EP3961123A1 - Dampfkompressionswärmepumpensystem und verfahren zum betreiben eines dampfkompressionswärmepumpensystems - Google Patents

Dampfkompressionswärmepumpensystem und verfahren zum betreiben eines dampfkompressionswärmepumpensystems Download PDF

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Publication number
EP3961123A1
EP3961123A1 EP20193703.4A EP20193703A EP3961123A1 EP 3961123 A1 EP3961123 A1 EP 3961123A1 EP 20193703 A EP20193703 A EP 20193703A EP 3961123 A1 EP3961123 A1 EP 3961123A1
Authority
EP
European Patent Office
Prior art keywords
compressor
refrigerant
valve
pcm
energy storage
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
EP20193703.4A
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English (en)
French (fr)
Inventor
James Freeman
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.)
Mitsubishi Electric Corp
Mitsubishi Electric R&D Centre Europe BV Netherlands
Original Assignee
Mitsubishi Electric Corp
Mitsubishi Electric R&D Centre Europe BV Netherlands
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 Mitsubishi Electric Corp, Mitsubishi Electric R&D Centre Europe BV Netherlands filed Critical Mitsubishi Electric Corp
Priority to EP20193703.4A priority Critical patent/EP3961123A1/de
Publication of EP3961123A1 publication Critical patent/EP3961123A1/de
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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/072—Intercoolers therefor
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver heat

Definitions

  • a vapour-compression heat pump system and a method for operating a vapour-compression heat pump system is presented.
  • the inventive system and method makes use of a thermal energy storage device which comprises a phase change material to receive and store heat from a superheated refrigerant vapour stream leaving the first compression stage, thereby also cooling the refrigerant close to its saturated vapour temperature, as desired.
  • the system and method have the advantage that they allow a stable operation of the heat pump system.
  • comfort conditions by cooling the indoor space during defrosting of the evaporator are not compromised and heat from the superheated refrigerant vapour exiting the first compression stage does not have to be rejected to an external fluid stream or recovered elsewhere within the cycle, i.e. the COP of the cycle is not limited and costs and complexity of the system and method are low.
  • HVAC Heating, ventilation and air-conditioning
  • Air source heat pump (ASHP) systems use a vapour compression cycle to provide space-heating and domestic hot water, using outdoor ambient air as the heat source.
  • temperature of the evaporator In heating mode the temperature of the evaporator must be lower than the outdoor air to transfer heat into the cycle. In low-ambient temperature conditions, this can cause moisture from the air to condense on the surface of the evaporator, where it freezes forming a layer of ice that inhibits heat transfer. Periodic defrosting of the evaporator is performed in order to melt the ice so that heating operation can resume.
  • RCD reverse cycle defrosting
  • Heat pump systems designed for operation in low-ambient temperatures may incorporate two or more compression stages to deliver high temperatures. Compared to single-stage cycles, cycles with multiple compression stages can provide improved coefficient of performance (COP) at increased pressure ratios with reduced risk of working fluid degradation.
  • COP coefficient of performance
  • intermediate gas cooling is typically implemented between the first and second compression stages. The exhaust gas discharged from the first compression stage is cooled down close to the saturated vapour temperature before undergoing the second compression stage. This in turn also reduces the superheated exhaust gas temperature at the discharge of the second compression stage.
  • US 5,269,151 A discloses a passive defrost system uses a heat-exchanger/storage defrost module containing a thermal storage material such as a phase change material to capture and store low grade, waste heat contained in the liquid refrigerant line of a refrigeration system.
  • a thermal storage material such as a phase change material
  • CN 102 003 853 B discloses a multi-connected unit phase change energy storage hot liquid defrosting system.
  • CN 102 620 493 B discloses a heat pump defrosting system comprising a compressor, a four-way valve, an outdoor machine and an indoor machine, wherein the compressor is respectively connected with the outdoor machine and the indoor machine through the four-way valve and a refrigerant pipeline.
  • EP 3 244 141 A1 discloses a heat pump system including a refrigerant circuit, a compressor driver, and a heat storage means.
  • the prior art suffers two specific and interrelated problems associated with two-stage ASHP systems designed for operation in low-ambient temperature environments: (1) the requirement to provide heat for defrosting of the evaporator, which in RCD systems can result in compromised comfort conditions by cooling the indoor space, and (2) the requirement to remove heat from the superheated refrigerant vapour exiting the first compression stage, which conventionally is either rejected to an external fluid stream (limiting the COP of the cycle) or recovered elsewhere within the cycle (increasing cost and complexity of the system).
  • vapour-compression heat pump system comprising
  • the inventive system makes use of a thermal energy storage device which comprises a phase change material (PCM) to receive and store heat from a superheated refrigerant vapour stream leaving the first compression stage, thereby also cooling the refrigerant close to its saturated vapour temperature, as desired.
  • PCM phase change material
  • Heat is accumulated in the PCM at constant temperature until such a time that evaporator defrosting is required, whereupon it is released to provide heat for the defrosting process. This negates the requirement to extract heat from the internal space heating circuit for the defrosting process, thereby reducing the risk of compromised indoor comfort conditions.
  • the constant phase-change temperature of the PCM assists in providing a stable operating condition of the heat pump, and the thermal energy storage device can be sized and selected with the optimal phase-change temperature for the required heat pump application and operating conditions.
  • the inventive system can be characterized in that, in the heating operation mode, the controller is configured to establish a fluid connection between the thermal energy storage device and the part of the fluid line which is located between the first compressor and the second compressor, wherein the thermal energy storage device preferably comprises a heat exchanger which is configured to receive refrigerant on one side of the heat exchanger.
  • the system can be characterized in that, in the defrosting operation mode, the controller is configured to establish a fluid connection between the thermal energy storage device and the first heat exchange device, preferably a fluid connection in which the refrigerant of the heat pump system is suitable to flow.
  • the system can comprise a first valve, preferably a three-port-valve, which is located, in a flow direction of refrigerant in the refrigerant circuit, upstream of the thermal energy storage device.
  • the controller can be configured to switch the first valve to allow refrigerant to flow from the first compressor to the thermal energy storage device.
  • the controller can be configured to switch the first valve to allow refrigerant to flow from the receiver vessel to the thermal energy storage device.
  • the system can comprise a second valve, preferably a three-port-valve, which is located, in a flow direction of refrigerant in the refrigerant circuit, downstream of the second compressor.
  • the controller can be configured to switch the second valve to allow refrigerant to flow from the second compressor to the first heat exchange device via at least the second heat exchange device, the second expansion device, the receiver vessel and the first expansion device.
  • the controller can be configured to switch the second valve to allow refrigerant to flow from the second compressor to the first heat exchange device.
  • the system can comprise a first bypass fluid line which comprises a non-return valve.
  • the first bypass fluid line especially the non-return valve
  • the first bypass fluid line can allow refrigerant to flow in the first bypass fluid line in a direction from the first heat exchange device to the second expansion device.
  • the system can comprise a second bypass fluid line.
  • the second bypass fluid line especially a switching status of the second valve, can prevent refrigerant from flowing in the second bypass fluid line.
  • the second bypass fluid line especially a switching status of the second valve, can allow refrigerant to flow in the second bypass fluid line from the second compressor to the first heat exchange device.
  • controller of the system can be configured to, when the heat load is reduced in the heating operation mode, charge the phase change material of the thermal energy storage device, switch the first valve to allow refrigerant to flow from the first compressor to the thermal energy storage device (PCM).
  • controller of the system can be configured to, when the heat load is reduced in the heating operation mode, discharge the phase change material of the thermal energy storage device, switch the first valve to allow refrigerant to flow from the receiver vessel to the thermal energy storage device.
  • the phase change material of the thermal energy storage device can have a phase change temperature which is suitable for under floor heating, hot water heating and/or space heating, preferably a phase change temperature in the range of 30 °C to 100 °C.
  • the system can further comprise an additional third heat exchange device which is in thermal connection with a cooling fluid; and a temperature sensor which is located, in a flow direction of refrigerant in the refrigerant circuit, downstream the third heat exchange device (HEX3) and upstream of the second compressor; wherein the controller is configured to receive temperature information from the temperature sensor, and when, during the heating operation,
  • the controller of the system can be configured to, in the heating operation, make refrigerant flow in a direction from the first heat exchange device via at least the first compressor, the thermal energy storage device and/or an additional cooling device, the second compressor, the second heat exchange device, the second expansion device, the receiver vessel, the first expansion device and then back to the first heat exchange device, optionally also from the receiver vessel directly to the second compressor.
  • controller of the system can be configured to, in a defrosting operation, make refrigerant flow from the first heat exchange device via at least the second expansion device, the receiver vessel, the thermal energy storage device and the second compressor back to the first heat exchange device, optionally also from the receiver vessel directly to the second compressor.
  • the controller of the system can be configured to, in a reduced load heating operation and during charging of the phase change material, make refrigerant flow in a direction from the first heat exchange device via at least the first compressor, the thermal energy storage device, the second compressor, the second heat exchange device, the second expansion device, the receiver vessel, the first expansion device and then back to the first heat exchange device, optionally also from the receiver vessel directly to the second compressor.
  • the controller of the system can be configured to, in a reduced load heating operation and during discharging of the phase change material, make refrigerant flow from the receiver vessel via at least the thermal energy storage device, the second compressor, the second heat exchange device, the second expansion device and then back to the receiver vessel, optionally also from the receiver vessel directly to the second compressor.
  • the first compressor of the system can be configured to compress refrigerant from a low pressure to an intermediate pressure and/or the second compressor of the system can be configured to compress refrigerant from an intermediate pressure to a high pressure.
  • the first expansion device and/or second expansion device can be an expansion valve, preferably a linear expansion valve or a turboexpander.
  • the first expansion valve can be configured to expand refrigerant from an intermediate pressure to a low pressure.
  • the second expansion valve can be configured to expand refrigerant from a high pressure to an intermediate pressure.
  • a method for operating a vapour-compression heat pump system comprising the steps
  • the method can be characterized in that a system according to the invention operated.
  • the inventive system and inventive method can relate to air-source heat pump (ASHP) systems, but can also relate to water-source heat pump (WSHP) systems and ground-source heat pump (GSHP) systems, or any heat pump application that has: (1) a high enough temperature lift to require two compression stages; (2) operating conditions in which ice formation may occur at the evaporator, such that periodic defrosting is a requirement.
  • ASHP air-source heat pump
  • WSHP water-source heat pump
  • GSHP ground-source heat pump
  • FIG. 1 shows a schematic drawing of a system according to the invention in a normal heating operation mode.
  • heat is pumped from the outdoor environment at low temperature to the heating circuit at an elevated temperature.
  • the system operates with three pressure levels, a low pressure, a high pressure and an intermediate pressure.
  • Refrigerant working fluid at State A enters HEX 1 where it is evaporated, receiving heat from the ambient air.
  • the vaporised refrigerant exiting HEX 1 at State B is then compressed to the intermediate pressure by COMP 1.
  • Superheated vapour exiting COMP 1 at State C is directed by valve V1 through the PCM vessel where it is cooled, transferring heat to the PCM.
  • the cooled vapour exiting the PCM vessel at State D mixes with saturated vapour exiting the RECEIVER vessel at State H before being compressed to the high pressure by COMP 2.
  • Superheated vapour exiting COMP 2 at State E is directed by valve V2 through HEX 2, where it is cooled and condensed, transferring heat to the heating circuit.
  • Subcooled liquid refrigerant exiting HEX 2 at State F is expanded to the intermediate pressure by LEV 2.
  • the refrigerant exits LEV 2 in a two-phase state at State G and is received in the RECEIVER vessel.
  • Saturated liquid exits the receiver at State I, and enters LEV 1 where it is expanded to the low pressure and exits at State A.
  • FIG. 2 shows a schematic drawing of a system according to the invention in a defrost operation mode.
  • stored heat is pumped from the PCM to melt the build-up of ice on HEX 1. Due to the smaller temperature lift required between the heat source and heat load in this operating mode, the first compression stage is bypassed.
  • the position of valves V1 and V2 change so that COMP 1, LEV 1 and HEX 2 are bypassed.
  • Refrigerant working fluid at State A is directed to the PCM vessel by valve V1 where it is evaporated, receiving heat from the PCM.
  • the vaporised refrigerant exiting the PCM vessel at State B mixes with saturated vapour exiting the RECEIVER vessel at State F before being compressed to the high pressure by COMP 2.
  • Superheated vapour exiting COMP 2 at State C is directed by valve V2 to HEX 1, where it is cooled and condensed, transferring heat to the ice layer on the fins which proceeds to melt.
  • Liquid refrigerant exiting HEX 1 at State D flows in the permitted direction through the NRV before being expanded to the low pressure by LEV 2.
  • Figures 3 and 4 show a schematic drawing of a system according to the invention in a heating operation mode under reduced load and PCM charging ( Figure 3 ) and discharging ( Figure 4 ).
  • Figure 3 shows the principle operation in a reduced-load case where outdoor ambient temperature is high enough that there is no build-up of ice on the evaporator and thus periodic defrosting not required. Under this condition, the system primarily operates in its normal configuration, as shown in Figure 3 (identical to Figure 1 ). Heat is stored in the PCM despite there being no requirement for defrosting of HEX 1. To make use of the stored heat in the PCM, the system periodically switches configuration to the alternative heating operation mode shown in Figure 4 .
  • the PCM vessel now serves as the heat source and the system operates using only one compression stage until the PCM is fully discharged (frozen).
  • the position of valve V1 changes so that HEX 1, COMP 1 and LEV 1 are bypassed.
  • saturated liquid working fluid at State A is directed to the PCM vessel by valve V1 where it is evaporated, receiving heat from the PCM.
  • the vaporised refrigerant exiting the PCM vessel at State B mixes with saturated vapour exiting the RECEIVER vessel at State F before being compressed to the high pressure by COMP 2.
  • Superheated vapour exiting COMP 2 at State C is directed by valve V2 to HEX 2 where it is cooled and condensed, transferring heat to the heating circuit.
  • Liquid refrigerant exiting HEX 2 is expanded to the low pressure by LEV 2.
  • the refrigerant exits LEV 2 in a two-phase state at State E and is received in the RECEIVER vessel. Saturated liquid exits the receiver at State A.
  • FIG 5 shows a schematic drawing of a system according to the invention comprising a third heat exchange device for inter-stage cooling from an external fluid stream.
  • cooling of the superheated refrigerant vapour prior to the second compression stage can be provided by an external fluid stream, via an additional heat exchanger installed in parallel with the PCM vessel.
  • additional heat exchanger HEX 3

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP20193703.4A 2020-08-31 2020-08-31 Dampfkompressionswärmepumpensystem und verfahren zum betreiben eines dampfkompressionswärmepumpensystems Pending EP3961123A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP20193703.4A EP3961123A1 (de) 2020-08-31 2020-08-31 Dampfkompressionswärmepumpensystem und verfahren zum betreiben eines dampfkompressionswärmepumpensystems

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20193703.4A EP3961123A1 (de) 2020-08-31 2020-08-31 Dampfkompressionswärmepumpensystem und verfahren zum betreiben eines dampfkompressionswärmepumpensystems

Publications (1)

Publication Number Publication Date
EP3961123A1 true EP3961123A1 (de) 2022-03-02

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Application Number Title Priority Date Filing Date
EP20193703.4A Pending EP3961123A1 (de) 2020-08-31 2020-08-31 Dampfkompressionswärmepumpensystem und verfahren zum betreiben eines dampfkompressionswärmepumpensystems

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EP (1) EP3961123A1 (de)

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