expander 3 is shown in Figure 5.
  • Short sealing teeth are arranged between adjacent wheel back sealing teeth, and the short sealing teeth are arranged opposite to the top of the impeller sealing teeth; short sealing teeth are arranged between adjacent shaft end stator sealing teeth, and the short sealing teeth are arranged opposite to the top of the shaft end rotor sealing teeth.
  • the specific sealing method is: after the outlet working fluid of the magnetic levitation secondary compressor 2 is cooled by the second aftercooler 62 (preferably, the temperature after cooling can be set to about 39°C, adjusted according to the actual supply cooling water temperature), it is drained through the 8th working fluid pipeline as the sealing gas of the magnetic levitation expander 3. In order to prevent the sealing gas from flowing back to the back of the expander impeller M31, its pressure and flow are adjusted by the sealing gas regulating valve 8.
  • the wheel back sealing teeth M32 and the impeller sealing teeth M33 are arranged, and the two form a labyrinth staggered structure; at the shaft end of the magnetic levitation expander 3, the shaft end stator sealing teeth M34 and the shaft end rotor sealing teeth M35 are arranged, and the two form a labyrinth staggered structure.
  • a sealing gas through hole M36 is opened at the shaft end to introduce sealing gas, and its pressure is adjusted to be equivalent to the pressure at the back of the wheel through the sealing gas regulating valve.
  • the dead zone between the wheel back seal and the shaft end seal will consume the dynamic pressure formed by the working fluid at the wheel back as the impeller rotates. Therefore, the working fluid and the sealing gas at the entrance of the expander wheel back gap will establish a balanced pressure field, preventing the low-temperature working fluid at the wheel back from leaking into the motor cavity and threatening the safe operation of the motor. At the same time, due to the pressure difference between the sealing gas and the cooling gas in the motor cavity, a small amount of leakage will occur. The design of the staggered sealing teeth at the shaft end will greatly reduce the leakage of this part, and the temperature of the sealing gas will not affect the safe operation of the motor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

一种用于制冷系统的磁悬浮电机密封-冷却装置及方法，磁悬浮一级压缩机（1）、磁悬浮二级压缩机（2）的磁悬浮电机采用风冷与水冷结合的方式冷却；磁悬浮二级压缩机（2）的冷却气取自磁悬浮一级压缩机（1）出口冷却后的工质；磁悬浮一级压缩机（1）的冷却气取自磁悬浮二级压缩机（2）的磁悬浮电机腔体出口的冷却气；磁悬浮一级压缩机（1）和磁悬浮二级压缩机（2）的磁悬浮电机机壳设置有冷却水环路。磁悬浮一级压缩机（1）、磁悬浮二级压缩机（2）、磁悬浮膨胀机（3）分别设置有轮背密封结构与轴封结构；磁悬浮二级压缩机（2）出口的一部分工质被引流至磁悬浮膨胀机（3）作为密封气。在保证电机冷却的同时，避免了低温工质泄漏进电机内部，保证了电机的稳定、安全运行。

Description

一种用于制冷系统的磁悬浮电机密封-冷却装置及方法 技术领域
 本发明属于磁悬浮电机领域，具体地，涉及一种用于制冷系统的磁悬浮电机密封-冷却装置及方法。
 背景技术
 压缩机与膨胀机是制冷系统中不可或缺的核心设备，使用磁悬浮电机驱动压缩机-膨胀机机组可有效提升系统性能，而磁悬浮电机的密封及冷却方式直接决定电机是否能够稳定安全运行。在制冷系统中，膨胀端的蜗壳入口气体可达到-160℃以下。若不采取密封处理，蜗壳入口的气体将通过叶轮与背板之间的间隙泄漏至电机腔体内，低温的介质将严重威胁到磁悬浮电机的安全。同时，在大功率磁悬浮电机运行过程中，需要通过冷却带走电机损耗产生的热量，否则也将影响电机的正常运行。
 现有磁悬浮电机密封与冷却的方式若应用于制冷系统中仍有一定技术壁垒。
 CN108895025A公布了一种可平衡部分轴向力的鼓风机轴端密封，其主要作用除平衡轴向力外，可起到较好的轴端密封作用。但该发明无法完全解决低温工质泄漏威胁电机安全的问题。此外，其叶轮轮背处有阶梯式设计，在高速旋转时，易产生刮擦。
 CN112583185A公布了一种磁悬浮电机用密封结构及磁悬浮电机。通过结构密封并通入氮气形成正压构成电机密封。通入的高压氮气将与蜗壳内工质形成逆流扰动，一定程度上会降低流体机械的气动性能。此外，该密封设计结构较为复杂，内部零件也较多。
 CN112833103A公布了一种磁悬浮密封轴承，在定转子所对应的内外环凹槽间隙之间填充磁流体，通过永磁体的磁极作用将其聚集在凹槽中以形成密封带。该发明公布的磁流体式密封法对所述的磁流体以及额外设置的永磁体要求较高，若用于密封低温工质，低温的影响使得密封性能难以保证。此外，第三永磁体的设计一定程度上将影响磁悬浮轴承的磁场，整个密封结构也较为复杂。
 CN112096467A公布了一种应用于有机朗肯循环的磁悬浮电机冷却系统及冷却方法，利用有机朗肯循环单元的工质完成磁悬浮电机的冷却，提升了系统的性能及发电效率。该冷却方式完全依靠循环系统的工质对电机进行冷却，对冷却气量消耗大，若应用于制冷系统中，对制冷工质的大量消耗将降低系统的制冷能力。
 发明内容
 为解决上述技术问题，本发明提供一种用于制冷系统的磁悬浮电机密封-冷却装置及冷却方法，便于匹配冷却气压力，对冷却气进行充分的利用，减小冷却气的消耗。此外，通过密封的设计，避免了膨胀端低温工质泄漏进电机内部，充分保证了电机的稳定、安全运行。还可以通过风冷与水冷的结合，实现了电机的充分冷却。
 本发明采用的技术方案为：
 一种用于制冷系统的磁悬浮电机密封-冷却装置，制冷系统包含磁悬浮一级压缩机、磁悬浮二级压缩机、磁悬浮膨胀机、主换热器和冷却气调节阀；磁悬浮一级压缩机、磁悬浮膨胀机同轴设置，磁悬浮一级压缩机、磁悬浮二级压缩机、磁悬浮膨胀机、主换热器依次连接；磁悬浮二级压缩机的磁悬浮电机腔体内的冷却气取自磁悬浮一级压缩机出口冷却后的工质；磁悬浮一级压缩机的磁悬浮电机腔体的冷却气取自磁悬浮二级压缩机的磁悬浮电机腔体出口的冷却气，并通过冷却气调节阀调整流量与压力，使其略低于磁悬浮一级压缩机轮背处工质压力。
 进一步，用于制冷系统的磁悬浮电机密封-冷却装置还包括第一后冷器、第二后冷器，第一后冷器、第二后冷器分别设置在磁悬浮一级压缩机、磁悬浮二级压缩机的下游，对压缩后的工质进行冷却。
 进一步，磁悬浮一级压缩机、磁悬浮二级压缩机的磁悬浮电机采用风冷与水冷结合的方式进行冷却；磁悬浮一级压缩机和磁悬浮二级压缩机的磁悬浮电机机壳设置有冷却水环路。
 进一步，冷却水流入电机机壳的冷却水环路后，沿电机机壳环向、轴向流动。
 进一步，磁悬浮一级压缩机、磁悬浮二级压缩机、磁悬浮膨胀机分别设置有轮背密封结构与轴封结构。
 进一步，轮背密封结构设置在叶轮与轮背间隙之中，包括叶轮密封齿与轮背密封齿，二者形成迷宫交错式结构。
 进一步，轴封结构设置在磁悬浮电机轴端，包括轴端定子密封齿与轴端转子密封齿，二者形成迷宫交错式结构。
 进一步，在相邻的轮背密封齿之间还设置有短密封齿，短密封齿与叶轮密封齿的顶端相对设置；在相邻的轴端定子密封齿之间设置有短密封齿，短密封齿与轴端转子密封齿的顶端相对设置。
 进一步，磁悬浮二级压缩机出口冷却后的一部分工质通过密封气调节阀被引流至磁悬浮膨胀机作为密封气，在磁悬浮膨胀机的轴端开有密封气通孔用于引入密封气，密封气的压力与流量通过密封气调节阀进行调整，密封气的压力被调整至与膨胀机轮背处的压力相当。
 进一步，悬浮二级压缩机的磁悬浮电机腔体出口下游设置有第一冷却器，经第二冷却器冷却后的冷却气一部分被引至磁悬浮一级压缩机的磁悬浮电机腔体，另一部分被引至磁悬浮一级压缩机工质入口的上游管路。
 进一步，磁悬浮一级压缩机的磁悬浮电机腔体出口下游设置有第二冷却器，经第二冷却器冷却后的冷却气通过管路引至磁悬浮一级压缩机工质入口的上游管路。
 一种用于制冷系统的磁悬浮电机密封-冷却装置的冷却方法，将一部分磁悬浮一级压缩机出口冷却后的工质作为冷却气经管路引入磁悬浮二级压缩机的磁悬浮电机腔体，对磁悬浮二级压缩机的磁悬浮电机进行冷却；磁悬浮二级压缩机的磁悬浮电机腔体出口下游的冷却气一部分被引至磁悬浮一级压缩机的磁悬浮电机腔体，对磁悬浮一级压缩机的磁悬浮电机进行冷却，另一部分被引至磁悬浮一级压缩机工质入口的上游管路，重新进入磁悬浮一级压缩机循环；磁悬浮一级压缩机的磁悬浮电机腔体出口下游的冷却气被引至磁悬浮一级压缩机工质入口的上游管路，重新进入磁悬浮一级压缩机循环。
 本发明的有益效果如下：
 将一部分磁悬浮一级压缩机出口冷却后的工质作为冷却气引入磁悬浮二级压缩机的磁悬浮电机腔体；将磁悬浮二级压缩机的磁悬浮电机腔体出口下游的冷却气一部分引至磁悬浮一级压缩机的磁悬浮电机腔体，便于匹配冷却气压力，对冷却气进行充分的利用，以减小冷却气的消耗。
 采用电机风冷与水冷方式的结合设计，通过风冷充分带走电机转子处产生的热量，通过水冷环路的设计充分带走电机定子的热量。在保证电机稳定运行的前提下，有效减少了冷却气的消耗，即系统制冷工质的额外消耗量，保证了系统的制冷能力。
 通过密封与冷却的设计，实现了密封气与冷却气的温度、压力配合，两者相辅相成，密不可分，形成了电机密封与冷却的协同解决方案。
 轮背密封与轴封的结合以及密封结构的交错式设计，极大降低了一级、二级压缩机轮背处工质的泄漏量，保证了系统的制冷能力。
 膨胀机密封设计中，通过热密封气的引入，建立了轮背处工质与密封气的平衡压力场，避免了轮背处低温工质进入电机腔体，热密封气在密封结构与电机腔体间的流动对电机运行亦无不良影响，有效保证了电机的安全、稳定运行。
 在制冷系统的工艺流程中，通过密封与冷却的设计，实现了密封气与冷却气的温度、压力配合，两者相辅相成，形成了电机密封与冷却的协同解决方案。
 附图说明
 为了更清楚地说明本发明具体实施方式或现有技术中的技术方案，下面将对具体实施方式或现有技术描述中所需要使用的附图做简单的介绍，显而易见地，下面描述中的附图是本发明一些实施方式，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下,还可以根据这些附图获得其他的附图。
 图1为制冷系统的整体工艺流程图；
 图2为磁悬浮一级压缩机-磁悬浮膨胀机密封、冷却协同解决方案示意图；
 图3为磁悬浮二级压缩机的密封、冷却协同解决方案示意图；
 图4为冷却水环路示意图；
 图5为密封结构的另一实施方案示意图。
 实施方式
 下面将结合本发明实施例中的附图，对本发明中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本发明的一部分，而不是全部的实施例。基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动所获得的所有其他实施例，都属于本发明保护的范围。
 第一实施例。
 本发明的用于制冷系统的磁悬浮电机密封-冷却装置，如图1所示，制冷系统包含磁悬浮一级压缩机1、磁悬浮二级压缩机2、磁悬浮膨胀机3、主换热器4、回热器5、第一后冷器61、第二后冷器62、第一冷却器71、第二冷却器72、密封气调节阀8和冷却气调节阀9。磁悬浮一级压缩机1、磁悬浮膨胀机3同轴设置，磁悬浮一级压缩机1、磁悬浮二级压缩机2、回热器5、磁悬浮膨胀机3、主换热器4依次连接。磁悬浮一级压缩机1的工质出口依次经第一工质管路S1、第一后冷器61和第二工质管路S2与磁悬浮二级压缩机2的工质入口连接，磁悬浮二级压缩机2的工质出口依次经第三工质管路S3、第二后冷器62、第四工质管路S4、回热器5、第五工质管路S5与磁悬浮膨胀机3的工质入口连接，磁悬浮膨胀机3的工质出口依次经第六工质管路S6、主换热器4、第七工质管路S7与磁悬浮一级压缩机1的工质入口连接。
 制冷系统可采用闭式循环。具体过程为：制冷工质进入磁悬浮一级压缩机1内被压缩，第一后冷器61对压缩机出口工质进行冷却；被冷却后的工质进入二级压缩机2内压缩，再经过第二后冷器62被冷却，被冷却的工质进入回热器5被预冷，之后工质进入磁悬浮膨胀机3中膨胀做功，回收一部分功率；膨胀后的工质进入主换热器4内为外界提供冷量，工质在经过主换热器4后仍持有一定冷量，进入回热器5中对二级压缩机2压缩后的工质进行预冷，回热器出口的工质进入一级压缩机中，完成闭式循环。
 作为磁悬浮电机稳定运行的保证，其密封及冷却方式尤为关键。由图2、图3可知，磁悬浮一级压缩机1、磁悬浮二级压缩机2的磁悬浮电机腔体内充满冷却气。为防止冷却气向叶轮轮背处回流，冷却气压力需低于叶轮轮背处工质压力。
 磁悬浮二级压缩机2的磁悬浮电机腔体内的冷却气取自一级压缩机出口冷却后的工质。磁悬浮二级压缩机2的磁悬浮电机腔体的冷却气入口经第九工质管路S9与第二工质管路S2连接，用于将一级压缩机出口冷却后的工质引入磁悬浮二级压缩机2的磁悬浮电机腔体。磁悬浮二级压缩机2的磁悬浮电机腔体的冷却气出口经第十工质管路S10、第一冷却器71、第十一工质管路S11、第十三工质管路S13与第七工质管路S7连接；磁悬浮一级压缩机1的磁悬浮电机腔体的冷却气入口经第十二工质管路S12和冷却气调节阀9连接至第十一工质管路S11和第十三工质管路S13之间；磁悬浮一级压缩机1的磁悬浮电机腔体的冷却气出口经第十四工质管路S14、第二冷却器72连接至第七工质管路S7。磁悬浮一级压缩机1的磁悬浮电机腔体的密封气入口经第八工质管路S8、密封气调节阀8与第四工质管路S4连接。
 通过上述冷却气的引入方式，能够使磁悬浮一级压缩机1和磁悬浮二级压缩机2的磁悬浮电机腔体内的冷却气的压力低于叶轮轮背处工质压力，有效为防止冷却气向叶轮轮背处回流。
 第二实施例。
 在第一实施例的基础上，磁悬浮一级压缩机1和磁悬浮二级压缩机2的磁悬浮电机机壳还设置有冷却水环路，冷却水经电机机壳冷却水环路对磁悬浮电机进行冷却。
 具体的电机机壳冷却水环路如图4所示。
 具体地，磁悬浮二级压缩机2的电机的冷却方式为：一级压缩机1的出口工质经后第一后冷器61冷却后（优选的，冷却后温度可设定为39℃左右，根据实际供应冷却水温调整），经第九工质管路S9进入磁悬浮二级压缩机2的电机腔体内，带走电机转子运行产生的热量。同时，冷却水经第一冷却水管路S15流入电机机壳冷却水环路，沿电机机壳环向、轴向流动，通过冷却水环路充分带走电机定子热量，冷却水经第二冷却水出口管路S16由电机外壳处管路排出。通过水冷与风冷方式的结合，在满足电机冷却要求的条件下，极大程度地减少了对制冷工质的流量消耗，保证了系统的制冷能力。在水冷设计中，通过冷却水环路的设计，拓宽了冷却水回路的流通范围，增强了对电机的冷却能力。
 磁悬浮一级压缩机1的冷却方式为：磁悬浮二级压缩机2的冷却气出口的冷却器经第一冷却器71冷却后，经第十二工质管路S12引入磁悬浮一级压缩机1的电机腔体中作为冷却气。为防止冷却气向一级压缩机叶轮轮背处回流，通过冷却气调节阀9调整第十二工质管路S12中冷却气的流量与压力，使其略低于磁悬浮一级压缩机1轮背处工质压力，然后流入磁悬浮一级压缩机1的电机腔体中；过量的冷却气可通过第十三工质管路S13引出至第七工质管路S7。进入磁悬浮一级压缩机1的电机腔体中的冷却气对电机转子M37进行充分冷却后，由电机外壳排出。带有电机热量的冷却气经第十四工质管路S14和第二冷却器72冷却后，重新汇入第七工质管路S7进入磁悬浮一级压缩机1中循环。磁悬浮一级压缩机1的水冷方式与磁悬浮二级压缩机2的水冷方式相同，不做赘述。
 第三实施例。
 为了进一步避免冷却气向叶轮轮背处回流，可以为磁悬浮一级压缩机1和磁悬浮二级压缩机2设置相应的密封，具体如下：
 磁悬浮二级压缩机2的密封方式为：在二级压缩机叶轮M21与轮背间隙之中，设置叶轮密封齿M23与轮背密封齿M22，二者形成迷宫交错式结构；在轴端，设置有轴端定子密封齿M24与轴端转子密封齿M25，二者形成迷宫交错式结构。由于叶轮M21出口处工质与电机腔体内冷却气之间的压差，叶轮轮背处将产生微量泄漏。通过轮背、轴端两道迷宫交错式结构设计及两道密封结构间形成的流动死区，将极大减少工质的泄漏量，保证了系统的制冷能力。微量的泄漏工质将与电机腔体内的冷却气汇合为一路经第十工质管路S10排出。
 磁悬浮一级压缩机1的密封方式与磁悬浮二级压缩机2的密封方式相似。由于一级压缩机叶轮轮背处工质与一体机电机腔体内冷却气间存在的压差，将产生少量泄漏。通过轮背与轴端的迷宫交错式密封设计以及两道密封结构间形成的流动死区，将极大减少工质的泄漏量，减少系统中循环工质的消耗，保证了系统的制冷能力。微量的泄漏工质将经第十四工质管路S14排出。
 磁悬浮一级压缩机1、磁悬浮二级压缩机2、磁悬浮膨胀机3的轮背和轴端密封结构的另一实施方式如图5所示。在相邻的轮背密封齿之间设置有短密封齿，短密封齿与叶轮密封齿的顶端相对设置；在相邻的轴端定子密封齿之间设置有短密封齿，短密封齿与轴端转子密封齿的顶端相对设置。
 第四实施例。
 为了进一步提高密封效果，可以对磁悬浮膨胀机3采取相应的密封措施。具体密封方式为：磁悬浮二级压缩机2的出口工质经第二后冷器62冷却后（优选的，冷却后温度可设定为39℃左右，根据实际供应冷却水温调整），经第8工质管路引流作为磁悬浮膨胀机3的密封气。为避免密封气向膨胀机叶轮M31轮背处回流，通过密封气调节阀8调整其压力与流量。在磁悬浮膨胀机3的轮背处，设置轮背密封齿M32和叶轮密封齿M33，二者形成迷宫交错式结构；在磁悬浮膨胀机3轴端设置轴端定子密封齿M34与轴端转子密封齿M35，二者形成迷宫交错式结构。为避免膨胀机轮背处低温工质泄漏至电机腔体内，轴端开有密封气通孔M36，引入密封气，其压力通过密封气调节阀调整至与轮背处压力相当。轮背密封与轴端密封间的流动死区将消耗轮背处工质随叶轮转动形成的动压。因此，膨胀机轮背间隙入口的工质与密封气将建立起平衡的压力场，避免了轮背处低温工质泄漏进电机腔体，威胁电机的运行安全。同时，由于密封气与电机腔体内冷却气间存在压差，将产生少量泄漏。通过轴端交错密封齿的设计，将极大减小该部分的泄漏量，密封气的温度也不会影响电机的安全运行。
 以上所述，仅为本发明较佳的具体实施方式，应当理解，本发明公开的申请的优选实施例是对本发明的实施方案的原理的说明，并不用于限制本发明。凡是在本发明的发明构思下，利用本发明说明书及附图内容所作的等效结构变换，或直接/间接运用在其他相关的技术领域均包括在本发明的专利保护范围内。

Claims (11)

  1. [根据细则91更正 26.12.2023]
    一种用于制冷系统的磁悬浮电机密封-冷却装置的冷却方法，所述制冷系统包含磁悬浮一级压缩机、磁悬浮二级压缩机、磁悬浮膨胀机、主换热器和冷却气调节阀；磁悬浮一级压缩机、磁悬浮膨胀机同轴设置，磁悬浮一级压缩机、磁悬浮二级压缩机、磁悬浮膨胀机、主换热器依次连接；其特征在于：磁悬浮二级压缩机的磁悬浮电机腔体内的冷却气取自磁悬浮一级压缩机出口冷却后的工质；磁悬浮一级压缩机的磁悬浮电机腔体的冷却气取自磁悬浮二级压缩机的磁悬浮电机腔体出口的冷却气，并通过冷却气调节阀调整流量与压力，将一部分磁悬浮一级压缩机出口冷却后的工质作为冷却气经管路引入磁悬浮二级压缩机的磁悬浮电机腔体，对磁悬浮二级压缩机的磁悬浮电机进行冷却；磁悬浮二级压缩机的磁悬浮电机腔体出口下游的冷却气一部分被引至磁悬浮一级压缩机的磁悬浮电机腔体，对磁悬浮一级压缩机的磁悬浮电机进行冷却，另一部分被引至磁悬浮一级压缩机工质入口的上游管路，重新进入磁悬浮一级压缩机循环；磁悬浮一级压缩机的磁悬浮电机腔体出口下游的冷却气被引至磁悬浮一级压缩机工质入口的上游管路，重新进入磁悬浮一级压缩机循环。
  2. [根据细则91更正 26.12.2023]
     2.根据权利要求1所述的冷却方法，其特征在于：还包括第一后冷器、第二后冷器，第一后冷器、第二后冷器分别设置在磁悬浮一级压缩机、磁悬浮二级压缩机的下游。
  3. [根据细则91更正 26.12.2023]
     3.根据权利要求1所述的冷却方法，其特征在于：磁悬浮一级压缩机和磁悬浮二级压缩机的磁悬浮电机机壳设置有冷却水环路。
  4. [根据细则91更正 26.12.2023]
     4.根据权利要求3所述的冷却方法，其特征在于：冷却水流入电机机壳的冷却水环路后，沿电机机壳环向、轴向流动。
  5. [根据细则91更正 26.12.2023]
    根据权利要求1所述的冷却方法，其特征在于：磁悬浮一级压缩机、磁悬浮二级压缩机、磁悬浮膨胀机分别设置有轮背密封结构与轴封结构。
  6. [根据细则91更正 26.12.2023]
    根据权利要求5所述的冷却方法，其特征在于：轮背密封结构设置在叶轮与轮背间隙之中，包括叶轮密封齿与轮背密封齿，二者形成迷宫交错式结构。
  7. [根据细则91更正 26.12.2023]
    根据权利要求6所述的冷却方法，其特征在于：轴封结构设置在磁悬浮电机轴端，包括轴端定子密封齿与轴端转子密封齿，二者形成迷宫交错式结构。
  8. [根据细则91更正 26.12.2023]
    根据权利要求7所述的冷却方法，其特征在于：在相邻的轮背密封齿之间还设置有短密封齿，短密封齿与叶轮密封齿的顶端相对设置；在相邻的轴端定子密封齿之间设置有短密封齿，短密封齿与轴端转子密封齿的顶端相对设置。
  9. [根据细则91更正 26.12.2023]
    根据权利要求1-7任一项所述的冷却方法，其特征在于：磁悬浮二级压缩机出口冷却后的一部分工质通过密封气调节阀被引流至磁悬浮膨胀机作为密封气，在磁悬浮膨胀机的轴端开有密封气通孔用于引入密封气。
  10. [根据细则91更正 26.12.2023]
    根据权利要求1-7任一项所述的冷却方法，其特征在于：磁悬浮二级压缩机的磁悬浮电机腔体出口下游设置有第一冷却器，经第二冷却器冷却后的冷却气一部分被引至磁悬浮一级压缩机的磁悬浮电机腔体，另一部分被引至磁悬浮一级压缩机工质入口的上游管路。
  11. [根据细则91更正 26.12.2023]
    根据权利要求10所述的冷却方法，其特征在于：磁悬浮一级压缩机的磁悬浮电机腔体出口下游设置有第二冷却器，经第二冷却器冷却后的冷却气通过管路引至磁悬浮一级压缩机工质入口的上游管路。
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN119616887A (zh) * 2024-12-09 2025-03-14 南京奥斯行系统工程有限公司 一种具有氧气风冷系统的磁悬浮离心式二级氧气压缩机

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115566857B (zh) * 2022-11-15 2023-10-27 中国船舶集团有限公司第七一一研究所 一种用于制冷系统的磁悬浮电机密封-冷却装置及方法

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160186764A1 (en) * 2014-12-31 2016-06-30 Ingersoll-Rand Company Multi-stage compressor with single electric direct drive motor
CN207975867U (zh) * 2018-01-10 2018-10-16 武汉市科瑞莱机电设备有限公司 一种环保冷媒磁悬浮式高效冷水机组
CN108895025A (zh) 2018-08-29 2018-11-27 亿昇(天津)科技有限公司 一种可平衡部分轴向力的鼓风机轴端密封结构
CN111322275A (zh) * 2020-01-16 2020-06-23 江苏乐科节能科技股份有限公司 一种高速永磁电机直驱的封闭式双级离心水蒸气压缩机的自冷却系统及其方法
CN111441960A (zh) * 2020-04-29 2020-07-24 佛山格尼斯磁悬浮技术有限公司 磁悬浮离心空气压缩机二级压缩系统
CN112096467A (zh) 2020-10-12 2020-12-18 中国船舶重工集团公司第七0三研究所 一种应用于有机朗肯循环的磁悬浮电机冷却系统及冷却方法
CN112583185A (zh) 2021-02-24 2021-03-30 苏州保邦电气有限公司 一种磁悬浮电机用密封结构及磁悬浮电机
CN112833103A (zh) 2021-02-02 2021-05-25 武汉波依迈科技有限公司 一种磁悬浮密封轴承
CN115566857A (zh) * 2022-11-15 2023-01-03 中国船舶集团有限公司第七一一研究所 一种用于制冷系统的磁悬浮电机密封-冷却装置及方法

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH138087A (de) * 1929-02-19 1930-02-15 Escher Wyss Maschf Ag Dichtung an sich drehenden Maschinenteilen, insbesondere von Kreiselmaschinen.
JP6747878B2 (ja) * 2016-06-07 2020-08-26 株式会社Ihi 回転機械
JP6982440B2 (ja) * 2017-09-11 2021-12-17 三菱重工コンプレッサ株式会社 回転機械、インペラ
FR3072428B1 (fr) * 2017-10-16 2019-10-11 L'air Liquide Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Dispositif et procede de compression et machine de refrigeration
CN110360136A (zh) * 2018-05-21 2019-10-22 南通大通宝富风机有限公司 蒸汽压缩机
CN110455002B (zh) * 2019-09-09 2024-10-15 合肥天鹅制冷科技有限公司 一种磁悬浮离心式冷水机组电机冷却系统

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160186764A1 (en) * 2014-12-31 2016-06-30 Ingersoll-Rand Company Multi-stage compressor with single electric direct drive motor
CN207975867U (zh) * 2018-01-10 2018-10-16 武汉市科瑞莱机电设备有限公司 一种环保冷媒磁悬浮式高效冷水机组
CN108895025A (zh) 2018-08-29 2018-11-27 亿昇(天津)科技有限公司 一种可平衡部分轴向力的鼓风机轴端密封结构
CN111322275A (zh) * 2020-01-16 2020-06-23 江苏乐科节能科技股份有限公司 一种高速永磁电机直驱的封闭式双级离心水蒸气压缩机的自冷却系统及其方法
CN111441960A (zh) * 2020-04-29 2020-07-24 佛山格尼斯磁悬浮技术有限公司 磁悬浮离心空气压缩机二级压缩系统
CN112096467A (zh) 2020-10-12 2020-12-18 中国船舶重工集团公司第七0三研究所 一种应用于有机朗肯循环的磁悬浮电机冷却系统及冷却方法
CN112833103A (zh) 2021-02-02 2021-05-25 武汉波依迈科技有限公司 一种磁悬浮密封轴承
CN112583185A (zh) 2021-02-24 2021-03-30 苏州保邦电气有限公司 一种磁悬浮电机用密封结构及磁悬浮电机
CN115566857A (zh) * 2022-11-15 2023-01-03 中国船舶集团有限公司第七一一研究所 一种用于制冷系统的磁悬浮电机密封-冷却装置及方法

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
See also references of EP4622074A1
ZHONG-WEI GUO, ZHU RUI-QI: "Analysis of The Irreversible Air Refrigeration Cycle with Combination Offering of Cool and Heat", JOURNAL OF ENGINEERING THERMOPHYSICS, vol. 25, no. Suppl., 30 December 2004 (2004-12-30), pages 9 - 12, XP093170244 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN119616887A (zh) * 2024-12-09 2025-03-14 南京奥斯行系统工程有限公司 一种具有氧气风冷系统的磁悬浮离心式二级氧气压缩机

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