WO2018090894A1 - Ensemble compresseur et son procédé de commande et système de réfrigération/chauffage - Google Patents

Ensemble compresseur et son procédé de commande et système de réfrigération/chauffage Download PDF

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Publication number
WO2018090894A1
WO2018090894A1 PCT/CN2017/110826 CN2017110826W WO2018090894A1 WO 2018090894 A1 WO2018090894 A1 WO 2018090894A1 CN 2017110826 W CN2017110826 W CN 2017110826W WO 2018090894 A1 WO2018090894 A1 WO 2018090894A1
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WIPO (PCT)
Prior art keywords
lubricant
exhaust gas
temperature
gas temperature
working fluid
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/CN2017/110826
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English (en)
Chinese (zh)
Inventor
任冬
乌静
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Copeland Suzhou Co Ltd
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Emerson Climate Technologies Suzhou Co Ltd
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Publication date
Application filed by Emerson Climate Technologies Suzhou Co Ltd filed Critical Emerson Climate Technologies Suzhou Co Ltd
Priority to KR1020197016498A priority Critical patent/KR102189168B1/ko
Publication of WO2018090894A1 publication Critical patent/WO2018090894A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/06—Superheaters
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/16—Lubrication
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2105—Oil temperatures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21155—Temperatures of a compressor or the drive means therefor of the oil

Definitions

  • the present invention relates to a control method for a compressor assembly, a compressor assembly, and a refrigeration/heating system.
  • Compressors such as scroll compressors typically include a compression mechanism comprised of, for example, a fixed scroll member and an orbiting scroll member.
  • the compression mechanism receives working fluid from a suction pressure zone of the compressor, compresses the working fluid in one or more compression chambers defined by the compression mechanism, and then discharges the compressed working fluid to a discharge pressure zone of the compressor.
  • the compression mechanism achieves lubrication by means of a lubricant.
  • the lubricant used to lubricate the compression mechanism can also be used for lubrication of other components of the compressor, such as the lubrication of the main bearing housing or motor.
  • a lubricant for lubricating the various components of the compressor typically flows through the compression mechanism with the working fluid and is discharged to a discharge pressure zone of the compressor. During this compression, the temperature of the lubricant is raised along with the temperature of the working fluid. The lubricant is then separated from the working fluid and recovered for reuse in the lubrication of the compressor.
  • this reheating lubricant can overheat the inhaled working fluid, thereby reducing compressor volumetric efficiency and consequently reducing compressor performance.
  • overheated lubricants can cause excessive wear when lubricating various components of the compressor, such as motors, reducing compressor reliability. For example, it is difficult for the superheated lubricant to keep the viscosity of the lubricant at a desired level capable of maintaining the desired oil film thickness between the moving parts.
  • Another object of one or more embodiments of the present invention is to provide a compressor assembly that is capable of monitoring the temperature of a lubricant used to lubricate a compressor and controlling its operation based on the sensed temperature of the lubricant For example, when the temperature of the lubricant is too high, the temperature of the lubricant is actively controlled (eg, lowered), an alarm signal is issued, and/or a shutdown operation is performed to improve the performance of the compressor (eg, stability and reliability, etc.).
  • a control method for a compressor assembly including a compressor that compresses a working fluid from a suction pressure to a discharge pressure, wherein the discharge pressure is greater than the suction Pressure, the control method includes:
  • the operation of the compressor assembly is controlled based on the sensed temperature of the lubricant.
  • control method further includes: a lubricant temperature target determining operation, the lubricant temperature target determining operation comprising: determining whether the temperature of the lubricant is greater than a lubricant temperature target value; The lubricant temperature control logic is executed when the temperature is greater than the lubricant temperature target value; and the first control logic is executed when the temperature of the lubricant is less than or equal to the lubricant temperature target value.
  • a lubricant temperature target determining operation comprising: determining whether the temperature of the lubricant is greater than a lubricant temperature target value
  • the lubricant temperature control logic is executed when the temperature is greater than the lubricant temperature target value
  • the first control logic is executed when the temperature of the lubricant is less than or equal to the lubricant temperature target value.
  • control method further includes: sensing an exhaust gas temperature of the working fluid compressed by the compressor; and an exhaust gas temperature target determining operation, the exhausting temperature target determining operation comprising: determining the row Whether the gas temperature is greater than the exhaust gas temperature target value; when the exhaust gas temperature is greater than the exhaust gas temperature target value, performing exhaust gas temperature control logic; and when the exhaust gas temperature is less than or equal to the exhaust gas temperature target value Executing the lubricant temperature target determination operation or the first control logic.
  • the control method further includes: a lubricant temperature protection determining operation, the lubricant temperature protection determining operation comprising: determining whether the temperature of the lubricant is greater than a lubricant temperature protection value; When the temperature is greater than the lubricant temperature protection value, performing lubricant temperature protection logic; and when the temperature of the lubricant is less than or equal to the lubricant temperature protection value, performing the exhaust temperature target determination operation And the lubricant temperature target determining operation or the first control logic, wherein the lubricant temperature protection value is greater than the lubricant temperature target value.
  • a lubricant temperature protection determining operation comprising: determining whether the temperature of the lubricant is greater than a lubricant temperature protection value; When the temperature is greater than the lubricant temperature protection value, performing lubricant temperature protection logic; and when the temperature of the lubricant is less than or equal to the lubricant temperature protection value, performing the exhaust temperature target determination operation And the lubricant temperature target
  • the control method further includes: an exhaust gas temperature protection determining operation, the exhaust gas temperature protection determining operation comprising: determining whether the exhaust gas temperature is greater than an exhaust gas temperature protection value; and when the exhaust gas temperature is greater than Exhaust gas temperature protection logic is executed when the exhaust gas temperature protection value is; and the lubricant temperature protection determination operation, the exhaust gas temperature target determination operation is performed when the exhaust gas temperature is less than or equal to the exhaust gas temperature protection value And the lubricant temperature target determining operation or the first control logic, wherein the exhaust gas temperature protection value is greater than the exhaust gas temperature target value.
  • an exhaust gas temperature protection determining operation comprising: determining whether the exhaust gas temperature is greater than an exhaust gas temperature protection value; and when the exhaust gas temperature is greater than Exhaust gas temperature protection logic is executed when the exhaust gas temperature protection value is; and the lubricant temperature protection determination operation, the exhaust gas temperature target determination operation is performed when the exhaust gas temperature is less than or equal to the exhaust gas temperature protection value And the lubricant temperature target determining operation or the first control logic, where
  • the exhaust gas temperature protection logic and the lubricant temperature protection logic each comprise an alarm operation and/or a shutdown operation
  • the exhaust gas temperature control logic includes increasing a flow rate of the expanded working fluid to reduce the exhaust gas temperature
  • the lubricant temperature control logic includes increasing a flow rate of the expanded working fluid to reduce the temperature of the lubricant
  • the first control logic includes adjusting the flow of the expanded working fluid to improve performance of the compressor assembly.
  • control method further includes transferring heat from the condensed working fluid to the expanded working fluid.
  • control method further includes supplying the heated working fluid to an intermediate pressure region of the compressor, the intermediate pressure being greater than the suction pressure and less than the discharge pressure.
  • a compressor assembly comprising:
  • the compression mechanism causing compression of the working fluid from a suction pressure to a discharge pressure, wherein the discharge pressure is greater than the suction pressure;
  • An expansion device configured to expand the working fluid condensed by the condenser
  • a heat exchanger configured to transfer heat from a lubricant for lubricating the compressor to the working fluid expanded by the expansion device to cool the lubricant and heat by the expansion The working fluid that the device expands;
  • a first sensing device configured to sense a temperature of the lubricant cooled by the heat exchanger
  • a controller configured to control operation of the compressor assembly based on the temperature of the lubricant sensed by the first sensing device.
  • the controller is configured to perform a lubricant temperature target determining operation, the lubricant temperature target determining operation comprising: determining whether the temperature of the lubricant is greater than a lubricant temperature target value; The lubricant temperature control logic is executed when the temperature is greater than the lubricant temperature target value; and the first control logic is executed when the temperature of the lubricant is less than or equal to the lubricant temperature target value.
  • the compressor assembly further includes a second sensing device configured to sense an exhaust gas temperature of the working fluid compressed by the compressor, the controller further configured to Executing an exhaust gas temperature target determining operation, the exhaust gas temperature target determining operation includes: determining whether the exhaust gas temperature is greater than an exhaust gas temperature target value; and performing an exhaust when the exhaust gas temperature is greater than the exhaust gas temperature target value a gas temperature control logic; and when the exhaust gas temperature is less than or equal to the exhaust gas temperature target value, performing the lubricant temperature target determination operation or the first control logic.
  • the controller is further configured to perform a lubricant temperature protection determining operation, the lubricant temperature protection determining operation comprising: determining whether the temperature of the lubricant is greater than a lubricant temperature protection value; When the temperature is greater than the lubricant temperature protection value, Performing a lubricant temperature protection logic; and performing the exhaust gas temperature target determination operation, the lubricant temperature target determination operation, or the first when the temperature of the lubricant is less than or equal to the lubricant temperature protection value A control logic, wherein the lubricant temperature protection value is greater than the lubricant temperature target value.
  • the controller is further configured to perform an exhaust gas temperature protection determining operation, the exhaust gas temperature protection determining operation comprising: determining whether the exhaust gas temperature is greater than an exhaust gas temperature protection value; and when the exhaust gas temperature is greater than Exhaust temperature protection logic is executed when the exhaust gas temperature protection value is described; and when the exhaust gas temperature is less than or equal to the exhaust gas temperature protection value, the lubricant temperature protection determination operation, the exhaust gas temperature target determination operation, The lubricant temperature target determining operation or the first control logic, wherein the exhaust gas temperature protection value is greater than the exhaust gas temperature target value.
  • the exhaust gas temperature protection determining operation comprising: determining whether the exhaust gas temperature is greater than an exhaust gas temperature protection value; and when the exhaust gas temperature is greater than Exhaust temperature protection logic is executed when the exhaust gas temperature protection value is described; and when the exhaust gas temperature is less than or equal to the exhaust gas temperature protection value, the lubricant temperature protection determination operation, the exhaust gas temperature target determination operation, The lubricant temperature target determining operation or the first control logic, wherein
  • the exhaust gas temperature protection logic and the lubricant temperature protection logic each comprise an alarm operation and/or a shutdown operation
  • the exhaust gas temperature control logic includes increasing a flow rate of the working fluid expanded by the expansion device to reduce the exhaust gas temperature
  • the lubricant temperature control logic includes increasing a flow rate of the working fluid expanded by the expansion device to reduce the temperature of the lubricant
  • the first control logic includes adjusting a flow rate of the working fluid expanded by the expansion device to improve performance of the compressor assembly.
  • the heat exchanger is further configured to transfer heat from the working fluid condensed by the condenser to the working fluid expanded by the expansion device.
  • the compressor assembly is further configured to supply the working fluid heated by the heat exchanger to an intermediate pressure region of the compressor, the intermediate pressure being greater than the suction pressure and less than the discharge pressure.
  • the first sensing device is disposed in a line that fluidly communicates the heat exchanger with the compressor to allow the lubricant to flow from the heat exchanger to the compressor.
  • the compressor comprises a scroll compressor.
  • a refrigeration/heating system comprising a compressor assembly according to the teachings herein.
  • a refrigeration/heating system comprising:
  • the compression mechanism causing compression of the working fluid from a suction pressure to a discharge pressure, wherein the discharge pressure is greater than the suction pressure;
  • a condenser configured to condense the working fluid compressed by the compressor
  • An expansion device configured to expand the working fluid condensed by the condenser
  • a heat exchanger configured to transfer heat from a lubricant for lubricating the compressor to the working fluid expanded by the expansion device to cool the lubricant and heat by the expansion The working fluid that the device expands;
  • a first sensing device configured to sense a temperature of the lubricant cooled by the heat exchanger
  • a controller configured to control operation of the refrigeration/heating system based on the temperature of the lubricant sensed by the first sensing device.
  • the controller is configured to perform a lubricant temperature target determining operation, the lubricant temperature target determining operation comprising: determining whether the temperature of the lubricant is greater than a lubricant temperature target value; The lubricant temperature control logic is executed when the temperature is greater than the lubricant temperature target value; and the first control logic is executed when the temperature of the lubricant is less than or equal to the lubricant temperature target value.
  • the refrigeration/heating system further includes a second sensing device configured to sense an exhaust gas temperature of the working fluid compressed by the compressor, the controller further Configuring to perform an exhaust gas temperature target determination operation, the exhaust gas temperature target determining operation includes: determining whether the exhaust gas temperature is greater than an exhaust gas temperature target value; and when the exhaust gas temperature is greater than the exhaust gas temperature target value, Performing exhaust gas temperature control logic; and executing the lubricant temperature target determination operation or the first control logic when the exhaust gas temperature is less than or equal to the exhaust gas temperature target value.
  • the controller is further configured to perform a lubricant temperature protection determining operation, the lubricant temperature protection determining operation comprising: determining whether the temperature of the lubricant is greater than a lubricant temperature protection value; Performing lubricant temperature protection logic when the temperature is greater than the lubricant temperature protection value; and performing the exhaust temperature target determination when the temperature of the lubricant is less than or equal to the lubricant temperature protection value Operation, the lubricant temperature target Determining an operation or the first control logic, wherein the lubricant temperature protection value is greater than the lubricant temperature target value.
  • the controller is further configured to perform an exhaust gas temperature protection determining operation, the exhaust gas temperature protection determining operation comprising: determining whether the exhaust gas temperature is greater than an exhaust gas temperature protection value; and when the exhaust gas temperature is greater than Exhaust temperature protection logic is executed when the exhaust gas temperature protection value is described; and when the exhaust gas temperature is less than or equal to the exhaust gas temperature protection value, the lubricant temperature protection determination operation, the exhaust gas temperature target determination operation, The lubricant temperature target determining operation or the first control logic, wherein the exhaust gas temperature protection value is greater than the exhaust gas temperature target value.
  • the exhaust gas temperature protection determining operation comprising: determining whether the exhaust gas temperature is greater than an exhaust gas temperature protection value; and when the exhaust gas temperature is greater than Exhaust temperature protection logic is executed when the exhaust gas temperature protection value is described; and when the exhaust gas temperature is less than or equal to the exhaust gas temperature protection value, the lubricant temperature protection determination operation, the exhaust gas temperature target determination operation, The lubricant temperature target determining operation or the first control logic, wherein
  • the exhaust gas temperature protection logic and the lubricant temperature protection logic each comprise an alarm operation and/or a shutdown operation
  • the exhaust gas temperature control logic includes increasing a flow rate of the working fluid expanded by the expansion device to reduce the exhaust gas temperature
  • the lubricant temperature control logic includes increasing a flow rate of the working fluid expanded by the expansion device to reduce the temperature of the lubricant
  • the first control logic includes adjusting a flow rate of the working fluid expanded by the expansion device to improve performance of the refrigeration/heating system.
  • the heat exchanger is further configured to transfer heat from the working fluid condensed by the condenser to the working fluid expanded by the expansion device.
  • the refrigeration/heating system is further configured to supply the working fluid heated by the heat exchanger to an intermediate pressure region of the compressor, the intermediate pressure being greater than the suction pressure and less than Describe the discharge pressure.
  • the first sensing device is disposed in a line that fluidly communicates the heat exchanger with the compressor to allow the lubricant to flow from the heat exchanger to the compressor.
  • the compressor comprises a scroll compressor.
  • An advantage of the control method for a compressor assembly, the compressor assembly, and the refrigeration/heating system according to one or more embodiments of the present invention lies in at least one of being capable of monitoring a lubricant for lubricating a compressor Temperature to signal an alarm when the temperature of the lubricant is too high and/or to perform a shutdown operation to avoid loss due to excessive wear of the compressor; to actively control the temperature of the lubricant by monitoring the temperature of the lubricant, thereby reducing compression
  • FIGS. 1A and 1B are perspective views showing a partial structure of a compressor assembly according to an embodiment of the present application at different angles of view;
  • FIG. 1C is a longitudinal cross-sectional view of a compressor in accordance with an embodiment of the present application.
  • FIG. 2 is a schematic diagram of a refrigeration/heating system in accordance with an embodiment of the present application.
  • FIG. 3 is an exemplary flow chart of a control method for a compressor assembly in accordance with an embodiment of the present application.
  • the compressor assembly 1 mainly includes a compressor 10, a heat exchanger 40, and a controller 60.
  • a lubricant e.g., lubricating oil
  • the controller 60 can monitor the temperature of the lubricant flowing out of the heat exchanger 40 and/or into the compressor 10 (in the figures and figures, when the lubricant is a lubricating oil, the temperature of the lubricating oil can be referred to simply as the oil temperature).
  • the controller 60 is capable of adjusting the heat exchange capacity of the heat exchanger 40 by the monitored temperature of the lubricant, thereby actively controlling the above temperature of the lubricant (eg, controlling the temperature of the lubricant within a specific range) to prevent Lubricant
  • the temperature is too high to degrade the performance of the compressor 10.
  • the performance of the compressors described herein optionally include: stability, safety, reliability, refrigeration/heating capacity, efficiency, energy consumption, and the like.
  • the compressor 10 generally includes a housing 101, a high-pressure side end cover 103 disposed at one end of the housing 101 (right end as shown in Fig. 1C), and a low-pressure side provided at the other end of the housing 101 (left end as shown in Fig. 1C).
  • the space between the partition 104 and the high pressure side end cover 103 constitutes the high pressure side region 109, and the space between the partition 104, the casing 101 and the low pressure side end cover 102 constitutes a low pressure side region (not identified).
  • An intake joint 110 for sucking a working fluid is disposed in the low pressure side region, and an exhaust joint 111 for discharging the compressed working fluid is disposed in the high pressure side region 109.
  • a motor 107 composed of a stator and a rotor (not labeled) is provided in the casing 101.
  • a rotating shaft 106 is provided in the rotor of the motor 107 to drive a compression mechanism 108 composed of, for example, a fixed scroll member and an orbiting scroll member (not labeled).
  • a compression chamber is formed between the fixed scroll member and the movable scroll member, and the compression chamber is gradually reduced from the radially outer side to the radially inner side, wherein the radially outermost compression chamber is at the suction pressure and the radially innermost portion is compressed.
  • the chamber is at discharge pressure.
  • the intermediate compression chamber is at an intermediate pressure between the suction pressure and the discharge pressure, and is also referred to as a medium pressure chamber.
  • the vicinity of one end of the rotating shaft 106 (right end as shown in FIG. 1C) is supported by a main bearing provided in the main bearing housing 105.
  • the one end (right end) of the rotating shaft 106 is provided with an eccentric crank pin capable of driving the orbiting scroll member such that the orbiting scroll member rotates in translation with respect to the fixed scroll member to effect compression of the working fluid.
  • the working fluid compressed by the fixed scroll member and the movable scroll member is discharged to the high pressure side region 109, and then exits the compressor 10 through the exhaust joint 111.
  • the lubricant from the outside of the compressor 10 is first supplied to one end of the rotating shaft 106 via a line (not shown) in the casing 101 (as shown in FIG. 1C).
  • the left end is formed in the rotary shaft 106 with a passage extending substantially in the axial direction thereof, that is, a center hole formed on the left side of the rotary shaft 106 and an eccentric hole extending from the center hole to the right to the end surface of the eccentric crank pin.
  • the lubricant is first supplied to the center hole.
  • the lubricant of the orifice is swung and/or pumped into the eccentric bore by the rotation of the rotating shaft 106 and/or under the pressure differential and flows to the right along the eccentric bore until the end face of the eccentric crank pin.
  • a part of the lubricant discharged from the end surface of the eccentric crank pin flows to the main bearing housing 105 to lubricate the main bearing, and a part flows to the end plate of the orbiting scroll member and extends over the thrust plate as the orbiting scroll member rotates. Push the surface.
  • the lubricant supplied to the moving parts in the compressor 10 is scooped up and splashed to form droplets or mist.
  • lubricant droplets or mists are mixed in a working fluid (eg, a refrigerant) that is drawn from the intake fitting 110.
  • a working fluid eg, a refrigerant
  • These lubricant-mixed working fluids are then drawn into the compression chamber of the compression mechanism 108 to effect lubrication, sealing and cooling of the interior of the compression mechanism 108.
  • the working fluid and lubricant compressed by the compression mechanism 108 are discharged into the high pressure side region 109, for example, by separation of the lubricant separator, which is separated from the working fluid and temporarily stored at the bottom of the high pressure side region 109.
  • the lubricant at the bottom of the high pressure side region 109 is discharged to the outside of the compressor 10, and then enters the heat exchanger 40 described above for cooling, and after being cooled by the heat exchanger 40, the lubricant is again supplied back.
  • the compressor 10 for example, is fed back to the left end of the rotating shaft 106 to continue lubricating the compressor 10 as described above.
  • FIGS. 1A-1C and Figure 2 illustrate the cooling process for the lubricant when the compressor assembly 1 and the refrigeration/heating system 2 are in operation.
  • the compressor assembly 1 includes a compressor 10 that compresses a working fluid (e.g., refrigerant) flowing therethrough from a suction pressure to a discharge pressure greater than a suction pressure.
  • a working fluid e.g., refrigerant
  • Intake connection 110 is in fluid communication with the low pressure side region of compressor 10 to supply working fluid to the low pressure side region.
  • the exhaust connection 111 is in fluid communication with the high pressure side region 109 of the compressor 10 to receive the compressed working fluid from the high pressure side region 109 of the compressor 10.
  • the compressor 10 is also provided with an intermediate pressure port 112 that is in fluid communication with the intermediate pressure chamber of the compression mechanism 108 of the compressor 10 at a position corresponding to an intermediate pressure between the discharge pressure and the suction pressure.
  • the intermediate pressure port 112 can supply working fluid to the compression chamber of the compressor 10 at, for example, the intermediate pressure.
  • the compressor assembly 1 may further include an expansion device 30, a heat exchanger 40, and a controller 60.
  • the compressor assembly 1 may also be provided with a first one for sensing the temperature of the lubricant.
  • Sensing device 50 see FIG. 2
  • controller 60 is configured to control the operation of compressor assembly 1 based on the temperature of the lubricant sensed by first sensing device 50, which components will be described in detail below.
  • the working fluid flowing out of the exhaust joint 111 flows into the condenser 20 where the working fluid releases a part of the heat.
  • This portion of the heat can be released into another fluid flowing through the condenser 20.
  • this portion of the heat can be transferred to the air stream introduced by the fan and flowing through the condenser 20.
  • the working fluid flowing through the condenser 20 is capable of (at least partially) condensing from a high temperature, high pressure gaseous working fluid to a reduced temperature high pressure condensing liquid working fluid.
  • the condensed working fluid then flows from the condenser 20 into the heat exchanger 40.
  • a reservoir 86 and/or a drying filter 85 may be disposed between the condenser 20 and the heat exchanger 40, wherein the reservoir 86 is configured to store a portion of the working fluid to supplement the working fluid.
  • the drying filter 85 is configured to remove unwanted impurities such as moisture in the working fluid during some of the losses during the cycle.
  • the condensed working fluid can enter the heat exchanger 40 (e.g., the top of the heat exchanger 40 of FIG. 1B) via line 401 via port 401, which is in fluid communication to port 42 via line 412 within heat exchanger 40.
  • the working fluid exits heat exchanger 40 (e.g., the bottom of heat exchanger 40 in Figure IB) via line 402 through port 42.
  • the working fluid releases a portion of the heat.
  • the condensed working fluid is recooled and exits the heat exchanger 40 at a lower temperature than when entering the heat exchanger 40.
  • the secondary cooled working fluid in line 402 flows through a primary throttling device 82 (e.g., a thermal expansion valve).
  • the working fluid flowing through the main throttle device 82 is expanded, and the pressure is lowered, and the temperature is further lowered.
  • the primary throttle device 82 can be dynamically controlled to accommodate variable loads on the refrigeration/heating system 2.
  • the primary throttling device 82 can be static (non-adjustable).
  • a sight glass 84 may be disposed between the heat exchanger 40 and the main throttle device 82 to observe the gas-liquid phase of the working fluid within the line 402.
  • a solenoid valve 83 may be provided between the heat exchanger 40 and the main throttle device 82 for opening or closing the circulation of the working fluid in the refrigeration/heating system 2.
  • the solenoid valve 83 can also be replaced by other types of valves or switches and can be placed at other locations of the refrigeration/heating system 2.
  • the expanded working fluid Downstream of the main throttling device 82, the expanded working fluid enters the evaporator 81.
  • the working fluid absorbs heat and changes from a low temperature and low pressure (liquid) working fluid to a temperature rise.
  • High low pressure (gaseous) working fluid As a non-limiting example, the heat absorbed by the working fluid may be drawn from the air stream introduced through the fan and flowing through the evaporator 81.
  • the working fluid leaving the evaporator 81 is returned to the low pressure side region of the compressor 10 via the intake fitting 110, thereby forming a closed circulation system.
  • Lubricant from compressor 10 can also flow through heat exchanger 40 as described above with respect to compressor 10.
  • lubricant can exit the compressor 10 from the high pressure side zone 109 via port 47, which is in fluid communication via line 45 to line 456 within the heat exchanger 40.
  • Line 406 is in fluid communication with line 456 via port 46 and fluid communication to compressor 10 via port 48, such that lubricant exiting compressor 10 flows through heat exchanger 40 and returns to the low pressure side region of compressor 10. For example, return to the left end of the rotating shaft 106 as shown in FIG. 1C.
  • the flowing lubricant releases heat. Therefore, the temperature of the lubricant leaving the heat exchanger 40 is lower than the temperature of the lubricant entering the heat exchanger 40.
  • a cooling medium such as cold water may be supplied to the heat exchanger 40 to cool the lubricant within the line 456 and/or the working fluid within the line 412.
  • the working fluid that is secondarily cooled by the heat exchanger 40 can increase the ability of the working fluid to absorb heat in the evaporator 81 before the working fluid flows through the main throttle device 82, thereby improving the refrigeration/heating system 2
  • the cooling capacity on the other hand, it can reduce the temperature of the lubricant that lubricates the compressor and improve the performance of the compressor.
  • the compressor assembly 1 utilizes the expanded condensed working fluid to absorb the heat released by the working fluid and lubricant flowing through the heat exchanger 40 in the heat exchanger 40.
  • a portion of the working fluid flowing through line 402 downstream of heat exchanger 40 may expand within expansion device 30 via line 408 (thus reducing the temperature and pressure of the working fluid) and through the line.
  • 403 is introduced into the heat exchanger 40.
  • the working fluid can reach the lower portion of the heat exchanger 40 through the port 43.
  • the expanded working fluid within line 403 can be in a liquid, gaseous or gas-liquid two phase state.
  • the working fluid can flow up through line 434 in heat exchanger 40 and into line 404 in fluid communication with intermediate pressure port 112.
  • the working fluid can exit the upper portion of the heat exchanger 40 through a port 44 that is in fluid communication with the line 404.
  • the working fluid flowing through line 434 flows from the flow through line 412
  • the body absorbs heat such that the temperature of the condensed working fluid within line 412 is reduced (i.e., it is secondary cooled).
  • the working fluid exiting the heat exchanger 40 via line 404 enters the intermediate pressure location (intermediate pressure chamber) of the compression mechanism 108 through the intermediate pressure port 112.
  • the compressor assembly 1 advantageously uses an expanded working fluid to cool the lubricant flowing through the compressor 10.
  • heat is transferred from the lubricant within line 456 to the working fluid within line 434 such that the temperature of the lubricant exiting heat exchanger 40 via line 406 is reduced.
  • increasing the supply of working fluid within line 403 can reduce the temperature of the lubricant to a greater extent, as will be described in detail below. Therefore, the heat exchanger 40 functions as a double heat exchange.
  • the expansion device 30 can be a dynamic device as needed to provide the desired cooling effect of the lubricant.
  • expansion device 30 can maintain the pressure within line 404 above the pressure of the intermediate pressure chamber in communication with intermediate pressure port 112.
  • the working fluid injected into the medium pressure chamber may be in a gaseous, liquid or gas-liquid two-phase state. Injection of the working fluid into the intermediate pressure chamber may also advantageously cool the compression mechanism 108 and reduce the exhaust temperature of the working fluid. In particular, increasing the supply of working fluid within line 404 can reduce the exhaust temperature to a greater extent, as will be described in detail below.
  • heat exchanger 40 to cool the working fluid and lubricant can provide a simpler cooling process and/or a more compact compressor assembly, as only a single heat exchanger can provide secondary cooling of the working fluid and cooling of the lubricant.
  • different heat exchangers may be used to achieve secondary cooling of the working fluid and cooling of the lubricant, respectively.
  • the compressor assembly 1 can (advantageously utilize an expanded working fluid) reduce the temperature of the lubricant that lubricates the compressor.
  • the cooling of the lubricant can be adjusted using a circuit that recools the condensed working fluid.
  • an external cooling medium or cooling source is not required to cool the lubricant.
  • the expanded working fluid can be used to cool the lubricant without secondary cooling of the condensed working fluid line 412, ie, only the lubricant is cooled by the expanded working fluid.
  • the endothermic expanded working fluid is preferably injected into an intermediate pressure position (intermediate pressure chamber) of the compressor 10.
  • the reduction in the temperature of the lubricant prevents or reduces overheating of the suction gas (inhaled working fluid), thereby increasing compressor volumetric efficiency and improving performance.
  • the reduced lubricant temperature improves the reliability of the compressor due to the suction gas and the cooling of the motor, and maintains the ideal
  • the viscosity level is such that a suitable oil film thickness between the moving parts of the compressor is achieved.
  • a line may be machined in the housing 101 to allow lubricant to flow directly from the port 48 to one end of the rotating shaft 106 and/or the low pressure side region.
  • the supply amount of the working fluid flowing through the line 404 or the line 434 can adjust the exhaust temperature of the compressor 10, but also the temperature of the lubricant (injected into the temperature of the compressor).
  • the compressor assembly 1 is provided with the heat exchanger 40 for cooling the lubricant, for some reasons such as malfunction, there is still a case where the lubricant is overheated and the performance of the compressor 1 is lowered.
  • the compressor assembly 1 can actively sense the temperature of the lubricant cooled by the heat exchanger 40 to avoid the above.
  • the refrigeration/heating system 2 can include not only the compressor 10, the expansion device 30, the heat exchanger 40, the first sensing device 50, and the controller 60 (as shown in Figures 1A and 1B, these components constitute the above compression
  • the machine assembly 1) may also include other components such as the condenser 20, the evaporator 81, the main throttle device 82, and the like described above.
  • a control method for the compressor assembly 1 according to an embodiment of the present application can be understood with reference to FIG.
  • a first sensing device 50 for sensing the temperature of the lubricant may be disposed in the compressor assembly 1.
  • the first sensing device 50 is disposed between the heat exchanger 40 and the compressor 10 to intuitively sense the temperature of the lubricant exiting the heat exchanger 40 and/or entering the compressor 10.
  • the first sensing device 50 can alternatively be placed in other suitable locations.
  • the first sensing device 50 can provide a signal indicative of the temperature of the lubricant to the controller 60 via line 650, which will sense the sensed temperature of the lubricant with the desired lubricant temperature.
  • the target value is compared, and when the temperature of the lubricant is greater than the target value of the lubricant temperature, it is considered that the lubricant may be overheated.
  • the controller 60 executes the lubricant temperature control logic.
  • the lubricant temperature control logic can include increasing the flow of working fluid expanded by the expansion device 30 to reduce the temperature of the lubricant flowing through the heat exchanger 40.
  • controller 60 is coupled to motor 32 via line 632, which can be actuated to change the operational state of expansion device 30.
  • Changing the operational state of the expansion device 30 includes, for example, increasing or decreasing the opening of the expansion device 30 to increase or decrease the working fluid flowing through the expansion device 30. Traffic.
  • the controller 60 when the controller 60 confirms that the temperature of the lubricant is less than or equal to the lubricant temperature target value, it is considered that the lubricant may not have an overheating phenomenon. At this time, the controller 60 can execute, for example, the following first control logic or not execute any logic.
  • the first control logic includes jet boost control, i.e., by monitoring (by means of line 601 and sensor 61) the temperature of the expanded working fluid entering heat exchanger 40 (by means of line 602) And sensor 62) monitoring the temperature of the expanded working fluid exiting heat exchanger 40 and/or (by means of line 603 and second sensing means 63) monitoring the exhaust temperature of the working fluid of compressor 10, controlling expansion device 30
  • jet boost control i.e., by monitoring (by means of line 601 and sensor 61) the temperature of the expanded working fluid entering heat exchanger 40 (by means of line 602) And sensor 62) monitoring the temperature of the expanded working fluid exiting heat exchanger 40 and/or (by means of line 603 and second sensing means 63) monitoring the exhaust temperature of the working fluid of compressor 10, controlling expansion device 30
  • the degree of opening to improve the performance of the compressor assembly 1 or the refrigeration/heating system 2 e.g., capacity, efficiency, energy consumption, etc.
  • lubricant temperature target determination operations The above operations may be referred to herein as lubricant temperature target determination operations.
  • the controller 60 may also adjust the opening degree of the expansion device 30 in response to an overheating phenomenon of the exhaust gas temperature.
  • the controller 60 may determine whether the exhaust gas temperature obtained by the second sensing device 63 is greater than the exhaust gas temperature target value, and when the exhaust gas temperature is greater than the exhaust gas temperature target value, it is considered that there may be an exhaust gas temperature Overheating, thus performing exhaust temperature control logic.
  • the exhaust gas temperature control logic includes increasing the flow of working fluid expanded by the expansion device 30 to reduce the exhaust gas temperature (as described above).
  • the second sensing means 63 for sensing the temperature of the exhaust gas may be disposed within the compressor 10 as shown in FIG. 1C or may be disposed between the compressor 10 and the condenser 20 as shown in FIG.
  • the controller 60 executes the above-described lubricant temperature target determination operation or the above-described first control logic.
  • exhaust gas temperature target determination operations The above operations may be referred to herein as exhaust gas temperature target determination operations.
  • embodiments of the present application provide for limiting the lubricant temperature and/or exhaust gas temperature below a particular target value, there are still lubricant temperature and/or exhaust gas temperatures that are increasing due to some cause, such as a fault. The phenomenon. To this end, it is also necessary to set a further higher protection value for the lubricant temperature and/or the exhaust gas temperature to provide an alarm signal to the user even when the lubricant temperature and/or the exhaust gas temperature reach this protection value.
  • Component 1 or compressor 10 is shut down to avoid losses due to compressor failure (eg, due to excessive wear). Preferably, when the shutdown operation is taken Thereafter, the compressor assembly 1 or the compressor 10 may be automatically restarted after a predetermined period of time, or the above-described restarting operation may be performed until further instructions from the user are received.
  • the controller 60 may further determine whether the temperature of the lubricant is greater than a lubricant temperature protection value, wherein the lubricant temperature protection value is greater than the lubricant temperature target value, and when the lubricant temperature is greater than the lubricant temperature protection value Controller 60 can perform lubricant temperature protection logic.
  • the lubricant temperature protection logic can include an alarm operation and/or a shutdown operation. More specifically, when the temperature of the lubricant is greater than the first lubricant temperature protection value, the controller 60 may send an alarm signal to the user, and when the temperature of the lubricant continues to rise to be greater than the higher second lubricant temperature protection value Controller 60 may choose to shut down compressor assembly 1 or compressor 10 for protection.
  • the controller 60 may perform the above-described exhaust gas temperature target determination operation, the above-described lubricant temperature target determination operation, or the above-described first control logic.
  • the above operation may be referred to herein as a lubricant temperature protection judging operation.
  • the controller 60 may further determine whether the exhaust gas temperature is greater than the exhaust gas temperature protection value, wherein the exhaust gas temperature protection value is greater than the exhaust gas temperature target value, The controller 60 may perform exhaust gas temperature protection logic when the exhaust gas temperature is greater than the exhaust gas temperature protection value.
  • the exhaust temperature protection logic may include an alarm operation and/or a shutdown operation. More specifically, when the exhaust gas temperature is greater than the first exhaust gas temperature protection value, the controller 60 may issue an alarm signal to the user, and when the exhaust gas temperature continues to rise to be greater than the higher second exhaust gas temperature protection value, Controller 60 may choose to shut down compressor assembly 1 or compressor 10 for protection.
  • the controller 60 may perform the lubricant temperature protection determination operation, the exhaust gas temperature target determination operation, the lubricant temperature target determination operation, or the first Control logic.
  • exhaust gas temperature protection determination operations The above operations may be referred to herein as exhaust gas temperature protection determination operations.
  • the exhaust gas temperature protection judging operation the lubricant temperature protection judging operation, the exhaust gas temperature target judging operation, the lubricant temperature target judging operation, and the first control logic are in this order Executed, but in other embodiments of the present application, The above-described judgment operations or control logic can be executed in any combination order.
  • control method for the compressor assembly may include only the above-described exhaust gas temperature protection determination operation, lubricant temperature protection determination operation, exhaust gas temperature target determination operation, lubricant temperature target determination operation, and At least one of the control logic determines the operation or control logic and does not necessarily have to include all of the decision operations or control logic.
  • one or more of the above-described decision operations or control logic may be repeated (periodically or irregularly) multiple times.
  • first control logic described herein may include any suitable control logic other than the jet enhancement control logic.
  • the flow direction of the expanded working fluid in the heat exchanger may be opposite to the flow direction of the condensed working fluid and/or lubricant in the heat exchanger.
  • the flow direction may be the same in terms of structural design considerations.
  • the refrigeration/heating system may be not only a refrigeration/heating system including the compressor assembly described herein, but also a compressor, a heat exchanger, and the like, as described herein.
  • a refrigeration/heating system of a first sensing device and a controller wherein the compressor, the heat exchanger, the first sensing device, and the controller are not in the form of components, but are relatively independently presented in the refrigeration/ In the heating system.
  • heat exchanger 40 may also include other types of Heat exchanger.
  • a horizontal scroll compressor has been described as an example of the compressor 10, in other embodiments, it will be appreciated that the compressor 10 may also include a horizontal scroll compressor.
  • Other types of compressors such as reciprocating compressors, rotor compressors, vertical compressors, and the like.
  • lubricating oil is described as an example of a lubricant
  • the lubricants described herein may also include other types of lubricants other than lubricating oils, such as Grease and the like.
  • oil temperature as used in the embodiments of the present application may be limited not only to the temperature of the lubricating oil but also to the lubricant in a broader sense. temperature.
  • references herein to terms such as front, back, left, right, up, and down are used for the purpose of description only, and do not limit the orientation and orientation of the embodiments of the present invention in practical applications.

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  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
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Abstract

L'invention concerne un ensemble compresseur (1), comprenant un compresseur (10) pour comprimer un fluide de travail d'une pression d'admission à une pression de refoulement, un détendeur (30) conçu pour dilater le fluide de travail condensé par un condenseur (20), un échangeur de chaleur (40) conçu pour transférer un agent lubrifiant d'un compresseur de lubrification (10) au fluide de travail dilaté par le dispositif d'expansion (30) de manière à refroidir l'agent lubrifiant et à chauffer le fluide de travail dilaté par le dispositif d'expansion (30), un premier dispositif de détection (50) configuré pour détecter la température de l'agent lubrifiant refroidi par l'échangeur de chaleur (40), et un dispositif de commande configuré pour commander le fonctionnement de l'ensemble compresseur (1) en fonction de la température de l'agent lubrifiant détectée par le premier dispositif de détection (50).
PCT/CN2017/110826 2016-11-16 2017-11-14 Ensemble compresseur et son procédé de commande et système de réfrigération/chauffage Ceased WO2018090894A1 (fr)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110762914A (zh) * 2019-10-25 2020-02-07 青岛海尔空调电子有限公司 控制压缩机加热带的方法

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108954909A (zh) * 2018-09-19 2018-12-07 珠海格力电器股份有限公司 一种热泵系统及其油冷却循环控制方法
US11125482B2 (en) * 2019-05-31 2021-09-21 Trane International Inc. Lubricant quality management for a compressor
US10935293B2 (en) * 2019-06-28 2021-03-02 Trane International Inc. Systems and methods for controlling differential refrigerant pressure

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11182478A (ja) * 1997-12-24 1999-07-06 Kobe Steel Ltd スクリュ冷凍機
CN102721237A (zh) * 2012-06-19 2012-10-10 合肥天鹅制冷科技有限公司 水源回热型高温热泵
CN103080555A (zh) * 2010-08-27 2013-05-01 株式会社日立产机系统 油冷式气体压缩机
CN105042915A (zh) * 2015-07-27 2015-11-11 湖南大学 一种具有油冷却压缩循环与补气增焓循环的制冷系统
CN105115197A (zh) * 2015-08-18 2015-12-02 松下压缩机(大连)有限公司 一种压缩机润滑油冷却系统及其控制方法
CN105324616A (zh) * 2013-06-17 2016-02-10 开利公司 制冷系统的油料回收
CN105526683A (zh) * 2016-02-19 2016-04-27 珠海格力电器股份有限公司 一种空调系统的控制方法及装置
CN105627614A (zh) * 2016-01-25 2016-06-01 珠海格力电器股份有限公司 制冷机组及其控制方法和控制系统

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5669642B2 (ja) * 2011-03-23 2015-02-12 三菱電機株式会社 冷凍装置
KR101606269B1 (ko) * 2014-07-07 2016-03-24 엘지전자 주식회사 공기조화기
CN105091424B (zh) * 2015-09-10 2019-03-12 Tcl空调器(中山)有限公司 空调器、空调器冷媒调节方法及装置

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11182478A (ja) * 1997-12-24 1999-07-06 Kobe Steel Ltd スクリュ冷凍機
CN103080555A (zh) * 2010-08-27 2013-05-01 株式会社日立产机系统 油冷式气体压缩机
CN102721237A (zh) * 2012-06-19 2012-10-10 合肥天鹅制冷科技有限公司 水源回热型高温热泵
CN105324616A (zh) * 2013-06-17 2016-02-10 开利公司 制冷系统的油料回收
CN105042915A (zh) * 2015-07-27 2015-11-11 湖南大学 一种具有油冷却压缩循环与补气增焓循环的制冷系统
CN105115197A (zh) * 2015-08-18 2015-12-02 松下压缩机(大连)有限公司 一种压缩机润滑油冷却系统及其控制方法
CN105627614A (zh) * 2016-01-25 2016-06-01 珠海格力电器股份有限公司 制冷机组及其控制方法和控制系统
CN105526683A (zh) * 2016-02-19 2016-04-27 珠海格力电器股份有限公司 一种空调系统的控制方法及装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110762914A (zh) * 2019-10-25 2020-02-07 青岛海尔空调电子有限公司 控制压缩机加热带的方法

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