EP3683520B1 - Dispositif à cycle de réfrigération et dispositif de chauffage de liquide le comprenant - Google Patents

Dispositif à cycle de réfrigération et dispositif de chauffage de liquide le comprenant Download PDF

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Publication number
EP3683520B1
EP3683520B1 EP19191742.6A EP19191742A EP3683520B1 EP 3683520 B1 EP3683520 B1 EP 3683520B1 EP 19191742 A EP19191742 A EP 19191742A EP 3683520 B1 EP3683520 B1 EP 3683520B1
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EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
temperature
intermediate heat
utilization
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EP19191742.6A
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German (de)
English (en)
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EP3683520A1 (fr
Inventor
Tsuneko Imagawa
Yuki YAMAOKA
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Panasonic Intellectual Property Management Co Ltd
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Panasonic Intellectual Property Management Co Ltd
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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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • 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
    • 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
    • F25B2400/13—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
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures

Definitions

  • the present invention relates to a refrigeration cycle device and a liquid heating device having the same.
  • a supercritical vapor compression type refrigeration cycle which includes a two-stage compressor for compressing refrigerant in two stages, and two expansion devices for expanding refrigerant in two stages, and which uses carbon dioxide as the refrigerant (see patent document 1 for example).
  • the supercritical vapor compression type refrigeration cycle of patent document 1 includes a gas-liquid separator.
  • Refrigerant composed of gaseous phase in the gas-liquid separator as main ingredient is intermediately injected into a refrigerant mixer located between an injection circuit and an intermediate connection circuit of the two-stage compressor, the refrigerant is mixed with refrigerant discharged from a low stage-side rotary compression rotary element, and is sucked into a high stage-side rotary compression rotary element.
  • the refrigeration device of patent document 2 includes a supercooling heat exchanger and an injection circuit.
  • the injection circuit a portion of refrigerant discharged from the two-stage compressor is expanded, and the refrigerant is heat-exchanged with refrigerant discharged from the supercooling heat exchanger and thereafter, the refrigerant is injected into an intermediate port.
  • an opening of an expansion valve is controlled.
  • Patent Document 3 is considered to represent the closest prior art and discloses a refrigeration cycle device according to the preamble of claim 1, namely a refrigeration cycle device with a compression mechanism, a heat radiator, a first pressure reducer, an evaporator, a second pressure reducer, an internal heat exchanger, a temperature detection unit, and a control device.
  • the compression mechanism discharges a high-pressure refrigerant in a supercritical state, and introduces an intermediate-pressure refrigerant having an intermediate pressure between a low pressure and a high pressure during a process in which a refrigerant is compressed from the low pressure to the high pressure.
  • the temperature detection unit detects the temperature of a heat exchange medium flowing into the heat radiator.
  • the control device adjusts the pressure of the high-pressure refrigerant so that the higher the detected temperature, the higher the pressure of the high-pressure refrigerant becomes, and also adjusts the flow rate of the intermediate-pressure refrigerant so that the higher the detected temperature, the greater the flow rate of the intermediate-pressure refrigerant becomes.
  • control since control is performed based on the degree of overheat of the outlet of the supercooling heat exchanger, control cannot be performed when pressure of refrigerant which is discharged from the two-stage compressor and expanded is equal to or higher than critical pressure.
  • the present invention has been accomplished to solve the problems, and it is an object of the invention to provide a refrigeration cycle device and a liquid heating device having the same which do not deteriorate COP by appropriately performing the control even when high pressure is further increased.
  • the present invention provides a refrigeration cycle device as defined in appended claim 1.
  • a first aspect of the present invention provides a refrigeration cycle device as defined in appended claim 1.
  • control device controls the valve opening of the second expansion device such that the temperature difference between the outlet temperature of the refrigerant flowing through the bypass refrigerant circuit at the intermediate heat exchanger and the inlet temperature of the refrigerant flowing through the bypass refrigerant circuit at the intermediate heat exchanger increases when the pressure of the refrigerant after it is decompressed by the second expansion device increases.
  • inlet temperature of the utilization-side heating medium to the utilization-side heat exchanger outlet temperature of the utilization-side heating medium from the utilization-side heat exchanger, and heat source-side heating medium (air) to the heat source-side heat exchanger rise.
  • pressure of the refrigerant flowing through the bypass refrigerant circuit in the intermediate heat exchanger also rises.
  • the control device controls the valve opening of the second expansion device such that the higher the pressure of refrigerant after it is decompressed by the second expansion device becomes, the larger the temperature difference between the outlet temperature of the refrigerant flowing through the bypass refrigerant circuit at the intermediate heat exchanger and inlet temperature of the refrigerant flowing through the bypass refrigerant circuit at the intermediate heat exchanger becomes. Therefore, since the enthalpy difference between refrigerant of the outlet and refrigerant of the inlet in the intermediate heat exchanger flowing through the bypass refrigerant circuit can be secured even if intermediate pressure rises, it is possible to provide a refrigeration cycle device which realizes high COP.
  • the control device determines whether the pressure of the refrigerant after it is decompressed by the second expansion device is equal to or higher than the critical pressure from a pressure value of the refrigerant discharged from the compressing mechanism , from outlet temperature of the refrigerant at the utilization-side heat exchanger, and from the inlet temperature of the refrigerant flowing through the bypass refrigerant circuit at the intermediate heat exchanger.
  • the refrigerant is carbon dioxide.
  • the invention further provides a liquid heating device as defined in appended claim 5.
  • the liquid heating device further includes: a heating medium outlet temperature thermistor for detecting temperature of the utilization-side heating medium which flows out from the utilization-side heat exchanger; and a heating medium inlet temperature thermistor for detecting the temperature of the utilization-side heating medium which flows into the utilization-side heat exchanger, wherein the control device operates the transfer device such that detected temperature of the heating medium outlet temperature thermistor becomes equal to target temperature, and the control device controls the valve opening of the second expansion device such that when detected temperature of the heating medium inlet temperature thermistor exceeds first predetermined temperature, the temperature difference between the outlet temperature of the refrigerant flowing through the bypass refrigerant circuit at the intermediate heat exchanger and the inlet temperature of the refrigerant flowing through the bypass refrigerant circuit at the intermediate heat exchanger becomes larger than the temperature difference when the refrigerant flows through the intermediate heat exchanger in the gas-liquid two-phase state, and such that the temperature difference between the outlet temperature of the refrigerant flowing through
  • the liquid heating device further includes: a heating medium outlet temperature thermistor for detecting temperature of the utilization-side heating medium which flows out from the utilization-side heat exchanger; and a heating medium inlet temperature thermistor for detecting the temperature of the utilization-side heating medium which flows into the utilization-side heat exchanger, wherein the control device operates the transfer device such that a temperature difference between detected temperature of the heating medium outlet temperature thermistor and detected temperature of the heating medium inlet temperature thermistor becomes equal to a target temperature difference, and the control device controls the valve opening of the second expansion device such that when the detected temperature of the heating medium outlet temperature thermistor exceeds second predetermined temperature, the temperature difference between the outlet temperature of the refrigerant flowing through the bypass refrigerant circuit at the intermediate heat exchanger and the inlet temperature of the refrigerant flowing through the bypass refrigerant circuit at the intermediate heat exchanger becomes larger than the temperature difference when the refrigerant flows through the intermediate heat exchanger in the gas-liquid two
  • the control device determines whether the pressure of the refrigerant after it is decompressed by the second expansion device is equal to or higher than the critical pressure from a pressure value of the refrigerant discharged from the compressing mechanism , from the temperature of the utilization-side heating medium which flows into the utilization-side heat exchanger, and from the inlet temperature of the refrigerant flowing through the bypass refrigerant circuit at the intermediate heat exchanger.
  • the utilization-side heating medium is water or antifreeze liquid.
  • high temperature water can be stored in a hot water storage tank for example without deteriorating COP, and it is possible to provide a liquid heating device for heating a room using high temperature water.
  • Fig. 1 is a block diagram of a liquid heating device in a first embodiment of the present invention.
  • the liquid heating device is composed of a refrigeration cycle device which is a supercritical vapor compression type refrigeration cycle and a utilization-side heating medium circuit 30.
  • the refrigeration cycle device is composed of a main refrigerant circuit 10 and a bypass refrigerant circuit 20.
  • the main refrigerant circuit 10 is formed by sequentially connecting, to one another through a pipe 16, a compressing mechanism 11 for compressing refrigerant, a utilization-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 the refrigerant.
  • the refrigerant it is optimal to use carbon dioxide, but it is also possible to use non-azeotropic mixture refrigerant such as R407C, pseudoazeotropic mixture refrigerant such as R410A and single refrigerant such as R32.
  • the compressing mechanism 11 is composed of a low stage-side compression rotary element 11a and a high stage-side compression rotary element 11b.
  • the utilization-side heat exchanger 12 heats utilization-side heating medium by refrigerant discharged from the high stage-side compression rotary element 11b.
  • a volume ratio of the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b constituting the compressing mechanism 11 is constant, the rotary elements 11a, 11b use a common driving shaft (not shown), and are composed of one compressor placed in one container.
  • the embodiment will be described using the two-stage compressing mechanism 11 in which the compression rotary element is composed of the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b, but the compression rotary element may not be divided into the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b, and the invention can be applied also in a single compression rotary element.
  • the invention can be applied based on such a configuration that refrigerant from the bypass refrigerant circuit 20 joins up with refrigerant at a position where the compression rotary element is on an intermediate stage of compression, a compression rotary element to a position where refrigerant from the bypass refrigerant circuit 20 joins up is the low stage-side compression rotary element 11a, and a compression rotary element after the position where refrigerant from the bypass refrigerant circuit 20 joins up is the high stage-side compression rotary element 11b.
  • the two-stage compressing mechanism 11 may be composed of two compressors in which the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b are independent from each other.
  • the bypass refrigerant circuit 20 branches off from a pipe 16 extending from the utilization-side heat exchanger 12 to the first expansion device 14, and the bypass refrigerant circuit 20 is connected to the pipe 16 between the low stage-side compression rotary element 11a and the high stage-side compression rotary 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 utilization-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.
  • the intermediate pressure refrigerant heat-exchanges with high pressure refrigerant flowing through the main refrigerant circuit 10 in the intermediate heat exchanger 13, and joins up with refrigerant between the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b.
  • the utilization-side heating medium circuit 30 is formed by sequentially connecting, to one another through a heating medium pipe 33, the utilization-side heat exchanger 12, a transfer device 31 which is a transfer pump, and a heating terminal 32a.
  • a heating medium water or antifreeze liquid is used.
  • the utilization-side heating medium circuit 30 of this embodiment includes the heating terminal 32a and a hot water storage tank 32b in parallel. By switching between a first switching valve 34 and a second switching valve 35, utilization-side heating medium is circulated through the heating terminal 32a or the hot water storage tank 32b. It is only necessary that the utilization-side heating medium circuit 30 includes any one of the heating terminal 32a or the hot water storage tank 32b.
  • High temperature water produced by the utilization-side heat exchanger 12 radiates heat by the heating terminal 32a and is utilized for heating a room, and low temperature water which radiates heat by the heating terminal 32a is again heated by the utilization-side heat exchanger 12.
  • High temperature water produced by the utilization-side heat exchanger 12 is introduced into the hot water storage tank 32b from an upper portion of the hot water storage tank 32b, and low temperature water is taken out from a lower portion of the hot water storage tank 32b and heated by the utilization-side heat exchanger 12.
  • a hot water supply-heat exchanger 42 is placed in the hot water storage tank 32b, and makes water supplied from a water supply-pipe 43 and high temperature water in the hot water storage tank 32b heat-exchange with each other. That is, when a hot water supply plug hot water supply plug 41 is opened, water is supplied from the water supply-pipe 43 to the hot water supply-heat exchanger 42, the water is heated by the hot water supply-heat exchanger 42, and adjusted to predetermined temperature by the hot water supply plug hot water supply plug 41, and hot water is supplied from the hot water supply plug hot water supply plug 41.
  • Hot Water is supplied from the water supply-pipe 43, and heated by the hot water supply-heat exchanger 42. Hot water supplied from the hot water supply plug hot water supply plug 41 and high temperature water in the hot water storage tank 32b are indirectly heated so that they are not mixed with each other.
  • the hot water supply-heat exchanger 42 is a water heat exchanger using a copper pipe or a stainless pipe as a heat transfer pipe. As shown in Fig. 1 , the hot water supply plug 41 and the water supply-pipe 43 extending from a water supply source (waterline) are connected to the hot water supply-heat exchanger 42.
  • the water supply-pipe 43 introduces normal temperature water to a lower end of the hot water supply-heat exchanger 42, i.e., to a lower location in the hot water storage tank 32b.
  • the normal temperature water which enters the hot water supply-heat exchanger 42 from the water supply-pipe 43 moves from downward to upward in the hot water storage tank 32b, draws heat from high temperature water in the hot water storage tank 32b, and becomes high temperature heated water, and is supplied from the hot water supply plug hot water supply plug 41.
  • the hot water storage tank 32b is provided with 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.
  • the normal temperature water which flows into the hot water supply-heat exchanger 42 from the water supply-pipe 43 draws heat from high temperature water in the hot water storage tank 32b while moving from downward to upward in the hot water storage tank 32b. Therefore, temperature of an upper portion of hot water in the hot water storage tank 32b naturally becomes high and temperature of a lower portion thereof naturally becomes low.
  • a discharge-side pipe 16 of the high stage-side compression rotary element 11b of the main refrigerant circuit 10 is provided with a high pressure-pressure detection device 51.
  • the high pressure-pressure detection device 51 is provided in the main refrigerant circuit 10 between a discharge side of the high stage-side compression rotary element 11b and an upstream side of the first expansion device 14. It is only necessary that the high pressure-pressure detection device 51 can detect pressure of high pressure refrigerant of the main refrigerant circuit 10.
  • the pipe 16 located downstream of the utilization-side heat exchanger 12 of the main refrigerant circuit 10 and upstream of the intermediate heat exchanger 13 is provided with an intermediate heat exchanger main refrigerant inlet thermistor 57.
  • the intermediate heat exchanger main refrigerant inlet thermistor 57 detects temperature of refrigerant which flows out from the utilization-side heat exchanger 12.
  • the pipe 16 located downstream of the intermediate heat exchanger 13 of the main refrigerant circuit 10 and upstream of the first expansion device 14 is provided with an intermediate heat exchanger main refrigerant outlet thermistor 58.
  • the bypass refrigerant circuit 20 is provided with an intermediate heat exchanger bypass inlet thermistor 56 downstream of the second expansion device 21 and upstream of the intermediate heat exchanger 13. Further, the bypass refrigerant circuit 20 is provided with an intermediate heat exchanger bypass outlet thermistor 52 downstream of the intermediate heat exchanger 13.
  • the utilization-side heating medium circuit 30 is provided with a heating medium outlet temperature thermistor 53 for detecting temperature of utilization-side heating medium flowing out from the utilization-side heat exchanger 12 and a heating medium inlet temperature thermistor 54 for detecting temperature of utilization-side heating medium flowing into the utilization-side heat exchanger 12.
  • a control device 60 controls operation frequencies of the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b, valve openings of the first expansion device 14 and the second expansion device 21, and a transfer amount of utilization-side heating medium by the transfer device 31.
  • the control device 60 controls these elements by pressure detected by the high pressure-pressure detection device 51, calculated intermediate pressure, a temperature difference ( ⁇ TM) between detected temperature of the intermediate heat exchanger bypass outlet thermistor 52 and detected temperature of the intermediate heat exchanger bypass inlet thermistor 56, a temperature difference ( ⁇ TH) between detected temperature of the intermediate heat exchanger bypass outlet thermistor 52 and detected temperature of the intermediate heat exchanger main refrigerant inlet thermistor 57, a temperature difference ( ⁇ TL) between detected temperature of the intermediate heat exchanger bypass inlet thermistor 56 and detected temperature of the intermediate heat exchanger main refrigerant outlet thermistor 58, detected temperature of the heating medium outlet temperature thermistor 53 and detected temperature of the heating medium inlet temperature thermistor 54.
  • ⁇ TM temperature difference
  • ⁇ TH temperature difference
  • ⁇ TL temperature difference
  • a method, by the control device 60, for calculating pressure (intermediate pressure) of refrigerant after it is decompressed by the second expansion device 21 in the bypass refrigerant circuit 20 will be described later.
  • Figs. 2 are pressure-enthalpy diagrams (P-h diagram) under ideal conditions concerning the refrigeration cycle device in this embodiment, wherein Figs. 2(a) shows a case where high pressure is lower than predetermined pressure, and Fig. 2(b) shows a case where high pressure is equal to or higher than the predetermined pressure.
  • Points a to e and points A and B in Figs. 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 rotary element 11b radiates heat in the utilization-side heat exchanger 12 and then, the refrigerant branches off from the main refrigerant circuit 10 at a refrigerant branch A, the refrigerant is decompressed to intermediate pressure by the second expansion device 21 and becomes intermediate pressure refrigerant (point e), and heat-exchanges by the intermediate heat exchanger 13.
  • High pressure refrigerant flowing through the main refrigerant circuit 10 after it radiates heat in the utilization-side heat exchanger 12 is cooled by intermediate pressure refrigerant (point e) flowing through the bypass refrigerant circuit 20 and the high pressure refrigerant is decompressed by the first expansion device 14 in a state where enthalpy is reduced (point b).
  • refrigerant enthalpy of refrigerant (point c) which flows into the heat source-side heat exchanger 15 is also reduced.
  • a refrigerant dryness fraction (ratio of weight occupied by gaseous phase component with respect to entire refrigerant) when the refrigerant 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 ratio of refrigerant is increased, a heat absorption amount from outside air is increased, and the refrigerant returns to a suction side (point d) of the low stage-side compression rotary element 11a.
  • refrigerant of an amount corresponding to gaseous phase component which does not contribute to evaporation in the heat source-side heat exchanger 15 bypasses to the bypass refrigerant circuit 20 and becomes intermediate pressure refrigerant (point e), the refrigerant is heated by high pressure refrigerant flowing through the main refrigerant circuit 10 in the intermediate heat exchanger 13, and the refrigerant reaches a refrigerant junction B located between the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b in a state where refrigerant enthalpy is increased.
  • control device 60 starts controlling the valve opening of the second expansion device 21 such that pressure of refrigerant after it is decompressed by the second expansion device 21 exceeds critical pressure.
  • control device 60 determines that detected pressure of the high pressure-pressure detection device 51 rises and exceeds a first predetermined high pressure value, if intermediate pressure is equal to or lower than critical pressure, the control device 60 starts operation to increase the valve opening of the second expansion device 21 so that the intermediate pressure exceeds the critical pressure.
  • the control device 60 operates the second expansion device 21 to increase the valve opening thereof, rises operation frequencies of the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b, increases a circulation amount of refrigerant flowing between the utilization-side heat exchanger 12 and the bypass refrigerant circuit 20, and brings the detected pressure from the high pressure-pressure detection device 51 into a second predetermined high pressure value which is a target high pressure value.
  • the second predetermined high pressure value is higher than the first predetermined high pressure value.
  • suction pressure of the high stage-side compression rotary element 11b can be maintained in a state where the suction pressure exceeds the critical pressure which is a predetermined intermediate pressure value.
  • suction pressure of the high stage-side compression rotary element 11b i.e., pressure (intermediate pressure) of refrigerant after it is decompressed by the second expansion device 21 can be maintained in a state where the pressure exceeds the critical pressure which is the predetermined intermediate pressure value, and heating ability of refrigerant in the utilization-side heat exchanger 12 can also be enhanced.
  • the compressing mechanism 11 may be composed of two compressors in which the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b are independent from each other, and it is only necessary to rise operation frequency of at least the high stage-side compression rotary element 11b.
  • the pressure-enthalpy diagram (P-h diagram) as shown in Figs. 2 is stored in the control device 60.
  • high pressure-side pressure discharged pressure of high stage-side compression rotary element 11b
  • high pressure-pressure detection device 51 outlet temperature (point A) of refrigerant of the utilization-side heat exchanger 12 is detected by the intermediate heat exchanger main refrigerant inlet thermistor 57
  • inlet temperature (point e) of refrigerant of the bypass refrigerant circuit 20 of the intermediate heat exchanger 13 is detected by the intermediate heat exchanger bypass inlet thermistor 56.
  • the control device 60 calculates pressure and enthalpy at the point e, thereby calculating a value of pressure (intermediate pressure) of refrigerant after it is decompressed by the second expansion device 21, and it is possible to determine whether the pressure is equal to or higher than the critical pressure based on the calculated value.
  • pressure (intermediate pressure) of refrigerant after it is decompressed by the second expansion device 21 is equal to or higher than the critical pressure from discharged pressure of the high stage-side compression rotary element 11b, inlet temperature (point e) of refrigerant of the bypass refrigerant circuit 20 of the intermediate heat exchanger 13, and temperature of utilization-side heating medium which flows into the utilization-side heat exchanger 12.
  • control device 60 controls the valve opening of the second expansion device 21 such that a state where suction pressure pf the high stage-side compression rotary element 11b, i.e., pressure (intermediate pressure) of refrigerant after it is decompressed by the second expansion device 21 exceeds the critical pressure is maintained, and such that a heat exchanging amount between refrigerant of the bypass refrigerant circuit 20 and refrigerant of the main refrigerant circuit 10 in the intermediate heat exchanger 13 becomes the maximum.
  • FIG. 3 shows a relation between refrigerant of the main refrigerant circuit 10 and temperature of refrigerant of the bypass refrigerant circuit 20 which flow through the intermediate heat exchanger 13.
  • the control device 60 controls the valve opening of the second expansion device 21 based on a temperature difference ( ⁇ TM) between detected temperature (point B) of the intermediate heat exchanger bypass outlet thermistor 52 and detected temperature (e) of the intermediate heat exchanger bypass inlet thermistor 56, a temperature difference ( ⁇ TH) between detected temperature (point B) of the intermediate heat exchanger bypass outlet thermistor 52 and detected temperature (point A) of the intermediate heat exchanger main refrigerant inlet thermistor 57, and a temperature difference ( ⁇ TL) between detected temperature (e) of the intermediate heat exchanger bypass inlet thermistor 56 and detected temperature (b) of the intermediate heat exchanger main refrigerant outlet thermistor 58.
  • Fig. 4(a) is a diagram showing a relation between ⁇ TM and a circulation amount of refrigerant of the bypass refrigerant circuit 20 flowing through the intermediate heat exchanger 13.
  • Fig. 4(b) is a diagram showing a relation between a heat exchanging amount of the intermediate heat exchanger 13 and a circulation amount of refrigerant of the bypass refrigerant circuit 20 flowing through the intermediate heat exchanger 13.
  • Fig. 4(c) is a diagram showing a relation between ⁇ TH, ⁇ TL and a circulation amount of refrigerant of the bypass refrigerant circuit 20 flowing through the intermediate heat exchanger 13.
  • a solid line shows variation when intermediate pressure is supercritical
  • a dash line shows variation when intermediate pressure is in a gas-liquid two-phase area.
  • a solid line shows variation when intermediate pressure is supercritical
  • a dash line shows variation when intermediate pressure is in the gas-liquid two-phase area.
  • ⁇ TM When intermediate pressure is in the gas-liquid two-phase area and when the intermediate pressure exceeds the critical pressure, a size of ⁇ TM when a heat exchanging amount of the intermediate heat exchanger 13 is set to the maximum is different, and when the intermediate pressure exceeds the critical pressure, it can be found that ⁇ TM is larger than that when the intermediate pressure is in the gas-liquid two-phase area.
  • outlet temperature (point e) of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 is temperature of refrigerant after it is decompressed by the second expansion device 21, but if the valve opening of the second expansion device 21 is small and if an amount of bypass refrigerant flowing through the bypass refrigerant circuit 20 is small, intermediate pressure also becomes low and therefore, temperature of the refrigerant is also low.
  • ⁇ TL which is a temperature difference with respect to outlet temperature (point b) of refrigerant flowing through the main refrigerant circuit 10 at the intermediate heat exchanger 13 becomes large.
  • control device 60 operates to increase the valve opening of the second expansion device 21 and to increase the circulation amount of bypass refrigerant, since a heat exchanging amount at the intermediate heat exchanger 13 is increased, rise of outlet temperature (point B) of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 is suppressed, and ⁇ TH is increased.
  • control device 60 operates to increase the valve opening of the second expansion device 21 and a circulation amount of bypass refrigerant is increased, intermediate pressure is increased. Therefore, outlet temperature (point e) of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 rises, and ⁇ TL which is a temperature difference with respect to outlet temperature (point b) of refrigerant flowing through the main refrigerant circuit 10 at the intermediate heat exchanger 13 becomes small.
  • control device 60 executes the following intermediate pressure supercritical operation mode.
  • control device 60 determines that detected pressure of the high pressure-pressure detection device 51 rises and exceeds the first predetermined high pressure value, if the intermediate pressure is equal to or lower than the critical pressure, the control device 60 starts the operation to increase the valve opening of the second expansion device 21 so that intermediate pressure exceeds critical pressure.
  • control device 60 controls the valve opening of the second expansion device 21 such that a temperature difference ( ⁇ TM) between outlet temperature of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 and inlet temperature of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 becomes larger than a temperature difference ( ⁇ TM) when refrigerant flows through the intermediate heat exchanger 13 in the gas-liquid two-phase state so that a state where pressure (intermediate pressure) of refrigerant after it is decompressed by the second expansion device 21 exceeds the critical pressure is maintained.
  • ⁇ TM temperature difference
  • ⁇ TM temperature difference
  • control device 60 controls the valve opening of the second expansion device 21 such that a temperature difference ( ⁇ TM) between detected temperature (point B) of the intermediate heat exchanger bypass outlet thermistor 52 and detected temperature (e) of the intermediate heat exchanger bypass inlet thermistor 56 becomes larger than a temperature difference ( ⁇ TM) when refrigerant flows through the intermediate heat exchanger 13 in the gas-liquid two-phase state so that a state where pressure (intermediate pressure) of refrigerant after it is decompressed by the second expansion device 21 exceeds the critical pressure is maintained.
  • ⁇ TM temperature difference
  • control device 60 controls the valve opening of the second expansion device 21 such that when it is determine4ed that detected pressure of the high pressure-pressure detection device 51 rises and exceeds the first predetermined high pressure value, if intermediate pressure is equal to or lower than the critical pressure, the control device 60 starts the operation to increase the valve opening of the second expansion device 21 so that the intermediate pressure exceeds the critical pressure, and so that a state where pressure (intermediate pressure) of refrigerant after it is decompressed by the second expansion device 21 exceeds the critical pressure is maintained, a temperature difference ( ⁇ TH) between outlet temperature of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 and inlet temperature of refrigerant flowing through the main refrigerant circuit 10 at the intermediate heat exchanger 13 becomes larger than a temperature difference ( ⁇ TH) when refrigerant flows through the intermediate heat exchanger 13 in the gas-liquid two-phase state and larger than a temperature difference ( ⁇ TL) between inlet temperature of refrigerant flowing through the bypass refriger
  • control device 60 controls the valve opening of the second expansion device 21 such that a temperature difference ( ⁇ TH) between detected temperature (point B) of the intermediate heat exchanger bypass outlet thermistor 52 and detected temperature (point A) of the intermediate heat exchanger main refrigerant inlet thermistor 57 becomes larger than a temperature difference ( ⁇ TH) when refrigerant flows through the intermediate heat exchanger 13 in the gas-liquid two-phase state and larger than a temperature difference ( ⁇ TL) between detected temperature (e) of the intermediate heat exchanger bypass inlet thermistor 56 and detected temperature (b) of the intermediate heat exchanger main refrigerant outlet thermistor 58 so that a state where pressure (intermediate pressure) of refrigerant after it is decompressed by the second expansion device 21 exceeds the critical pressure is maintained.
  • ⁇ TH temperature difference
  • ⁇ TH temperature difference
  • ⁇ TH temperature difference
  • ⁇ TL temperature difference
  • the control device 60 controls such that a temperature difference ( ⁇ TM) between outlet temperature of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 and inlet temperature of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 becomes larger than a temperature difference when refrigerant flows through the intermediate heat exchanger 13 in the gas-liquid two-phase state as shown in Figs. 4 .
  • ⁇ TM temperature difference
  • control device 60 controls such that a temperature difference ( ⁇ TH) between outlet temperature of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 and inlet temperature of refrigerant flowing through the main refrigerant circuit 10 at the intermediate heat exchanger 13 becomes larger than a temperature difference ( ⁇ TL) between inlet temperature of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 and outlet temperature of refrigerant flowing through the main refrigerant circuit 10 at the intermediate heat exchanger 13.
  • ⁇ TH temperature difference
  • ⁇ TL temperature difference
  • control device 60 adjusts the valve opening of the second expansion device 21 such that a heat exchanging amount at the intermediate heat exchanger 13 becomes the maximum value, and sets a circulation amount of bypass refrigerant flowing through the bypass refrigerant circuit 20.
  • the control device 60 adjusts the valve opening of the second expansion device 21 such that ⁇ TM, ⁇ T and the heat exchanging amount of the intermediate heat exchanger 13 become the maximum values, and sets a circulation amount of bypass refrigerant flowing through the bypass refrigerant circuit 20.
  • 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 rotary element 11a and the high stage-side compression rotary element 11b, heats low temperature water by the utilization-side heat exchanger 12, and operates the transfer device 31 such that detected temperature of the heating medium outlet temperature thermistor 53 which is its heating temperature becomes target temperature.
  • low temperature water is taken out from a lower portion of the hot water storage tank 32b and heated by the utilization-side heat exchanger 12 and then, high temperature water is produced.
  • the high temperature water is introduced into the hot water storage tank 32b from an upper portion of the hot water storage tank 32b.
  • the refrigeration cycle device operates in a state described in Fig. 2(a) .
  • the refrigeration cycle device Since high temperature water is gradually stored in the hot water storage tank 32b from the upper portion, detected temperature of the heating medium inlet temperature thermistor 54 gradually rises, but if the detected temperature of the heating medium inlet temperature thermistor 54 exceeds the first predetermined temperature, the refrigeration cycle device operates in a state described in Fig. 2(b) .
  • operation is carried out to increase the valve opening of the second expansion device 21, operation frequencies of the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b are made to rise, a circulation amount of refrigerant flowing between the utilization-side heat exchanger 12 and the bypass refrigerant circuit 20 is increased, and detected pressure from the high pressure-pressure detection device 51 is made equal to a second predetermined high pressure value which is a target high pressure value.
  • the intermediate pressure supercritical operation mode is executed.
  • inlet temperature at the utilization-side heat exchanger 12 of heating medium becomes high, and an enthalpy difference (a-A) of refrigerant at the utilization-side heat exchanger 12 becomes small.
  • a-A enthalpy difference
  • the same operation action may be executed using, as a threshold value, the first predetermined high pressure value and the second predetermined high pressure value which are detected pressure of the high pressure-pressure detection device 51 instead of the first predetermined temperature and the third predetermined temperature which are detected temperature of the heating medium inlet temperature thermistor 54.
  • the compressing mechanism 11 may be composed of the two compressors in which the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b are independent from each other, and it is only necessary that operation frequency of at least the high stage-side compression rotary element 11b is lowered.
  • the control device 60 operates the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b, and heats circulation water by the utilization-side heat exchanger 12, but the control device 60 operates the transfer device 31 such that a temperature difference between detected temperature of the heating medium outlet temperature thermistor 53 which is a temperature difference of the circulation water and detected temperature of the heating medium inlet temperature thermistor 54 becomes equal to a target temperature difference.
  • high temperature water produced by the utilization-side heat exchanger 12 radiates heat in the heating terminal 32a and is utilized for heating a room, and low temperature water which radiates heat in the heating terminal 32a is again heated by the utilization-side heat exchanger 12.
  • control is performed such that a temperature difference between detected temperature of the heating medium outlet temperature thermistor 53 and detected temperature of the heating medium inlet temperature thermistor 54 becomes equal to the target temperature difference. Since detected temperature of the heating medium outlet temperature thermistor 53 is equal to or lower than the second predetermined temperature, the refrigeration cycle device is operated in the state described in Fig. 2(a) .
  • operation is carried out to increase the valve opening of the second expansion device 21, operation frequencies of the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b are made to rise, a circulation amount of refrigerant flowing between the utilization-side heat exchanger 12 and the bypass refrigerant circuit 20 is increased, and detected pressure from the high pressure-pressure detection device 51 is made equal to a second predetermined high pressure value which is a target high pressure value.
  • the intermediate pressure supercritical operation mode is executed.
  • the heating load becomes small, and an enthalpy difference (a-A) of refrigerant at the utilization-side heat exchanger 12 becomes small.
  • a-A enthalpy difference
  • the present invention can be utilized as a heating device using high temperature water while suppressing the rise of pressure of the high pressure refrigerant in the utilization-side heat exchanger 12 so that pressure of the high pressure refrigerant in the utilization-side heat exchanger 12 does not exceed a second predetermined high pressure value which is a target high pressure value.
  • the same operation action may be executed using, as a threshold value, the first predetermined high pressure value and the second predetermined high pressure value which are detected pressure of the high pressure-pressure detection device 51 instead of the second predetermined temperature and the fourth predetermined temperature.
  • the intermediate pressure supercritical operation mode will be described below using Fig. 5 .
  • This mode is executed by the control device 60 in a case where detected temperature of the heating medium inlet temperature thermistor 54 exceeds the first predetermined temperature when the hot water storage tank 32b is used in the utilization-side heating medium circuit 30, or in a case where detected temperature of the heating medium outlet temperature thermistor 53 exceeds the second predetermined temperature when the heating terminal 32a is used in the utilization-side heating medium circuit 30.
  • a solid line shows the case where detected temperature of the heating medium inlet temperature thermistor 54 exceeds the first predetermined temperature when the hot water storage tank 32b is used in the utilization-side heating medium circuit 30, or the case where detected temperature of the heating medium outlet temperature thermistor 53 exceeds the second predetermined temperature when the heating terminal 32a is used in the utilization-side heating medium circuit 30.
  • a broken line shows the case where detected temperature of the heating medium inlet temperature thermistor 54 is equal to or lower than the first predetermined temperature when the hot water storage tank 32b is used in the utilization-side heating medium circuit 30, or the case where detected temperature of the heating medium outlet temperature thermistor 53 is equal to or lower than the second predetermined temperature when the heating terminal 32a is used in the utilization-side heating medium circuit 30.
  • inlet temperature (point A) of refrigerant flowing through the main refrigerant circuit 10 at the intermediate heat exchanger 13 moves to increase the enthalpy and similarly, outlet temperature (point e) of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 and outlet temperature (point B) of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 also move to increase the enthalpy.
  • the control device 60 must control the valve opening of the second expansion device 21 such that a temperature difference ( ⁇ TM) between outlet temperature of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 and inlet temperature of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 becomes large.
  • control device 60 must control the valve opening of the second expansion device 21 such that as the intermediate pressure becomes high, a temperature difference ( ⁇ TM) between detected temperature (point B) of the intermediate heat exchanger bypass outlet thermistor 52 and detected temperature (e) of the intermediate heat exchanger bypass inlet thermistor 56 becomes large.
  • a value of pressure (intermediate pressure) of refrigerant after it is decompressed by the second expansion device 21 is calculated from discharged pressure of the high stage-side compression rotary element 11b, outlet temperature (point A) of refrigerant of the utilization-side heat exchanger 12 or temperature of utilization-side heating medium which flows into the utilization-side heat exchanger 12, inlet temperature (point e) of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13.
  • control device 60 may control the valve opening of the second expansion device 21 such that the temperature difference between the outlet temperature and inlet temperature of refrigerant flowing through the bypass refrigerant circuit 20 at the intermediate heat exchanger 13 becomes large as pressure of refrigerant after it is decompressed by the second expansion device 21 becomes high based on the value of the calculated intermediate pressure.
  • ⁇ TM is previously set in the control device 60 such that as the intermediate pressure becomes high, the value of ⁇ TM also becomes large.
  • the control device 60 may control the valve opening of the second expansion device 21 such that the intermediate pressure rises and the value of ⁇ TM also becomes large by reducing the valve opening of the first expansion device 14 and increasing the valve opening of the second expansion device 21 as detected temperature of the heating medium inlet temperature thermistor 54 or detected temperature of the heating medium outlet temperature thermistor 53 rises.
  • ⁇ TM is previously set in the control device 60 such that the value of ⁇ TM also becomes large as inlet temperature of the utilization-side heating medium to the utilization-side heat exchanger 12 or outlet temperature of utilization-side heating medium from the utilization-side heat exchanger 12 becomes high.
  • the compressing mechanism 11 may be configured such that the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b are composed of two independent compressors, and it is only necessary that operation frequency of at least the high stage-side compression rotary element 11b is lowered.
  • the compressing mechanism 11 may not be divided into the low stage-side compression rotary element 11a and the high stage-side compression rotary element 11b, and may be a single compression rotary element.
  • refrigerant from the bypass refrigerant circuit 20 joins up with refrigerant at a position where the compression rotary element is on an intermediate stage of compression.
  • refrigerant is carbon dioxide. This is because temperature of utilization-side heating medium when it is heated by carbon dioxide which is refrigerant can be made high in the utilization-side heat exchanger 12.
  • the utilization-side heating medium is water or antifreeze liquid
  • the utilization-side heating medium can be used to the heating terminal 32a or high temperature water can be stored in the hot water storage tank 32b.
  • the refrigeration cycle device of the present invention is composed of the main refrigerant circuit having the intermediate heat exchanger and the bypass refrigerant circuit, and a pressure difference between high pressure and intermediate pressure is not made large. According to this, since COP is not deteriorated, the refrigeration cycle device of the present invention is useful for liquid heating devices of refrigerant, air conditioning, hot water supply and a heating device.

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Claims (9)

  1. Dispositif à cycle de réfrigération comprenant : un circuit de fluide frigorigène principal (10) formé par liaison séquentielle, entre eux par l'intermédiaire d'un tuyau (16), d'un mécanisme de compression (11) composé d'un élément rotatif de compression, d'un échangeur de chaleur côté utilisation (12) pour chauffer un milieu chauffant côté utilisation par le fluide frigorigène évacué à partir de l'élément rotatif de compression, d'un échangeur de chaleur intermédiaire (13), d'un premier dispositif d'expansion (14) et d'un échangeur de chaleur côté source de chaleur (15) ;
    un circuit de fluide frigorigène de dérivation (20) dans lequel le fluide frigorigène bifurque à partir du tuyau (16) entre l'échangeur de chaleur côté utilisation (12) et le premier dispositif d'expansion (14), le fluide frigorigène bifurqué est décompressé par un deuxième dispositif d'expansion (21) et ensuite, le fluide frigorigène échange de la chaleur, dans l'échangeur de chaleur intermédiaire (13), avec le premier fluide frigorigène qui s'écoule à travers le circuit de fluide frigorigène principal (10) et le fluide frigorigène rejoint le fluide frigorigène qui est sur un étage intermédiaire de compression de l'élément rotatif de compression ;
    une thermistance d'entrée de fluide frigorigène principal (57) d'échangeur de chaleur intermédiaire qui détecte la température du fluide frigorigène s'écoulant hors de l'échangeur de chaleur côté utilisation (12),
    une thermistance de sortie de fluide frigorigène principal (58) d'échangeur de chaleur intermédiaire disposée au niveau du tuyau (16) située en aval de l'échangeur de chaleur intermédiaire (13) du circuit de fluide frigorigène principal (10) et en amont du premier dispositif d'expansion (14),
    une thermistance d'entrée de dérivation (56) d'échangeur de chaleur intermédiaire en aval du deuxième dispositif d'expansion (21) et en amont de l'échangeur de chaleur intermédiaire (13) disposée au niveau du circuit de fluide frigorigène de dérivation (20),
    une thermistance de sortie de dérivation (52) d'échangeur de chaleur intermédiaire en aval de l'échangeur de chaleur intermédiaire (13) disposée au niveau du circuit de fluide frigorigène de dérivation (20),
    un dispositif de commande (60),
    caractérisé en ce que le dispositif de commande (60) commande une ouverture de soupape du deuxième dispositif d'expansion (21)
    de telle sorte qu'une différence de température entre la température de sortie du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13) et la température d'entrée du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13) devient supérieure à une différence de température obtenue lorsque le fluide frigorigène s'écoule à travers l'échangeur de chaleur intermédiaire (13) dans un état diphasique gaz-liquide et
    de telle sorte qu'une différence de température entre la température de sortie du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13) et la température d'entrée du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène principal (10) au niveau de l'échangeur de chaleur intermédiaire (13) devient supérieure à une différence de température entre la température d'entrée du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13) et la température de sortie du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène principal (10) au niveau de l'échangeur de chaleur intermédiaire (13) et
    la pression du fluide frigorigène après sa décompression par le deuxième dispositif d'expansion (21) est maintenue dans un état dans lequel la pression dépasse une pression critique.
  2. Dispositif à cycle de réfrigération selon la revendication 1,
    le dispositif de commande (60) commandant l'ouverture de soupape du deuxième dispositif d'expansion (21) de telle sorte que la différence de température entre la température de sortie du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13) et la température d'entrée du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13) augmente lorsque la pression du fluide frigorigène après sa décompression par le deuxième dispositif d'expansion (21) augmente.
  3. Dispositif à cycle de réfrigération selon la revendication 1 ou 2,
    le dispositif de commande (60) déterminant le fait que la pression du fluide frigorigène après sa décompression par le deuxième dispositif d'expansion (21) est égale ou supérieure, ou non, à la pression critique à partir d'une valeur de pression du fluide frigorigène évacué du mécanisme de compression (11), à partir de la température de sortie du fluide frigorigène au niveau de l'échangeur de chaleur côté utilisation (12) et à partir de la température d'entrée du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13).
  4. Dispositif à cycle de réfrigération selon l'une quelconque des revendications 1 à 3, le fluide frigorigène étant du dioxyde de carbone.
  5. Dispositif de chauffage de liquide comprenant un circuit de milieu chauffant côté utilisation (30) qui fait circuler le milieu chauffant côté utilisation par un dispositif de transfert (31) comprenant le dispositif à cycle de réfrigération selon l'une quelconque des revendications 1 à 4.
  6. Dispositif de chauffage de liquide selon la revendication 5, comprenant en outre :
    une thermistance de température de sortie de milieu chauffant (53) pour détecter la température du milieu chauffant côté utilisation qui s'écoule hors de l'échangeur de chaleur côté utilisation (12) ; et
    une thermistance de température d'entrée de milieu chauffant (54) pour détecter la température du milieu chauffant côté utilisation qui s'écoule dans l'échangeur de chaleur côté utilisation (12),
    le dispositif de commande (60) actionnant le dispositif de transfert (31) de telle sorte que la température détectée de la thermistance de température de sortie de milieu chauffant (53) devient égale à la température cible et
    le dispositif de commande (60) commandant l'ouverture de soupape du deuxième dispositif d'expansion (21)
    de telle sorte que lorsque la température détectée de la thermistance de température d'entrée de milieu chauffant (54) dépasse une première température prédéterminée, la différence de température entre la température de sortie du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13) et la température d'entrée du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13) devient supérieure à la différence de température obtenue lorsque le fluide frigorigène s'écoule à travers l'échangeur de chaleur intermédiaire (13) dans l'état diphasique gaz-liquide et
    de telle sorte que la différence de température entre la température de sortie du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13) et la température d'entrée du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène principal (10) au niveau de l'échangeur de chaleur intermédiaire (13) devient supérieure à la différence de température entre la température d'entrée du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13) et la température de sortie du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène principal (10) au niveau de l'échangeur de chaleur intermédiaire (13).
  7. Dispositif de chauffage de liquide selon la revendication 5, comprenant en outre :
    une thermistance de température de sortie de milieu chauffant (53) pour détecter la température du milieu chauffant côté utilisation qui s'écoule hors de l'échangeur de chaleur côté utilisation (12) ; et
    une thermistance de température d'entrée de milieu chauffant (54) pour détecter la température du milieu chauffant côté utilisation qui s'écoule dans l'échangeur de chaleur côté utilisation (12),
    le dispositif de commande (60) actionnant le dispositif de transfert (31) de telle sorte qu'une différence de température entre la température détectée de la thermistance de température de sortie de milieu chauffant (53) et la température détectée de la thermistance de température d'entrée de milieu chauffant (54) devient égale à une différence de température cible et
    le dispositif de commande (60) commandant l'ouverture de soupape du deuxième dispositif d'expansion (21)
    de telle sorte que lorsque la température détectée de la thermistance de température de sortie de milieu chauffant (53) dépasse une deuxième température prédéterminée, la différence de température entre la température de sortie du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13) et la température d'entrée du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13) devient supérieure à la différence de température obtenue lorsque le fluide frigorigène s'écoule à travers l'échangeur de chaleur intermédiaire (13) dans l'état diphasique gaz-liquide et
    de telle sorte que la différence de température entre la température de sortie du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13) et la température d'entrée du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène principal (10) au niveau de l'échangeur de chaleur intermédiaire (13) devient supérieure à la différence de température entre la température d'entrée du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13) et la température de sortie du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène principal (10) au niveau de l'échangeur de chaleur intermédiaire (13).
  8. Dispositif de chauffage de liquide selon l'une quelconque des revendications 5 à 7,
    le dispositif de commande (60) déterminant le fait que la pression du fluide frigorigène après sa décompression par le deuxième dispositif d'expansion (21) est égale ou supérieure, ou non, à la pression critique à partir d'une valeur de pression du fluide frigorigène évacué du mécanisme de compression (11), à partir de la température du milieu chauffant côté utilisation qui s'écoule dans l'échangeur de chaleur côté utilisation (12) et à partir de la température d'entrée du fluide frigorigène s'écoulant à travers le circuit de fluide frigorigène de dérivation (20) au niveau de l'échangeur de chaleur intermédiaire (13).
  9. Dispositif de chauffage de liquide selon l'une quelconque des revendications 5 à 8, le milieu chauffant côté utilisation étant de l'eau ou un liquide antigel.
EP19191742.6A 2019-01-18 2019-08-14 Dispositif à cycle de réfrigération et dispositif de chauffage de liquide le comprenant Active EP3683520B1 (fr)

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JP2010054194A (ja) * 2008-07-31 2010-03-11 Daikin Ind Ltd 冷凍装置
JP4833330B2 (ja) * 2009-11-27 2011-12-07 三菱電機株式会社 超臨界蒸気圧縮式冷凍サイクルおよびこれを用いる冷暖房空調設備とヒートポンプ給湯機
WO2011135616A1 (fr) 2010-04-27 2011-11-03 三菱電機株式会社 Dispositif de cycle de refroidissement
JP2014105891A (ja) * 2012-11-26 2014-06-09 Panasonic Corp 冷凍サイクル装置及びそれを備えた温水生成装置
WO2017061233A1 (fr) * 2015-10-05 2017-04-13 株式会社デンソー Dispositif à cycle frigorifique
US11175072B2 (en) * 2016-03-23 2021-11-16 Mitsubishi Electric Corporation Air conditioner

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ES2904478T3 (es) 2022-04-05
EP3683520A1 (fr) 2020-07-22
JP7012208B2 (ja) 2022-01-28
DK3683520T3 (da) 2021-12-20

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