EP3835687A1 - Pompe à chaleur - Google Patents

Pompe à chaleur Download PDF

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Publication number
EP3835687A1
EP3835687A1 EP20206234.5A EP20206234A EP3835687A1 EP 3835687 A1 EP3835687 A1 EP 3835687A1 EP 20206234 A EP20206234 A EP 20206234A EP 3835687 A1 EP3835687 A1 EP 3835687A1
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EP
European Patent Office
Prior art keywords
refrigerant
usage
heat exchanger
side heat
temperature
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
EP20206234.5A
Other languages
German (de)
English (en)
Inventor
Tsuneko Imagawa
Yuki YAMAOKA
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.)
Panasonic Intellectual Property Management Co Ltd
Original Assignee
Panasonic Intellectual Property Management Co Ltd
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 Panasonic Intellectual Property Management Co Ltd filed Critical Panasonic Intellectual Property Management Co Ltd
Publication of EP3835687A1 publication Critical patent/EP3835687A1/fr
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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary 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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser 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
    • F25B2700/17—Speeds
    • F25B2700/171—Speeds 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
    • F25B2700/21—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
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser

Definitions

  • the present invention relates to a heat pump system whose a high-pressure side is operated under supercritical pressure.
  • the refrigerant circuit uses refrigerant whose a high-pressure side becomes supercritical pressure, and the refrigerant circuit is formed by annularly connecting, to one another through a pipe, a two-stage compressing type compressor, a heating heat exchanger which heats hot water, a cooler, a first electric expansion valve and an evaporator.
  • the intermediate injection circuit branches off from the refrigerant circuit between the heating heat exchanger and the cooler.
  • the intermediate injection circuit includes a second electric expansion valve and the cooler in the middle of the refrigerant circuit.
  • the intermediate injection circuit returns a portion of refrigerant discharged from the heating heat exchanger to an intermediate portion between a low-pressure side and a high-pressure side of the compressor.
  • This refrigeration cycle device includes a first temperature detection sensor which detects high-pressure side refrigerant discharge temperature of the compressor, a second temperature detection sensor which detects refrigerant temperature of an outlet of the heating heat exchanger, and a third temperature detection sensor which detects refrigerant temperature of an outlet of the cooler.
  • a first temperature detection sensor which detects high-pressure side refrigerant discharge temperature of the compressor
  • a second temperature detection sensor which detects refrigerant temperature of an outlet of the heating heat exchanger
  • a third temperature detection sensor which detects refrigerant temperature of an outlet of the cooler.
  • Patent Document 1 Japanese Patent Application Laid-open No. 2008-008499
  • the present invention is achieved to solve the conventional problem, and it is an object of the invention to provide a heat pump system in which even if temperature of usage-side heat medium which flows into a usage-side heat exchanger rises, a high-pressure side which suppresses deterioration of COP is operated under supercritical pressure by performing appropriate control.
  • the present invention provides a heat pump system including: a main refrigerant circuit formed by sequentially connecting, through a pipe, a compression mechanism composed of a compression rotation element, a usage-side heat exchanger for heating usage-side heat medium by refrigerant which is discharged from the compression rotation element and which exceeds critical pressure, an intermediate heat exchanger, a first expansion device, and a heat source-side heat exchanger; a bypass refrigerant circuit branched off from the pipe between the usage-side heat exchanger and the first expansion device, in which branched refrigerant is decompressed by a second expansion device and thereafter, heat of the refrigerant is exchanged with that of the refrigerant flowing through the main refrigerant circuit by the intermediate heat exchanger, and the refrigerant joins up with the refrigerant which is in middle of a compression operation of the compression rotation element; and a control device, wherein when temperature of the usage-side heat medium which flows into the usage-side heat exchanger rises, the control device
  • Claim 1 of the present invention provides a heat pump system Including: a main refrigerant circuit formed by sequentially connecting, through a pipe, a compression mechanism composed of a compression rotation element, a usage-side heat exchanger for heating usage-side heat medium by refrigerant which is discharged from the compression rotation element and which exceeds critical pressure, an intermediate heat exchanger, a first expansion device, and a heat source-side heat exchanger; a bypass refrigerant circuit branched off from the pipe between the usage-side heat exchanger and the first expansion device, in which branched refrigerant is decompressed by a second expansion device and thereafter, heat of the refrigerant is exchanged with that of the refrigerant flowing through the main refrigerant circuit by the intermediate heat exchanger, and the refrigerant joins up with the refrigerant which is in middle of a compression operation of the compression rotation element; and a control device, wherein when temperature of the usage-side heat medium which flows into the usage-side heat exchanger rises, the control device
  • the heat pump system of claim 1 further comprises a heat medium inlet temperature thermistor for detecting the temperature of the usage-side heat medium which flows into the usage-side heat exchanger, wherein when detected temperature which is detected by the heat medium inlet temperature thermistor rises, the control device operates to increase the valve opening of the second expansion device.
  • the control device operates to reduce a valve opening of the first expansion device.
  • the pressure of the high-pressure side of refrigerant of the main refrigerant circuit rises. Therefore, even if temperature of the usage-side heat medium which flows into the usage-side heat exchanger rises, it is possible to suppress the reduction of the enthalpy difference between the outlet of refrigerant and inlet of refrigerant in the usage-side heat exchanger.
  • the heat pump system of claim 3 further includes a discharge temperature thermistor which detects temperature of the refrigerant discharged from the compressing rotation element, wherein the control device brings the temperature detected by the discharge temperature thermistor close to a target value by adjusting the valve opening of the first expansion device and the valve opening of the second expansion device.
  • the heat pump system of claim 3 further includes a high pressure-side pressure detector which detects pressure of the refrigerant discharged from the compressing rotation element, wherein the control device brings a pressure value detected by the high pressure-side pressure detector close to a target value by adjusting the valve opening of the first expansion device and the valve opening of the second expansion device.
  • the heat pump system of any one of claims 1 to 5 further includes a usage-side heat medium circuit which includes a conveying device and which circulates the usage-side heat medium by the conveying device.
  • the usage-side heat medium is water or antifreeze liquid.
  • Fig. 1 is a block diagram of a heat pump system according to the embodiment of the invention.
  • the heat pump system is composed of a refrigeration cycle device 9 which is a supercritical vapor compressing type refrigeration cycle, and a usage-side heat medium circuit 30.
  • the refrigeration cycle device 9 is composed of a main refrigerant circuit 10 and a bypass refrigerant circuit 20.
  • the main refrigerant circuit 10 is formed by sequentially connecting, through a pipe 16, a compression mechanism 11 which compresses refrigerant, a usage-side heat exchanger 12 which is a radiator, an intermediate heat exchanger 13, a first expansion device 14 and a heat source-side heat exchanger 15 which is an evaporator.
  • Carbon dioxide (CO2) is used as refrigerant.
  • the compression mechanism 11 is composed of a low stage-side compression rotation element 11a and a high stage-side compression rotation element 11b.
  • the usage-side heat exchanger 12 heats usage-side heat medium by refrigerant discharged from the high stage-side compression rotation element 11b.
  • a volume ratio of the low stage-side compression rotation element 11a and the high stage-side compression rotation element 11b which configure the compression mechanism 11 is constant, these rotation elements use a common driving shaft (not shown), and the rotation elements are composed of a single compressor placed in one container.
  • This embodiment is described using a two-stage compression mechanism 11 in which the compression rotation element is composed of the low stage-side compression rotation element 11a and the high stage-side compression rotation element 11b, but the present invention can be applied also to a single compression mechanism in which the compressing rotation element is not divided into the low-stage side compressing rotation element 11a and the high-stage side compressing rotation element 11b.
  • a position where refrigerant from the bypass refrigerant circuit 20 joins up is defined as a middle position of being compressed by the compression rotation element
  • a portion of the compression rotation element up to a position where refrigerant from the bypass refrigerant circuit 20 joins up is defined as the low stage-side compression rotation element 11a
  • a portion of the compression rotation element after the position where the refrigerant from the bypass refrigerant circuit 20 joins up is defined as the high stage-side compression rotation element 11b.
  • the low-stage side compressing rotation element 11a and the high-stage side compressing rotation element 11b may be a two-stage compression mechanism 11 which is composed of independent two compressors.
  • the bypass refrigerant circuit 20 branches off from the pipe 16 between the usage-side heat exchanger 12 and the first expansion device 14, and is connected to the pipe 16 between the low stage-side compression rotation element 11a and the high stage-side compression rotation element 11b.
  • the bypass refrigerant circuit 20 is provided with a second expansion device 21.
  • a portion of high pressure refrigerant after it passes through the usage-side heat exchanger 12, or a portion of high pressure refrigerant after it passes through the intermediate heat exchanger 13 is decompressed by the second expansion device 21, and becomes intermediate pressure refrigerant and after that, this refrigerant is heat-exchanged with high pressure refrigerant which flows through the main refrigerant circuit 10 by the intermediate heat exchanger 13, and the refrigerant joins up with refrigerant between the low stage-side compression rotation element 11a and the high stage-side compression rotation element 11b.
  • the usage-side heat medium circuit 30 is formed by sequentially connecting the usage-side heat exchanger 12, a conveying device 31 which is a conveying pump, and the heating terminal 32a through a heat medium pipe 33. Water of antifreeze liquid is used as the usage-side heat medium.
  • the usage-side heat medium circuit 30 in this embodiment includes a hot water storage tank 32b in parallel to the heating terminal 32a.
  • the usage-side heat medium circuit 30 circulates the usage-side heat medium through the heating terminal 32a or a hot water storage tank 32b by switching between a first switching valve 34 and a second switching valve 35.
  • the usage-side heat medium circuit 30 may include any one of the heating terminal 32a and the hot water storage tank 32b.
  • High temperature water produced by the usage-side heat exchanger 12 radiates heat in the heating terminal 32a and is utilized for heating a room, and low temperature water whose heat is radiated in the heating terminal 32a is again heated by the usage-side heat exchanger 12.
  • High temperature water produced by the usage-side heat exchanger 12 is introduced into the hot water storage tank 32b from an upper portion of the hot water storage tank 32b, low temperature water is sent out from a lower portion of the hot water storage tank 32b and heated by the usage-side heat exchanger 12.
  • a hot water supplying heat exchanger 42 is placed in the hot water storage tank 32b, and the hot water supplying heat exchanger 42 exchanges heat between supplied water from a water supplying pipe 43 and high temperature water in the hot water storage tank 32b. That is, if a hot water supplying plug 41 is opened, water is supplied from the water supplying pipe 43 into the hot water supplying heat exchanger 42, the water is heated by the hot water supplying heat exchanger 42, temperature of the water is adjusted to predetermined temperature by the hot water supplying plug 41, and hot water is supplied from the hot water supplying plug 41.
  • Water is supplied from the water supplying pipe 43 and heated by the hot water supplying heat exchanger 42, and hot water supplied from the hot water supplying plug 41 and high temperature water in the hot water storage tank 32b are not mixed with each other, and they are indirectly heated.
  • the hot water supplying heat exchanger 42 is a water heat exchanger using a copper pipe or stainless steel pipe as a heat transfer pipe, and the water supplying pipe 43 extending from a water supplying source (running water) and the hot water supplying plug 41 are connected to the hot water supplying heat exchanger 42 as shown in Fig. 1 .
  • the water supplying pipe 43 sends normal temperature water into a lower end of the hot water supplying heat exchanger 42, i.e., into a lower portion in the hot water storage tank 32b.
  • the normal temperature water sent into the hot water supplying heat exchanger 42 from the water supplying pipe 43 draws heat from the high temperature water in the hot water storage tank 32b while moving upward in the hot water storage tank 32b from downward, and the normal temperature water becomes high temperature heated water and is supplied from the hot water supplying plug 41.
  • the hot water storage tank 32b is provided with a plurality of hot water storage tank temperature thermistors, e.g., a first hot water storage tank temperature thermistor 55a, a second hot water storage tank temperature thermistor 55b and a third hot water storage tank temperature thermistor 55c.
  • a first hot water storage tank temperature thermistor 55a e.g., a first hot water storage tank temperature thermistor 55a
  • a second hot water storage tank temperature thermistor 55b e.g., a third hot water storage tank temperature thermistor 55c.
  • the normal temperature water which enters the hot water supplying heat exchanger 42 from the water supplying pipe 43 draws heat from high temperature water in the hot water storage tank 32b while moving upward in the hot water storage tank 32b from downward. Therefore, temperature of hot water in the hot water storage tank 32b naturally becomes high at an upper portion and lower at a low portion in the hot water storage tank 32b.
  • the main refrigerant circuit 10 is provided with a high pressure-side pressure detector 51 and a discharge temperature thermistor 52 in the pipe 16 on the discharge side of the high stage-side compression rotation element 11b.
  • the high pressure-side pressure detector 51 is provided in the main refrigerant circuit 10 from a discharge side of the high stage-side compression rotation element 11b to an upstream side of the first expansion device 14. It is only necessary that the high pressure-side pressure detector 51 can detect pressure of high pressure refrigerant in the main refrigerant circuit 10.
  • the discharge temperature thermistor 52 is also provided in the main refrigerant circuit 10 from the discharge side of the high-stage side compressing rotation element 11b to the upstream side of the first expansion device 14. It is also only necessary that the discharge temperature thermistor 52 can detect temperature of the high pressure refrigerant of the main refrigerant circuit 10.
  • the usage-side heat medium circuit 30 includes a heat medium inlet temperature thermistor 54 for detecting temperature of usage-side heat medium which flows into the usage-side heat exchanger 12.
  • the control device 60 controls operation frequencies of the low-stage side compressing rotation element 11a and the high-stage side compressing rotation element 11b, a valve opening of the first expansion device 14, a valve opening of the second expansion device 21 and a conveying amount of the usage-side heat medium conveyed by the conveying device 31 based on detected pressure detected by the high pressure-side pressure detector 51, detected temperature detected by the discharge temperature thermistor 52 and detected temperature detected by the heat medium inlet temperature thermistor 54.
  • Fig. 2 is a pressure-enthalpy diagram (P-h diagram) under the ideal condition concerning the refrigeration cycle device in the embodiment.
  • Points a to e and points A and B in Fig. 2 correspond to points in the refrigeration cycle device shown in Fig. 1 .
  • high pressure refrigerant (point a) discharged from the high stage-side compression rotation element 11b radiates heat in the usage-side heat exchanger 12 and after that, the high pressure refrigerant branches off from the main refrigerant circuit 10 at a refrigerant branch point (point A), the high pressure refrigerant is decompressed to intermediate pressure by the second expansion device 21 and becomes intermediate pressure refrigerant (point e), and the intermediate pressure refrigerant is heat-exchanged by the intermediate heat exchanger 13.
  • the high pressure refrigerant which flows through the main refrigerant circuit 10 after it radiates heat by the usage-side heat exchanger 12 is cooled by intermediate pressure refrigerant (point e) which flows through the bypass refrigerant circuit 20, and the high pressure refrigerant is decompressed by the first expansion device 14 in a state (point b) where enthalpy thereof is reduced.
  • refrigerant enthalpy of refrigerant (point c) which flows into the heat source-side heat exchanger 15 after it is decompressed by the first expansion device 14 is also reduced. Dryness (weight ratio occupied by gas phase component to the entire refrigerant) of refrigerant when it flows into the heat source-side heat exchanger 15 is reduced and liquid component of refrigerant is increased. Therefore, this contributes to evaporation in the heat source-side heat exchanger 15, a refrigerant ratio is increased and an endothermic energy amount from outside air is increased, and it returns to the suction side (point d) of the low stage-side compression rotation element 11a.
  • refrigerant of an amount corresponding to gas phase component which does not contribute to evaporation in the heat source-side heat exchanger 15 is made to bypass by the bypass refrigerant circuit 20, and becomes low temperature intermediate pressure refrigerant (point e), the refrigerant is heated by high pressure refrigerant which flows through the main refrigerant circuit 10 in the intermediate heat exchanger 13, and the refrigerant reaches a refrigerant joining point B located between the low stage-side compression rotation element 11a and the high stage-side compression rotation element 11b in a state where refrigerant enthalpy is increased.
  • the control device 60 determines that high temperature water is insufficient in the hot water storage tank 32b.
  • the control device 60 operates the low stage-side compression rotation element 11a and the high stage-side compression rotation element 11b and heats low temperature water by the usage-side heat exchanger 12.
  • the control device 60 operates the conveying device 31 such that detected temperature detected by the heat medium outlet temperature thermistor 53 which is heating producing temperature becomes equal to the target temperature.
  • the control device 60 operates the low stage-side compression rotation element 11a and the high stage-side compression rotation element 11b and heats circulated water by the usage-side heat exchanger 12, and the control device 60 operates the conveying device 31 such that a temperature difference, which is the temperature difference of the circulated water, between detected temperature detected by the heat medium outlet temperature thermistor 53 and detected temperature detected by the heat medium inlet temperature thermistor 54 becomes equal to a target temperature difference.
  • high temperature water produced by the usage-side heat exchanger 12 radiates heat in the heating terminal 32a and is utilized for heating a room, and low temperature water whose heat is released by the heating terminal 32a is again heated by the usage-side heat exchanger 12.
  • control since control is performed such that a temperature difference between detected temperature detected by the heat medium outlet temperature thermistor 53 and detected temperature detected by the heat medium inlet temperature thermistor 54 becomes equal to the target temperature difference.
  • control is performed such that a temperature difference between detected temperature detected by the heat medium outlet temperature thermistor 53 and detected temperature detected by the heat medium inlet temperature thermistor 54 becomes equal to the target temperature difference. Therefore, the detected temperature detected by the heat medium outlet temperature thermistor 53 and the detected temperature detected by the heat medium inlet temperature thermistor 54 increase gradually.
  • a solid line is a pressure-enthalpy diagram when temperature of the usage-side heat medium which flows into the usage-side heat exchanger 12 rises with respect to broken lines.
  • inlet temperature (point a) of refrigerant toward the usage-side heat exchanger 12 moves to an increasing direction (point a') of enthalpy.
  • outlet temperature (point A) of refrigerant from the usage-side heat exchanger 12 moves to the increasing direction (point A') of enthalpy.
  • outlet temperature (point B) of refrigerant from the bypass refrigerant circuit 20 of the intermediate heat exchanger 13 also moves to the increasing direction (point B') of enthalpy.
  • inlet temperature (point e) of refrigerant toward the bypass refrigerant circuit 20 of the intermediate heat exchanger 13 also moves to the increasing direction (point e') of enthalpy.
  • control device 60 must control the valve opening of the second expansion device 21 such that a temperature difference between the outlet temperature (point B') of refrigerant from the bypass refrigerant circuit 20 of the intermediate heat exchanger 13 and the inlet temperature (point e') of refrigerant toward the bypass refrigerant circuit 20 to the intermediate heat exchanger 13 does not become as small as possible in the intermediate heat exchanger 13.
  • a ratio of an amount of refrigerant which flows through the bypass refrigerant circuit 20 to an amount of refrigerant which flows on the side of the main refrigerant circuit 10 of the intermediate heat exchanger 13 is increased.
  • valve opening of the second expansion device 21 is increased and a ratio of an amount of refrigerant which circulates through the bypass refrigerant circuit 20, the high-stage side compressing rotation element 11b and the usage-side heat exchanger 12 to an amount of refrigerant which circulates through the main refrigerant circuit 10 is increased.
  • the enthalpy difference between the high pressure refrigerant (point a') discharged from the high-stage side compressing rotation element 11b and the refrigerant (point A') of a branch point of refrigerant after heat is released at the usage-side heat exchanger 12 is equal to a total of an enthalpy difference between refrigerant (point B') on the suction side of the high-stage side compressing rotation element 11b and the intermediate pressure refrigerant (point e') which flows through the bypass refrigerant circuit 20 and an enthalpy difference of the high-stage side compressing rotation element 11b.
  • the high-stage side compressing rotation element 11b and the usage-side heat exchanger 12 Since the amount of refrigerant which circulates through the bypass refrigerant circuit 20, the high-stage side compressing rotation element 11b and the usage-side heat exchanger 12 is increased, it is possible to suppress the deterioration of the heating ability in the usage-side heat exchanger 12.
  • the control device 60 operates to reduce the valve opening of the first expansion device 14. According to this, since pressure on the high-pressure side of refrigerant of the main refrigerant circuit 10 rises, even if temperature of the usage-side heat medium which flows into the usage-side heat exchanger 12 rises, it is possible to suppress the reduction of the enthalpy difference (point a' to point A') between the outlet of refrigerant and the inlet of refrigerant in the usage-side heat exchanger 12.
  • the control device 60 adjusts the valve opening of the first expansion device 14 and the valve opening of the second expansion device 21. According to this, temperature detected by the discharge temperature thermistor 52 is brought close to a target value.
  • the target value of discharge temperature is preset in the control device 60.
  • the control device 60 adjusts the valve opening of the first expansion device 14 and the valve opening of the second expansion device 21. According to this, a pressure value detected by the high pressure-side pressure detector 51 is brought close to a target value.
  • the compressing rotation element may be a single compressing rotation element which is not divided into the low-stage side compressing rotation element 11a and the high-stage side compressing rotation element 11b. If the single compressing rotation element is employed, a position where refrigerant from the bypass refrigerant circuit 20 joins up is defined as a middle position of being compressed by the compression rotation element.
  • the heat pump system of the present invention whose high-pressure side is operated under supercritical pressure, even if temperature of usage-side heat medium which flows into a usage-side heat exchanger rises, deterioration of COP is suppressed by performing appropriate control. Therefore, the heat pump system is suitable for refrigerating equipment, an air conditioner, a hot water supply system, heating equipment and the like.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
EP20206234.5A 2019-12-11 2020-11-06 Pompe à chaleur Pending EP3835687A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2019223863A JP7390605B2 (ja) 2019-12-11 2019-12-11 ヒートポンプシステム

Publications (1)

Publication Number Publication Date
EP3835687A1 true EP3835687A1 (fr) 2021-06-16

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Citations (4)

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JP2008008499A (ja) 2006-06-27 2008-01-17 Sanyo Electric Co Ltd 冷凍サイクル装置及びヒートポンプ式給湯機
WO2009091401A1 (fr) * 2008-01-17 2009-07-23 Carrier Corporation Modulation de capacité d'un système de compression de vapeur de fluide frigorigène
US20100115975A1 (en) * 2007-04-24 2010-05-13 Carrier Corporation Refrigerant vapor compression system and method of transcritical operation
DE112016004544T5 (de) * 2015-10-05 2018-06-21 Denso Corporation Kältekreislaufvorrichtung

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JP4269323B2 (ja) 2004-03-29 2009-05-27 三菱電機株式会社 ヒートポンプ給湯機
JP7233845B2 (ja) 2018-03-27 2023-03-07 株式会社富士通ゼネラル 空気調和機
EP3805663A4 (fr) 2018-05-31 2021-07-28 Panasonic Intellectual Property Management Co., Ltd. Cycle frigorifique à compression de vapeur supercritique et dispositif de chauffage de liquide

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008008499A (ja) 2006-06-27 2008-01-17 Sanyo Electric Co Ltd 冷凍サイクル装置及びヒートポンプ式給湯機
US20100115975A1 (en) * 2007-04-24 2010-05-13 Carrier Corporation Refrigerant vapor compression system and method of transcritical operation
WO2009091401A1 (fr) * 2008-01-17 2009-07-23 Carrier Corporation Modulation de capacité d'un système de compression de vapeur de fluide frigorigène
DE112016004544T5 (de) * 2015-10-05 2018-06-21 Denso Corporation Kältekreislaufvorrichtung

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