WO2024250179A1 - Pompe à chaleur à super-haute température - Google Patents

Pompe à chaleur à super-haute température Download PDF

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Publication number
WO2024250179A1
WO2024250179A1 PCT/CN2023/098708 CN2023098708W WO2024250179A1 WO 2024250179 A1 WO2024250179 A1 WO 2024250179A1 CN 2023098708 W CN2023098708 W CN 2023098708W WO 2024250179 A1 WO2024250179 A1 WO 2024250179A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
suction
compressor
evaporator
adjust valve
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.)
Pending
Application number
PCT/CN2023/098708
Other languages
English (en)
Inventor
Wuchao WANG
Xiaorui YU
Qingxuan ZHAO
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Trane Air Conditioning Systems China Co Ltd
Trane International Inc
Original Assignee
Trane Air Conditioning Systems China Co Ltd
Trane International Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Trane Air Conditioning Systems China Co Ltd, Trane International Inc filed Critical Trane Air Conditioning Systems China Co Ltd
Priority to PCT/CN2023/098708 priority Critical patent/WO2024250179A1/fr
Publication of WO2024250179A1 publication Critical patent/WO2024250179A1/fr
Anticipated expiration legal-status Critical
Pending legal-status Critical Current

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Classifications

    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and 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
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
    • 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

Definitions

  • This disclosure relates generally to a super-high temperature heat pump. More specifically, the disclosure relates to a super-high temperature heat pump to provide hot water with a heat source.
  • a heating, ventilation, air conditioning, and refrigeration (HVACR) system may include a heat pump to provide hot water with a heat source.
  • a refrigerant flows through an evaporator and absorbs heat from the heat source to change to a low-pressure refrigerant which can be applied to a compressor.
  • the refrigerant from the compressor flows through a condenser and rejects heat to a process fluid (e.g., water) to provide the hot water.
  • a process fluid e.g., water
  • HVAC heating, ventilation, air conditioning, and refrigeration
  • Embodiments disclosed herein provide HVACR systems including a super-high temperature heat pump to provide hot water (e.g., at or over 120 °C) or steam with a heat source (e.g., at or over 40 °C) .
  • Embodiments described herein can improve the reliability, stability and efficiency of a super-high temperature heat pump, by addressing issues including, for example, wet compression and/or low suction/discharge superheat when the system is in a starting stage, and oil viscosity in a stable running stage.
  • HVACR heating, ventilation, air conditioning and refrigeration
  • the HVACR system includes a refrigeration circuit including an evaporator, a compressor, an expansion device, and a condenser to operate a refrigerant therein, and a suction adjust valve fluidly connecting an outlet of the evaporator to a suction port of the compressor.
  • the suction adjust valve is configured to control a refrigerant flow from the outlet of the evaporator to the suction port of the compressor.
  • the system further includes a controller configured to monitor at least one of (i) a pressure difference at the expansion device and (ii) a refrigerant superheat downstream of the suction adjust valve, and adjust the suction adjust valve to control a refrigerant pressure drop from the outlet of the evaporator to the suction port of the compressor based on a result of the monitoring.
  • the present disclosure describes a method of controlling a heating, ventilation, air conditioning and refrigeration (HVACR) system including a refrigeration circuit including an evaporator, a compressor, an expansion device, and a condenser to operate a refrigerant therein.
  • the method includes fluidly connecting, via a suction adjust valve, an outlet of the evaporator to a suction port of the compressor.
  • the suction adjust valve is configured to control a refrigerant flow from the evaporator to the suction port of the compressor.
  • the method further includes monitoring at least one of (i) a pressure difference at the expansion device and (ii) a refrigerant superheat downstream of the suction adjust valve, and adjusting the suction adjust valve to control a refrigerant pressure drop from the outlet of the evaporator to the suction portion of the compressor based on a result of the monitoring.
  • FIG. 1 illustrates a schematic diagram of a refrigerant circuit, which may be implemented in an HVACR system, according to an embodiment.
  • FIG. 2 is a schematic diagram of a control system, according to an embodiment.
  • FIG. 3 is a schematic diagram of a super-high temperature heat pump, according to an embodiment.
  • FIG. 4 is a flow diagram of a method for controlling a heat pump, according to an embodiment.
  • FIG. 5 is a flow diagram of a method for controlling a heat pump in a starting stage or mode change stage, according to an embodiment.
  • FIG. 6 is a flow diagram of a method for controlling a re-heater of a heat pump, according to an embodiment.
  • FIG. 7 is a flow diagram of a method for controlling oil cooling and refrigerant superheat in a heat pump, according to an embodiment.
  • suction superheat may refer to a temperature difference between the temperature of refrigerant vapor at a suction line of a compressor and its saturation temperature at the corresponding suction pressure. It can be used as a parameter to evaluate and control the performance of a HVAC system. Suction superheat can be measured using temperature sensors placed at the suction line of the compressor. The measured temperature can be compared to the saturation temperature corresponding to the suction pressure to determine the temperature difference (i.e., superheat) .
  • discharge superheat may refer to a temperature difference between the temperature of refrigerant vapor at a discharge line of a compressor and its saturation temperature at the corresponding discharge pressure. It can be used as a parameter to evaluate and control the performance of a HVACR system. Discharge superheat can be measured using temperature sensors placed at the discharge line of the compressor. The measured temperature can be compared to the saturation temperature corresponding to the discharge pressure to determine the temperature difference (i.e., superheat) .
  • thermosyphon or “thermosyphon device” may refer to a passive heat exchange mechanism that is charged by a working fluid (e.g., a refrigerant such as hydrofluorocarbon (HFC) or haloalkane refrigerant, e.g., R-134a) .
  • a working fluid e.g., a refrigerant such as hydrofluorocarbon (HFC) or haloalkane refrigerant, e.g., R-134a
  • the working fluid flows (e.g., via its own gravity) into the heat exchange mechanism, receives heat from a process fluid at a relatively higher temperature (e.g., an oil from an oil separator) , evaporates and exits the heat exchange mechanism (e.g., by means of a pressure gradient) .
  • a thermosyphon device may include a brazed plate (BP) heat exchanger.
  • BP brazed plate
  • Embodiments described herein can maintain the suction superheat at a desired level for the efficient and reliable operation of the compressor and the refrigeration system.
  • a correct suction/discharge superheat can prevent refrigerant liquid from entering/leaving the compressor, and the so-called “wet compression, ” which may cause damage to the compressor and/or reduce efficiency or reliability of the system.
  • Embodiments disclosed herein provide HVACR systems including a super-high temperature heat pump.
  • Embodiments described herein can apply a low pressure refrigerant to a compressor to provide hot water (e.g., at or over 120 °C) or steam with a heat source (e.g., at or over 40 °C) .
  • a low pressure refrigerant may have a relative low pressure at a given saturated temperature, such as, for example, R245fa, and R1233zdE (E) .
  • R410A is an exemplary high pressure refrigerant.
  • R134a is an exemplary middle pressure refrigerant.
  • Embodiments described herein can improve the reliability, stability and efficiency of a super-high temperature heat pump, by addressing issues including, for example, wet compression and/or low suction/discharge superheat when the system is in a starting stage or a transition stage, and oil viscosity in a stable running stage.
  • Startting stage may refer to the initial phase of a refrigeration system (e.g., a heat pump) when it is turned on or restarted after a shutdown. During the starting stage, the compressor is started to begin the circulation of working fluid (e.g., refrigerant) in the refrigeration system.
  • working fluid e.g., refrigerant
  • “Stable running stage” may refer to the phase of which the refrigeration system operates at its intended and relatively steady state conditions. After the system goes through the starting stage, the system may enter the stable running stage.
  • Transport stage may refer to the phase of a refrigeration system when there are relatively obvious/dramatic changes in operating conditions/states or system requirements.
  • the system may be in a transition stage when the refrigeration system changes its operation mode (e.g., from a heating mode to a cooling mode) , or when the temperature of a process fluid dramatically changes (e.g., water temperature changes from 70 °C to 100 °C) .
  • a refrigeration system e.g., a heat pump
  • Running parameters such as, e.g., pressure, temperature, etc., in a stable running stage are relatively stable. That is, while the running parameters in the stable running stage may change or fluctuate, they are not as dramatic as in a starting stage and/or a transition stage.
  • FIG. 1 is a schematic diagram of a refrigerant circuit 100, according to an embodiment.
  • the refrigerant circuit 100 includes a compressor 120, a condenser 140, an expansion device 160, and an evaporator 180.
  • the refrigerant circuit 100 may also include a controller (e.g., controller 145 of FIG. 2) configured to control the operations of the compressor 120, the condenser 140, the expansion device 160, the evaporator 180, and/or other circuit components of the refrigerant circuit 100.
  • controller e.g., controller 145 of FIG. 2
  • the refrigerant circuit 100 can generally be applied in a variety of systems used to control an environmental condition (e.g., temperature, humidity, air quality, or the like) in a conditioned space.
  • the refrigerant circuit 100 can be applied to produce cold/hot fluid (e.g., water) .
  • the conditioned space can be a space within an office building, a commercial building, a factory, a laboratory, a data center, a residential building, or the like.
  • the refrigerant circuit 100 can be configured to be a cooling system (e.g., an air conditioning system) capable of operating in a heating mode or a cooling mode.
  • the refrigerant circuit 100 can be configured to be a heat pump that can operate in a heating mode. It is appreciated that the refrigerant circuit 100 can be configured to operate in a heating mode and switch to a cooling mode, or operate in a cooling mode and switch to a heating mode.
  • the compressor 120, the condenser 140, the expansion device 160, and the evaporator 180 can be fluidly connected.
  • An “expansion device” as described herein may also be referred to as an expander.
  • the expansion device 160 can be an expansion valve, expansion plate, expansion vessel, orifice, or the like, or other such types of expansion mechanisms. It should be appreciated that the expansion device 160 may be any suitable type of expansion device used in the field for expanding a working fluid to cause the working fluid to decrease in pressure and temperature.
  • the refrigerant circuit 100 is an example and can be configured to include more or less components.
  • the refrigerant circuit 100 can include other components such as, but not limited to, an economizer heat exchanger, one or more flow control devices (e.g., a valve, a pump, etc. ) , a receiver tank, a dryer, a suction-liquid heat exchanger (e.g., a reheater) , or the like.
  • the refrigerant circuit 100 can operate according to generally known principles.
  • the refrigerant circuit 100 can be configured to heat and/or cool a liquid process fluid.
  • the liquid process fluid can be a heat transfer fluid or medium (e.g., a liquid such as, but not limited to, water or the like) .
  • the refrigerant circuit 100 may be generally representative of a liquid chiller system.
  • the refrigerant circuit 100 can alternatively be configured to heat and/or cool a gaseous process fluid (e.g., a heat transfer medium or fluid (e.g., a gas such as, but not limited to, air or the like) , in which case the refrigerant circuit 100 may be generally representative of an air conditioner and/or heat pump.
  • a gaseous process fluid e.g., a heat transfer medium or fluid (e.g., a gas such as, but not limited to, air or the like)
  • the refrigerant circuit 100 may be generally representative of an air conditioner and/or heat pump.
  • the refrigerant circuit 100 can operate as a vapor-compression circuit such that the compressor 120 compresses a working fluid (e.g., a heat transfer fluid such as, but not limited to, refrigerant or the like) from a relatively lower pressure gas to a relatively higher-pressure gas.
  • a working fluid e.g., a heat transfer fluid such as, but not limited to, refrigerant or the like
  • the relatively higher-pressure gas is at a relatively higher temperature, being discharged from the compressor 120 and flowing through the condenser 140.
  • the working fluid flows through the condenser 140 and rejects heat to the process fluid (e.g., water, air, etc. ) , thereby cooling the working fluid.
  • the process fluid can be water which is heated to provide hot water, for example, over 120 °C water (steam) .
  • the cooled working fluid which is now in a liquid form, flows to the expansion device 160 that can reduce the pressure of the working fluid. As a result, a portion of the working fluid is converted to a gaseous form.
  • the working fluid which is now in a mixed liquid and gaseous form flows to the evaporator 180.
  • the working fluid flows through the evaporator 180 and absorbs heat from the process fluid (e.g., a heat transfer medium such as, but not limited to, water, a solution, air, etc. ) , heating the working fluid, and converting it to a gaseous form.
  • the process fluid is water with a temperature, for example, at or over 40 °C.
  • the process fluid (e.g., water at or over 40 °C) works as a heat source to evaporate the working fluid.
  • the gaseous working fluid then returns to the compressor 120.
  • the above-described process continues while the heat transfer circuit is operating, for example, in a heating mode to provide hot water or steam (e.g., while the compressor 120 is enabled) .
  • the refrigerant circuit 100 can be configured to operate as a free cooling/heating circuit to control one or more environmental conditions of the conditioned space.
  • a free cooling/heating circuit can include a first heat exchanger and a second heat exchanger fluidly connected by a working fluid.
  • the first and second heat exchangers of the free cooling/heating circuit can be dedicated heat exchangers in addition to the refrigeration circuit 100 having the compressor 120, the condenser 140, the expansion device 160, and the evaporator 180.
  • the first and second heat exchangers can share, for example, the condenser 140 and the evaporator 180 such that the refrigeration circuit 100 can operate as a free cooling/heating circuit or a vapor compression circuit.
  • the first heat exchanger can exchange thermal energy between a working fluid and an ambient fluid (e.g., outdoor air) .
  • the first exchanger can be disposed in a location suitable to exchange thermal energy with the ambient fluid.
  • the location can include a rooftop of the conditioned space.
  • the second heat exchanger can be the evaporator 180 to exchange thermal energy between the working fluid and fluid in the conditioned space. Fluid in the conditioned space can, for example, be indoor air.
  • the first heat exchanger can be the condenser 140.
  • the first heat exchanger can release thermal energy to the ambient fluid and cool the working fluid.
  • a pump can move the cooled working fluid to the second heat exchanger to exchange thermal energy with the fluid in the conditioned space, heating the working fluid to be cooled by the ambient fluid again.
  • the ambient fluid in a cooling operation, can have a temperature lower than the temperature of the fluid in the conditioned space.
  • the pump can circulate the working fluid between the first and the second heat exchangers to move thermal energy from the ambient fluid to the fluid in the conditioned space.
  • the ambient fluid in a heating operation, can have a temperature higher than the temperature of the fluid in the conditioned space.
  • the working fluid can be any heat transfer fluid such as a refrigerant, water, a water solution, glycol fluid, or the like.
  • FIG. 2 illustrates a schematic diagram of a control system 130, according to an embodiment.
  • the control system 130 includes a controller 145 configured to control a suction adjust valve 190 such as, for example, a suction adjust valve 350 in a refrigerant circuit 300 of FIG. 3.
  • the suction adjust valve 190 is controlled by the controller 145 and configured to control a refrigerant pressure drop from an outlet of an evaporator (e.g., evaporator 350 of FIG. 3) to a suction port of a compressor (e.g., compressor 310 of FIG. 3) to obtain a desired/required pressure difference between a suction port and a discharge port of the compressor.
  • a compressor e.g., compressor 310 of FIG.
  • the controller 145 can receive various sensing data from sensor (s) 182 distributed in a HVACR system and generate control signals based on the received sensing data.
  • the sensor (s) 182 may include, for example, temperature sensor (s) , pressure sensor (s) , etc.
  • the sensors can be located at various locations of a refrigeration system.
  • the controller 145 is generally representative of hardware aspects of a controller for the refrigerant circuit 100 (FIG. 1) .
  • the controller 145 is an example and is not intended to be limiting.
  • the controller 145 includes a processor 150, a memory 155, input/output 175, and storage 165. It is to be appreciated that the controller 145 can include one or more additional components.
  • the processor 150 can retrieve and execute programming instructions stored in the memory 155 and/or the storage 165.
  • the processor 150 can also store and retrieve application data residing in the memory 155.
  • the processor 150 can be a single processor, multiple processors, co-processors, or a single processor having multiple processing cores.
  • the processor 150 can be a single-threaded processor.
  • the processor 150 can be a multi-threaded processor.
  • the memory 155 is generally included to be representative of a random access memory such as, but not limited to, Static Random Access Memory (SRAM) , Dynamic Random Access Memory (DRAM) , Flash, suitable combinations thereof, or the like.
  • SRAM Static Random Access Memory
  • DRAM Dynamic Random Access Memory
  • Flash suitable combinations thereof, or the like.
  • the memory 155 can be a volatile memory.
  • the memory 155 can be a non-volatile memory.
  • aspects described herein can be embodied as a system, method, or computer readable medium.
  • the aspects described can be implemented in hardware, software (including firmware or the like) , or combinations thereof.
  • Some aspects can be implemented in a computer readable medium, including computer readable instructions for execution by a processor. Any combination of one or more computer readable medium (s) can be used.
  • the computer readable medium can include a computer readable signal medium and/or a computer readable storage medium.
  • a computer readable storage medium can include any tangible medium capable of storing a computer program for use by a programmable processor to perform functions described herein by operating on input data and generating an output.
  • a computer program is a set of instructions that can be used, directly or indirectly, in a computer system to perform a certain function or determine a certain result.
  • Examples of computer readable storage media include, but are not limited to, a floppy disk; a hard disk; a random access memory (RAM) ; a read-only memory (ROM) ; a semiconductor memory device such as, but not limited to, an erasable programmable read-only memory (EPROM) , an electrically erasable programmable read-only memory (EEPROM) , Flash memory, or the like; a portable compact disk read-only memory (CD-ROM) ; an optical storage device; a magnetic storage device; other similar device; or suitable combinations of the foregoing.
  • a computer readable signal medium can include a propagated data signal having computer readable instructions. Examples of propagated signals include, but are not limited to, an optical propagated signal, an electro-magnetic propagated signal, or the like.
  • a computer readable signal medium can include any computer readable medium that is not a computer readable storage medium that can propagate a computer program for use by a programmable processor to perform functions described herein by operating on input data and generating an output.
  • FIG. 3 is a schematic diagram of a refrigerant circuit 300 which can be a super-high temperature heat pump implemented in an HVACR system, according to an embodiment.
  • the heat pump 300 includes a refrigeration circuit including a compressor 310, an evaporator 320, an expansion device 330, and a condenser 340 to operate a working fluid (e.g., a refrigerant) therein.
  • a working fluid e.g., a refrigerant
  • the compressor 310 may include a compression mechanism and a motor.
  • the compressor 310 may include a suction adjust valve (e.g., suction adjust valve 350) at an inlet (i.e., suction port 310a) to control the flow of refrigerant vapor into the compressor 310, and a discharge check valve at an outlet (i.e., discharge port 310b) to prevent a backward flow when the refrigerant circuit is shutting down.
  • a suction adjust valve e.g., suction adjust valve 350
  • suction adjust valve e.g., suction adjust valve 350
  • a discharge check valve at an outlet (i.e., discharge port 310b) to prevent a backward flow when the refrigerant circuit is shutting down.
  • One or more pressure sensors and temperature sensors can be disposed at or adjacent to the discharge port 310b to measure refrigerant pressures and temperatures.
  • the compressor 310 is a screw compressor. It is to be understood that the compressor 310 can be any suitable types
  • the compressor 310 may also include an oil system to provide lubrication to reduce friction and wear between moving parts.
  • An oil separator 315 is connected, via the discharge line 313, to the compressor 310 to separate oil from the refrigerant vapor.
  • the separated oil is returned to the compressor 310 via a thermosyphon circuit to cool down the oil, which will be described further below.
  • the refrigerant vapor then proceeds to the condenser 340 and rejects heat to the process fluid, thereby cooling the refrigerant.
  • the process fluid is water which enters the condenser 340 via an inlet 341, and the heated water exits the condenser 340 via an outlet 343.
  • the water can be heated to a temperature, for example, at or over 120 °C.
  • the hot water can be injected to a flash tank (not shown) to generate water steam.
  • the inlet 341 and the outlet 343 may each include a temperature sensor to measure the respective water temperatures.
  • the cooled refrigerant liquid then flows to the expansion device 330 that can reduce the pressure of the refrigerant and may convert the refrigerant liquid into a mixed liquid and gaseous form flowing to the evaporator 320.
  • the refrigerant flows through the evaporator 320 and absorbs heat from the process fluid, which heats the working fluid, and converts it to a gaseous form.
  • the gaseous refrigerant then exits the evaporator 320 via an outlet 320a.
  • the process fluid is water which enters the evaporator 320 via an inlet 321, and acts as a heat source for the refrigerant in the evaporator 320.
  • the cooled water exits the evaporator 320 via an outlet 323.
  • the inlet 321 and the outlet 323 may each include a temperature sensor to measure the respective water temperatures.
  • the heat source e.g., water
  • the heat source may have a temperature, for example, at or over 40 °C, or from about 40 °C to about 85 °C.
  • the process fluid for the evaporator 320 may be any suitable process fluid other than water as the heat source.
  • the choice of a process fluid may depend on various factors such as, for example, the load of the system (e.g., the desired amount of hot water or steam provided at the condenser 340) .
  • water with a temperature at or over 40 °C e.g., from about 40 °C to about 85 °C
  • any tonnage chiller for providing/generating any desired amount of hot water or steam.
  • a suction adjust valve 350 fluidly connects the outlet 320a of the evaporator 320 to the suction port 310a of the compressor 310.
  • the suction adjust valve 350 is configured to control a refrigerant flow from the outlet 320a of the evaporator 320 to the suction port 310a of the compressor 310.
  • the suction adjust valve 350 can be any type of valves capable of controlling the refrigerant flow, including, for example, a butterfly valve, a solenoid valve, a ball valve, etc.
  • the suction adjust valve 350 may regulate the refrigerant flow continuously or at discrete level (s) between a fully open state and a fully closed state.
  • a butterfly valve may regulate the flow of fluids by adjusting among multiple states including, for example, a fully opened state to allow the maximum flow, a fully closed state to completely shut off the flow, and one or more partially closed/opened states between the fully opened state and the fully closed state.
  • the heat pump 300 further includes a re-heater 370 configured to conduct and control a heat exchange between the refrigerant liquid at a relatively higher temperature from the condenser 340 and the refrigerant vapor at a relatively lower temperature from the suction adjust valve 350.
  • the re-heater 370 may include any suitable type of heat exchanger to conduct the heat exchange.
  • the high-temperature refrigerant liquid leaving the condenser 340 is directed to the heat exchanger or re-heater 370.
  • the low-temperature refrigerant vapor from the evaporator 320 is also directed into the heat exchanger or re-heater 370.
  • a refrigerant bypass valve 332 is provided between the condenser 340 and the re-heater 370 to control a flow of the high-temperature refrigerant liquid from the condenser 340 to the re-heater 370.
  • the controller can instruct an operation of the refrigerant bypass valve 332 to control the amount of high-temperature refrigerant liquid from the condenser 340 to pass through the re-heater 370.
  • the controller can instruct an operation of the bypass valve 332 to allow more/less high-temperature refrigerant liquid to pass through the re-heater 370 to heat the low-temperature refrigerant vapor via the re-heater 370. Doing so can increase/decrease the refrigerant suction superheat at the suction port 310a of the compressor 310.
  • the heat pump 300 further includes a thermosyphon circuit to conduct and control a heat exchange at least between (i) the oil from the oil separator 315 and the refrigerant liquid from the evaporator 320, and (ii) the oil from the oil separator 315 and the refrigerant liquid from the condenser 340.
  • the thermosyphon circuit can provide a staged cooling to the oil from the oil separator 315.
  • the thermosyphon circuit includes a condenser thermosyphon 362 as a heat exchanger between the oil from the oil separator 315 and the refrigerant liquid from the condenser 340 to cool down the oil from the separator 315.
  • the evaporated refrigerant returns to the condenser 340.
  • the thermosyphon circuit further includes an evaporator thermosyphon 364 as a heat exchanger between the oil from the condenser thermosyphon 362 and the refrigerant liquid from the evaporator 320.
  • the refrigerant liquid is directed from the evaporator 320 via a liquid line 356 to flow through the evaporator thermosyphon 364 and absorb heat from the oil from the condenser thermosyphon 362 to further cool down the oil.
  • the evaporated refrigerant is directed from the evaporator thermosyphon 364 to the suction port 310a of the compressor 310 via a vent line 365.
  • the oil bypass valve 367 allows a portion of the oil from the condenser thermosyphon 362 to pass through the evaporator thermosyphon 364 to maintain the corresponding refrigerant superheat in a desired range (e.g., between about 0 °F and about 50 °F) .
  • a control valve 368 is provided at the vent line 365 to control the refrigerant flow from the evaporator thermosyphon 364 to the suction port 310a of the compressor 310.
  • the controller can monitor the refrigerant pressure difference between the suction port 310a and the evaporator 350, i.e., a refrigerant pressure drop from the outlet 320a of the evaporator 320 to the suction port 310a of the compressor 310, and adjust the control valve based on results of the monitoring.
  • One or more pressure sensors can be provided at the outlet 320a and the suction port 310a to measure refrigerant pressures.
  • the control valve 368 can be controlled to coordinate with the operation of suction adjust valve 350.
  • the controller can instruct the control valve 368 to operate to decrease the valve opening to prevent too much liquid refrigerant flow entering into the compressor 310.
  • the level of the valve opening may be determined based on the monitored refrigerant pressure difference.
  • the heat pump 300 may include one or more heaters installed at one or more of components of the heat pump 300 including, for example, the oil separator 315, a discharge cavity of the compressor 310, a motor cavity of the compressor 310, a suction line or port 310a of the compressor 310, etc.
  • the controller can monitor a component temperature of the heat pump 300, for example, a motor temperature of the compressor 310.
  • a predetermined threshold e.g. 60 °C to 80 °C
  • the controller can instruct one or more of the heaters to heat the relevant components to prevent refrigerant migration and condensing in the compressor 310 and the oil separator 315.
  • the flowchart 700 may include one or more operations, actions, or functions depicted by one or more blocks 705, 710, 720, 730, 740, 745, and 750. Although illustrated as discrete blocks, various blocks may be divided into additional blocks, combined into fewer blocks, or eliminated, depending on the desired implementation. In an embodiment, the method 700 can be performed by the control system 130 of FIG. 2, or any other suitable control systems or controllers.
  • a refrigeration circuit including an evaporator, a compressor, an expansion device, and a condenser to operate a refrigerant therein;
  • a suction adjust valve fluidly connecting an outlet of the evaporator to a suction port of the compressor, the suction adjust valve being configured to control a refrigerant flow from the outlet of the evaporator to the suction port of the compressor;
  • a controller configured to:
  • Aspect 3 The system of Aspect 1 or 2, wherein the controller is further configured to:
  • Aspect 14 The method of any one of Aspects 11-13, further comprising:
  • Aspect 15 The method of any one of Aspects 11-14, further comprising:
  • Aspect 17 The method of any one of Aspects 11-16, further comprising conducting, via a re-heater, a heat exchange between a controlled amount of refrigerant from the condenser and the refrigerant from the evaporator.
  • Aspect 18 The method of any one of Aspects 11-17, further comprising conducting, via a thermosyphon circuit, a heat exchange between a controlled amount of oil from the compressor and a refrigerant liquid from the evaporator to vaporize the liquid refrigerant to a refrigerant vapor.
  • Aspect 20 The method of Aspect 19, further comprising at least partially closing the control valve upon a detection of the suction adjust valve being at a partially closed state.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

Un système de chauffage, de ventilation, de climatisation et de réfrigération (HVACR) comprend une soupape de réglage d'aspiration reliant de manière fluidique une sortie de l'évaporateur à un orifice d'aspiration du compresseur. La soupape de réglage d'aspiration est destinée à commander un flux de réfrigérant entre la sortie de l'évaporateur et l'orifice d'aspiration du compresseur, et à commander une chute de pression de réfrigérant sur la base d'un résultat de surveillance (i) d'une différence de pression de réfrigérant au niveau du dispositif d'expansion et/ou (ii) d'une surchauffe de réfrigérant en aval de la soupape de réglage d'aspiration.
PCT/CN2023/098708 2023-06-06 2023-06-06 Pompe à chaleur à super-haute température Pending WO2024250179A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/CN2023/098708 WO2024250179A1 (fr) 2023-06-06 2023-06-06 Pompe à chaleur à super-haute température

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CN2023/098708 WO2024250179A1 (fr) 2023-06-06 2023-06-06 Pompe à chaleur à super-haute température

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WO2024250179A1 true WO2024250179A1 (fr) 2024-12-12

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CN108474598A (zh) * 2016-02-19 2018-08-31 三菱重工制冷空调系统株式会社 制冷机及其控制方法
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