WO2010103825A1 - Système de pompe à chaleur - Google Patents

Système de pompe à chaleur Download PDF

Info

Publication number
WO2010103825A1
WO2010103825A1 PCT/JP2010/001698 JP2010001698W WO2010103825A1 WO 2010103825 A1 WO2010103825 A1 WO 2010103825A1 JP 2010001698 W JP2010001698 W JP 2010001698W WO 2010103825 A1 WO2010103825 A1 WO 2010103825A1
Authority
WO
WIPO (PCT)
Prior art keywords
temperature
heat exchanger
heat
flow rate
heat pump
Prior art date
Application number
PCT/JP2010/001698
Other languages
English (en)
Japanese (ja)
Inventor
山田拓郎
奥田則之
藤本修二
吉見敦史
Original Assignee
ダイキン工業株式会社
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 ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Priority to US13/256,270 priority Critical patent/US20120000237A1/en
Priority to CN201080012689XA priority patent/CN102348942A/zh
Priority to EP10750582A priority patent/EP2407734A1/fr
Publication of WO2010103825A1 publication Critical patent/WO2010103825A1/fr

Links

Images

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
    • 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
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/072—Intercoolers therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—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

Definitions

  • the present invention relates to a heat pump system.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2004-177067
  • the subject of this invention is providing the heat pump system which can improve cycle efficiency in the process of the heat load by a secondary refrigerant.
  • the heat pump system of the first invention includes a heat pump circuit, a first heat load circuit, a first heat exchanger, a second heat exchanger, a first flow rate adjusting mechanism, and a control unit.
  • the heat pump circuit has at least a low-stage compression mechanism, a high-stage compression mechanism, an expansion mechanism, and an evaporator.
  • the primary refrigerant circulates.
  • the first heat load circuit includes a first branch portion, a second branch portion, a first branch path, a second branch path, and a first heat load processing section.
  • the first branch path connects the first branch portion and the second branch portion.
  • the second branch path connects the first branch portion and the second branch portion without joining the first branch path.
  • the first fluid circulates.
  • the first heat exchanger performs heat exchange between the primary refrigerant that flows from the discharge side of the low-stage compression mechanism toward the suction side of the high-stage compression mechanism and the first fluid that flows through the first branch path. Make it.
  • the second heat exchanger exchanges heat between the primary refrigerant that flows from the high-stage compression mechanism toward the expansion mechanism and the first fluid that flows through the second branch path.
  • the first flow rate adjusting mechanism is capable of adjusting at least one of the flow rate of the first fluid in the first branch path and the flow rate of the first fluid in the second branch path.
  • the control unit performs flow rate adjustment control for operating the first flow rate adjustment mechanism.
  • the first flow rate adjusting mechanism is operated so as to reduce the difference between the temperature of the first fluid flowing through the portion of the second branch passage that has passed through the second heat exchanger.
  • a compression mechanism may be further provided in addition to the high-stage compression mechanism and the low-stage compression mechanism, and the case where a multistage compression system is used is naturally included in the scope of the present invention.
  • the heat pump system according to a second aspect is the heat pump system according to the first aspect, wherein the temperature of the primary refrigerant flowing into the first heat exchanger is equal to or higher than the temperature of the first fluid flowing into the first heat exchanger.
  • the temperature of the primary refrigerant flowing into the first heat exchanger while the temperature of the primary refrigerant flowing into the second heat exchanger is equal to or higher than the temperature of the first fluid flowing into the second heat exchanger.
  • the low-stage compression mechanism and the high-stage compression mechanism are such that both the temperatures of the primary refrigerant flowing into the second heat exchanger are equal to or higher than the temperature corresponding to the first heat load required in the first heat load processing unit. Control the output of.
  • the temperature of the first fluid can be reliably increased by the primary refrigerant flowing into the first heat exchanger without lowering the temperature of the first fluid flowing into the first heat exchanger. And it can prevent that the discharge refrigerant
  • the temperature of the first fluid can be reliably increased by the primary refrigerant flowing into the second heat exchanger without lowering the temperature of the first fluid flowing into the second heat exchanger. And it becomes possible to respond
  • a heat pump system is the heat pump system according to the second aspect, wherein the first thermal load circuit includes a portion between the first thermal load processing unit and the first branch portion, a first thermal load processing unit, and a second branch portion. And a first thermal load bypass flow rate adjustment mechanism capable of adjusting the flow rate of the first fluid passing through the first thermal load bypass circuit.
  • the control unit is a target value of the temperature of the first fluid flowing through a portion of the first branch path that has passed through the first heat exchanger and a portion of the second branch path that has passed through the second heat exchanger. Control is performed so that the target value of the temperature of the first fluid flowing through the temperature exceeds the temperature corresponding to the first heat load.
  • the control unit operates the first thermal load bypass flow rate adjustment mechanism to operate the first thermal load bypass circuit so that the temperature of the first fluid supplied to the first thermal load processing unit becomes a temperature corresponding to the first thermal load. The flow rate of the first fluid passing through is adjusted.
  • the first heat load bypass flow rate adjusting mechanism causes the first heat to flow.
  • the part which passed the 2nd heat exchanger among the temperature of the 1st fluid which flows through the part which passed the 1st heat exchanger among the 1st branch, and the 2nd branch Even if the temperature of the first fluid flowing through the first temperature may exceed the temperature corresponding to the first heat load, the temperature of the first fluid supplied to the first heat load processing unit can be brought close to the temperature corresponding to the first load. become.
  • a heat pump system is the heat pump system according to the second aspect, wherein the control unit is a target value of the temperature of the first fluid flowing through a portion of the first branch path that has passed through the first heat exchanger in the flow rate adjustment control. And the target value of the temperature of the 1st fluid which flows through the part which passed the 2nd heat exchanger among 2nd branch paths is controlled so that it may become temperature corresponding to the 1st heat load.
  • the control unit is a target value of the temperature of the first fluid flowing through a portion of the first branch path that has passed through the first heat exchanger in the flow rate adjustment control.
  • the target value of the temperature of the 1st fluid which flows through the part which passed the 2nd heat exchanger among 2nd branch paths is controlled so that it may become temperature corresponding to the 1st heat load.
  • the control unit is a target value of the temperature of the first fluid flowing through a portion of the first branch path that has passed through the first heat exchanger in the flow rate adjustment control.
  • the first heat load circuit is provided with a function of adjusting the temperature of the first fluid heading to the first heat load processing unit. It becomes possible to eliminate the necessity.
  • the heat pump system is the heat pump system according to any one of the second to fourth aspects of the present invention, wherein the control unit controls the compression ratio in the low-stage compression mechanism and the compression ratio in the high-stage compression mechanism in the flow rate adjustment control.
  • the control unit controls the compression ratio in the low-stage compression mechanism and the compression ratio in the high-stage compression mechanism in the flow rate adjustment control.
  • the difference between the compression ratio in the low-stage compression mechanism and the compression ratio in the high-stage compression mechanism is At least one of the low-stage compression mechanism, the high-stage compression mechanism, and the expansion mechanism is controlled so as to reduce the size.
  • the temperature of the primary refrigerant flowing into the second heat exchanger is adjusted so that the temperature of the primary refrigerant flowing into the first heat exchanger is equal to or higher than the temperature of the first fluid flowing into the first heat exchanger.
  • Both the temperature of the primary refrigerant flowing into the first heat exchanger and the temperature of the primary refrigerant flowing into the second heat exchanger while corresponding to the temperature of the first fluid flowing into the second heat exchanger correspond to the first heat load.
  • the heat pump system according to a sixth aspect of the present invention is the heat pump system according to the fifth aspect of the present invention, wherein when the flow rate adjustment control is performed, the control unit causes the low-stage compression mechanism to operate when the discharge temperature of the primary refrigerant of the low-stage compression mechanism increases.
  • Low-stage suction superheat control is performed to increase the superheat of the primary refrigerant to be sucked.
  • the target value of the primary refrigerant discharge temperature of the low-stage compression mechanism is high, the compression ratio of the low-stage compression mechanism tends to increase. This also increases the compression ratio of the high-stage compression mechanism. For this reason, the required driving force of the compression mechanism increases and the energy consumption increases.
  • the compression ratio of the low-stage compression mechanism is reduced by reducing the degree of superheat of the primary refrigerant sucked by the low-stage compression mechanism.
  • a heat pump system is the heat pump system according to the sixth aspect, wherein the heat pump circuit flows toward the expansion mechanism after passing through the primary refrigerant sucked by the low-stage compression mechanism and the second heat exchanger. It further has a primary inter-refrigerant heat exchanger that exchanges heat with the primary refrigerant.
  • the control unit performs low-stage suction superheat degree control using a primary refrigerant heat exchanger. In this heat pump system, heat for cooling the primary refrigerant before flowing into the expansion mechanism can be recovered as heat for increasing the degree of superheat of the primary refrigerant sucked by the low-stage compression mechanism.
  • a heat pump system is the heat pump system according to any one of the fifth to seventh aspects of the present invention, wherein the control unit performs the flow rate adjustment control from the first heat load processing unit to the first heat exchanger and the second heat exchange system.
  • the control unit performs the flow rate adjustment control from the first heat load processing unit to the first heat exchanger and the second heat exchange system.
  • the load can be handled.
  • the density of the primary refrigerant sucked by the low-stage compression mechanism can be increased, and the circulation amount of the primary refrigerant can be increased. This makes it possible to increase the capacity of the heat pump circuit while accommodating load fluctuations.
  • a heat pump system is the heat pump system according to the eighth aspect of the present invention, having a second heat load portion, and a second heat load circuit through which the second fluid circulates and a second heat load circuit through which the second heat load circuit circulates.
  • a third heat exchanger that exchanges heat between the fluid and a primary refrigerant that is on the way from the high-stage compression mechanism toward the second heat exchanger;
  • the heat of the primary refrigerant discharged from the high-stage compression mechanism can only be used for both the heat load process in the first heat load circuit and the heat load process in the second heat load circuit. Instead, it is possible to use the second heat load circuit outside the temperature range required for the first heat load circuit.
  • a heat pump system is the heat pump system according to the ninth aspect of the invention, wherein the second fluid passing from the second heat load processing section to the third heat exchanger out of the second fluid passing through the second heat load circuit, It further includes a fourth heat exchanger that exchanges heat with the primary refrigerant that has passed through the heat exchanger and is still on its way to the expansion mechanism.
  • the high-stage compression mechanism is Of the primary refrigerant to be discharged, heat exchange with the primary refrigerant at a high temperature and heat exchange with the primary refrigerant at a low temperature are assigned to heat exchange with the second fluid, and the primary refrigerant at the intermediate temperature is heat with the first fluid.
  • heat exchange in the second heat exchanger, the third heat exchanger, and the fourth heat exchanger can be performed while the temperature difference between the first fluid and the second fluid and the primary refrigerant is kept small. Therefore, the heat exchange efficiency can be improved.
  • a heat pump system is the heat pump system according to the ninth or tenth aspect of the invention, wherein the controller is configured such that the target value of the temperature of the primary refrigerant discharged from the low-stage compression mechanism is the primary refrigerant discharged from the high-stage compression mechanism.
  • the second heat load circuit is set so that the temperature of the primary refrigerant passing through the third heat exchanger approaches the target value of the temperature of the primary refrigerant discharged by the low-stage compression mechanism when the temperature is lower than the target value of the temperature.
  • the circulation amount of the circulating second fluid is adjusted.
  • the maximum temperature of the primary refrigerant flowing through the first heat exchanger and the maximum temperature of the primary refrigerant flowing through the second heat exchanger are brought close to each other, thereby passing through the first heat exchanger in the first branch path. It becomes easy to make the temperature of the 1st fluid which flows through the part and the temperature of the 1st fluid which flows through the part which passed the 2nd heat exchanger out of the 2nd branch way close. For example, when it is desired to keep the flow rate of the first fluid supplied to the first heat load processing unit low, the time for the first fluid to pass through the first heat exchanger or the time for the second fluid to pass through the second heat exchanger.
  • the temperature of the primary refrigerant flowing through the first heat exchanger approaches the temperature of the primary refrigerant flowing through the second heat exchanger. Therefore, either the temperature of the first fluid flowing through the portion of the first branch passage that has passed through the first heat exchanger or the temperature of the first fluid flowing through the portion of the second branch passage that has passed through the second heat exchanger. With respect to the above, it becomes possible to converge to a value in the vicinity of the temperature of the primary refrigerant flowing through the first heat exchanger (the temperature of the primary refrigerant flowing through the second heat exchanger).
  • a heat pump system is the heat pump system according to any one of the ninth to eleventh aspects of the present invention, wherein the second heat load processing unit is a hot water supply tank.
  • the second fluid is water for hot water supply.
  • hot water can be produced using the temperature of the primary refrigerant discharged from the high-stage compression mechanism.
  • the heat pump system according to a thirteenth aspect of the present invention is the heat pump system according to any one of the second to twelfth aspects of the present invention, wherein the control unit operates the first flow rate adjustment mechanism in the flow rate adjustment control, thereby operating the first of the first branch paths.
  • the control unit operates the first flow rate adjustment mechanism in the flow rate adjustment control, thereby operating the first of the first branch paths.
  • the flow rate of the lower temperature is decreased.
  • the temperature of the first fluid flowing through the portion of the first branch passage that has passed through the first heat exchanger, and the first fluid flowing through the portion of the second branch passage that has passed through the second heat exchanger By lowering the flow rate of the lower one of the temperatures, the flow rate of the lower temperature is lowered and the heating time can be lengthened. This makes it possible to increase the amount of heat recovered from the primary refrigerant on the side of the first heat exchanger and the second heat exchanger where the flow rate has been reduced. For example, when the first heat exchanger or the second heat exchanger is passed at a high flow rate without being heated to the inlet temperature of the primary refrigerant, the passage speed is decreased and the heat exchange time is increased. By doing so, the amount of heat recovery can be increased.
  • a heat pump system is the heat pump system according to the thirteenth aspect, wherein the first flow rate adjusting mechanism is configured to obtain a ratio between a flow rate of the first fluid flowing through the first branch path and a flow rate of the first fluid flowing through the second branch path. It is adjustable.
  • the control unit operates the first flow rate adjustment mechanism to keep the flow rate of the first fluid supplied to the first thermal load processing unit constant, and the first heat exchange in the first branch path.
  • the flow rate ratio of the lower temperature is lowered.
  • the temperature of the first fluid flowing through the portion of the first branch passage that has passed through the first heat exchanger and the second branch passage of the second branch passage are passed.
  • the higher flow rate increases and the heating time becomes shorter, and the lower flow rate decreases and the heating time becomes longer.
  • the temperature of the 1st fluid which flows through the part which passed the 1st heat exchanger among the 1st branch paths, and the temperature of the 1st fluid which flows through the part which passed the 2nd heat exchanger among the 2nd branch paths Both can be changed to reduce the temperature difference.
  • the first heat load can be maintained by maintaining the flow rate of the first fluid supplied to the first heat load processing unit. It becomes possible to cope with the heat load in the processing section.
  • the heat pump system of the fifteenth aspect of the invention is the heat pump system of the thirteenth aspect of the invention, wherein the first flow rate adjusting mechanism can adjust the flow rate of the first fluid supplied to the first thermal load processing unit.
  • the control unit includes a temperature of the first fluid flowing through a portion of the first branch passage that has passed the first heat exchanger, and a temperature of the first fluid flowing through a portion of the second branch passage that has passed the second heat exchanger.
  • the temperature of the first fluid that flows through the portion of the first branch passage that has passed through the first heat exchanger and the temperature of the first fluid that flows through the portion of the second branch passage that has passed through the second heat exchanger If the flow rate of the first fluid supplied to the first thermal load processing unit is lowered when the flow rate ratio of the lower temperature is smaller, the temperature of the lower temperature is higher than the temperature increase of the higher temperature. The rise will be larger. Thereby, it becomes possible to change so as to reduce the temperature difference. Moreover, when the heat load in the first heat load processing unit is reduced, not only can the temperature difference be reduced, but also the heat load in the first heat load processing unit can be handled.
  • a heat pump system is the heat pump system according to the thirteenth aspect, wherein the first flow rate adjusting mechanism calculates a ratio between a flow rate of the first fluid flowing through the first branch path and a flow rate of the first fluid flowing through the second branch path.
  • a ratio adjusting unit for adjusting and a flow rate adjusting unit for adjusting the flow rate of the first fluid supplied to the first thermal load processing unit are included.
  • the control unit operates the first flow rate adjustment mechanism to change the temperature of the first fluid flowing through the portion of the first branch passage that has passed through the first heat exchanger and the second branch passage of the second branch passage.
  • One of the temperature of the first fluid flowing through the portion that has passed through the two heat exchangers and the flow rate that exceeds the temperature corresponding to the first heat load is increased and / or the temperature that does not satisfy the temperature corresponding to the first heat load
  • the controller supplies the first heat load to the first heat load processor when the temperature of the first fluid supplied to the first heat load processor exceeds the temperature corresponding to the first heat load. As the temperature of the fluid rises, the flow rate of the first fluid supplied to the first thermal load processing unit is lowered.
  • the temperature of the first fluid that flows through the portion of the first branch passage that has passed through the first heat exchanger and the temperature of the first fluid that flows through the portion of the second branch passage that has passed through the second heat exchanger can be made to be an amount corresponding to the thermal load in the first thermal load processing unit.
  • a heat pump system is the heat pump system according to any one of the first to sixteenth aspects of the present invention, wherein the first fluid grasps the temperature of the first fluid flowing through the portion of the first branch passage that has passed through the first heat exchanger. It further comprises a branch temperature detecting means and a second branch temperature detecting means for grasping the temperature of the first fluid flowing through the portion of the second branch that has passed through the second heat exchanger.
  • the temperature of the first fluid that flows through the portion of the first branch passage that has passed through the first heat exchanger and the temperature of the first fluid that flows through the portion of the second branch passage that has passed through the second heat exchanger Therefore, it is possible to improve the accuracy of the flow rate adjustment control.
  • a heat pump system is the heat pump system according to any one of the first to sixteenth aspects, further comprising a branching portion temperature detecting means and a merging portion temperature detecting means.
  • the branching portion temperature detecting means includes the temperature of the first fluid flowing through the portion of the first branch passage that has passed through the first heat exchanger and the first fluid flowing through the portion of the second branch passage that has passed through the second heat exchanger. Know at least one of the temperatures.
  • the merged part temperature detecting means grasps the temperature of the first fluid that flows toward the first thermal load processing unit after the first fluid that has passed through the first branch path and the first fluid that has passed through the second branch path have merged. To do.
  • the temperature of the first fluid that flows through the portion of the first branch passage that has passed through the first heat exchanger and the temperature of the first fluid that flows through the portion of the second branch passage that has passed through the second heat exchanger can be directly grasped by the branching part temperature detecting means, and the temperature of the first fluid after joining can be directly grasped by the joining part temperature detecting means. Thereby, it is possible to improve the accuracy of the flow rate adjustment control by controlling so that the difference between the temperature grasped by the branching portion temperature detecting means and the temperature grasped by the joining portion temperature detecting means becomes small.
  • a heat pump system is the heat pump system according to any one of the first to sixteenth aspects of the present invention, the first branch flow rate detecting means for grasping the flow rate of the first fluid flowing through the first branch, and the second branch And a second branch flow rate detecting means for grasping the flow rate of the first fluid flowing through the first fluid.
  • the flow rate of the first fluid flowing through the first branch path and the flow rate of the first fluid flowing through the second branch path can be directly grasped, so that the accuracy of the flow rate control can be improved.
  • a heat pump system is the heat pump system according to any one of the first to sixteenth aspects of the invention, wherein at least one of a flow rate of the first fluid flowing through the first branch path and a flow rate of the first fluid flowing through the second branch path.
  • the flow rate of the first fluid that flows toward the first thermal load processing unit after the branching part flow rate detecting means for grasping one of the first fluid flowing through the first branching channel and the first fluid flowing through the second branching channel join together.
  • a merging partial flow rate detecting means for grasping.
  • either the flow rate of the first fluid flowing through the first branch passage or the flow rate of the first fluid flowing through the second branch passage is determined by the branching portion flow rate detecting means, and the flow rate of the first fluid after joining is joined. It is possible to directly grasp the flow rate detection means. As a result, the flow rate on the side of the first branch path and the second branch path on which the branch partial flow rate detection unit is not provided is determined by the flow rate determined by the branch partial flow rate detection unit and the flow rate determined by the merged partial flow rate detection unit. It can be grasped as a difference. Thereby, it is possible to improve the accuracy of the flow rate adjustment control.
  • the heat pump system according to a twenty-first aspect of the present invention is the heat pump system according to any one of the first to twentieth aspects of the invention, wherein, in the first heat exchanger, the discharge side of the low-stage compression mechanism is directed toward the suction side of the high-stage compression mechanism.
  • the flowing primary refrigerant and the first fluid flowing through the first branch path are in a counterflow relationship.
  • the primary refrigerant that flows from the high-stage compression mechanism toward the expansion mechanism and the first fluid that flows through the second branch passage are in a counterflow relationship.
  • a heat pump system is the heat pump system according to any one of the first to 21st aspects of the present invention, wherein the first heat load processing section is a heat exchanger for heating that heats the air in the target space.
  • the first fluid is a secondary refrigerant. In this heat pump system, it is possible to warm the space in which the first thermal load processing unit is arranged.
  • a heat pump system is the heat pump system according to any one of the first to twenty-second aspects of the invention, wherein the low-stage compression mechanism and the high-stage compression mechanism are respectively common for performing compression work by being rotationally driven. It has a rotation axis.
  • this heat pump system it is possible to increase the driving efficiency by providing a phase difference of 180 degrees while sharing the rotating shaft.
  • a heat pump system is the heat pump system according to any one of the first to twenty-third aspects, wherein the control unit sets the discharge pressure of the high-stage compression mechanism to a pressure equal to or higher than the critical pressure of the primary refrigerant in the flow rate adjustment control. Is maintained. It is used in an environment where the ambient temperature of the first heat load processing unit is a temperature lower than the critical temperature of the primary refrigerant.
  • the primary refrigerant in a state exceeding the critical pressure is supplied to the heat load at a temperature lower than the critical temperature of the primary refrigerant, so that the gradient of the primary refrigerant isotherm on the Mollier diagram is gentle. Heat dissipation treatment can be performed in the area. For this reason, it becomes possible to perform an operation in which the difference in enthalpy between the start and end of the heat release process of the primary refrigerant is increased.
  • the primary refrigerant is carbon dioxide.
  • a refrigeration cycle of a heat pump circuit can be realized using natural refrigerant.
  • the first invention it is possible to improve the processing efficiency of the heat load in the first load heat exchanger by the heat pump system.
  • the second invention it becomes possible to cope with the heat load in the first load heat exchanger only by the amount of heat obtained by the first fluid in the first heat exchanger and the second heat exchanger.
  • 3rd invention in order to raise the efficiency of a heat pump circuit, it passes through a 2nd heat exchanger among the temperature of the 1st fluid which flows through the part which passed the 1st heat exchanger among the 1st branch, and the 2nd branch. Even if the temperature of the first fluid flowing through the part exceeds the temperature corresponding to the first heat load, the temperature of the first fluid supplied to the first heat load processing unit is brought close to the temperature corresponding to the first load. Is possible.
  • the fourth aspect of the invention it is possible to avoid a state in which the temperature of the first fluid flowing through the first heat load circuit greatly exceeds the temperature corresponding to the first heat load, and it is possible to effectively reduce the heat dissipation loss. .
  • the fifth aspect of the invention not only the heat dissipation loss due to the first fluid can be reduced, but also the heat load in the first heat load processing unit can be realized simultaneously with a small driving force, and the efficiency can be further improved.
  • the degree of superheat of the primary refrigerant sucked by the low-stage compression mechanism be increased, but also a reduction in the amount of passage of the primary refrigerant in the expansion mechanism can be suppressed, and the ability can be improved. become.
  • the heat of the primary refrigerant discharged from the high-stage compression mechanism can only be used for both the heat load process in the first heat load circuit and the heat load process in the second heat load circuit. Instead, it is possible to use the second heat load circuit outside the temperature range required for the first heat load circuit.
  • heat exchange is performed in the second heat exchanger, the third heat exchanger, and the fourth heat exchanger while the temperature difference between the first fluid and the second fluid and the primary refrigerant is kept small. Therefore, the heat exchange efficiency can be improved.
  • the temperature of the first fluid that flows through the portion of the first branch path that has passed through the first heat exchanger and the temperature of the first fluid that flows through the portion of the second branch path that has passed through the second heat exchanger It becomes easy to approach.
  • hot water can be produced using the temperature of the primary refrigerant discharged from the high-stage compression mechanism.
  • the temperature of the first fluid flowing through the portion of the first branch passage that has passed through the first heat exchanger and the temperature of the first fluid flowing through the portion of the second branch passage that has passed through the second heat exchanger. Both can be changed so as to reduce the temperature difference, and if there is no change in the thermal load in the first thermal load processing unit, not only the temperature difference can be reduced but also the first thermal load processing unit. By maintaining the flow rate of the first fluid supplied to, it becomes possible to cope with the thermal load in the first thermal load processing section.
  • the fifteenth aspect it is possible to change so as to reduce the temperature difference. Further, when the heat load in the first heat load processing unit is reduced, not only can the temperature difference be reduced, but also the heat load in the first heat load processing unit can be handled.
  • the flow rate of the first fluid flowing through the first thermal load circuit can be made to be an amount corresponding to the thermal load in the first thermal load processing unit.
  • it is possible to improve the accuracy of the flow rate adjustment control by controlling so that the difference between the temperature grasped by the branching portion temperature detecting means and the temperature grasping by the joining portion temperature detecting means becomes small. .
  • the driving force of the compression mechanism can be kept small.
  • a refrigeration cycle of a heat pump circuit can be realized using a natural refrigerant.
  • FIG. 1 is a schematic configuration diagram of a heat pump system according to a first embodiment of the present invention.
  • FIG. 3 is a pressure-enthalpy diagram of the heat pump circuit according to the first embodiment.
  • FIG. 3 is a temperature-entropy diagram of the heat pump circuit according to the first embodiment.
  • It is a schematic block diagram of the heat pump system concerning 2nd Embodiment.
  • It is a schematic block diagram of the heat pump system concerning 3rd Embodiment.
  • It is a schematic block diagram of the heat pump system concerning 4th Embodiment.
  • It is a schematic block diagram of the heat pump system concerning 5th Embodiment.
  • It is a schematic block diagram of the heat pump system concerning the modification A of 5th Embodiment.
  • FIG. 1 is a schematic configuration diagram of a heat pump system 1 according to a first embodiment which is an embodiment of the present invention.
  • the heat pump system 1 includes a heat pump circuit 10, a heating circuit 60, a hot water supply circuit 90, an intermediate pressure water heat exchanger 40, and a high pressure water heat exchanger 50.
  • the heat pump system 1 is a system that not only uses the heat obtained by the heat pump circuit 10 as heating heat via the heating circuit 60 but also uses it as hot water supply heat via the hot water supply circuit 90.
  • the intermediate pressure water heat exchanger 40 In the intermediate pressure water heat exchanger 40, heat exchange is performed between carbon dioxide as a primary refrigerant circulating in the heat pump circuit 10 and water as a secondary refrigerant circulating in the heating circuit 60.
  • the high-pressure water heat exchanger 50 includes a first high-pressure water heat exchanger 51, a second high-pressure water heat exchanger 52, and a third high-pressure water heat exchanger 53.
  • heat exchange is performed between carbon dioxide as a primary refrigerant circulating in the heat pump circuit 10 and hot water supply water circulating in the hot water supply circuit 90.
  • the heat pump circuit 10 is a circuit using a natural refrigerant in which carbon dioxide as a primary refrigerant is circulated.
  • the heat pump circuit 10 includes a low-stage compressor 21, a high-stage compressor 25, an economizer heat exchanger 7, an injection path 70, a primary inter-refrigerant heat exchanger 8, a primary bypass 80, an expansion valve 5a, an evaporator 4, an intermediate
  • the pressure tube 23, the high pressure tube 27, the low pressure tube 20, the fan 4 f, and the control unit 11 are provided.
  • the evaporator 4 is installed outdoors, for example.
  • the intermediate pressure pipe 23 connects the discharge side of the low-stage compressor 21 and the suction side of the high-stage compressor 25.
  • the intermediate pressure tube 23 includes a first intermediate pressure tube 23a, a second intermediate pressure tube 23b, a third intermediate pressure tube 23c, and a fourth intermediate pressure tube 23d.
  • the first intermediate pressure pipe 23 a connects the discharge side of the low-stage compressor 21 and the upstream end of the intermediate-pressure water heat exchanger 40 via the low-stage discharge point B.
  • An intermediate pressure temperature sensor 23T for detecting the temperature of the passing primary refrigerant is attached to the first intermediate pressure pipe 23a.
  • the second intermediate pressure pipe 23b passes through the intermediate pressure water heat exchanger 40 while flowing carbon dioxide as the primary refrigerant therein so as not to mix with the heating water as the secondary refrigerant. .
  • the third intermediate pressure pipe 23c connects the downstream end of the intermediate pressure water heat exchanger 40 and the injection junction point D via the intermediate pressure water heat exchanger passage point C.
  • the fourth intermediate pressure pipe 23d connects the injection merging point D and the suction side of the high-stage compressor 25.
  • a high stage suction pressure sensor 24P that detects the pressure of the passing primary refrigerant and a high stage suction temperature sensor 24T that detects the temperature of the passing primary refrigerant are attached to the fourth intermediate pressure pipe 23d.
  • the high-pressure pipe 27 connects the discharge side of the high-stage compressor 25 and the expansion valve 5 or the primary bypass expansion valve 5b.
  • the high pressure pipe 27 includes a first high pressure pipe 27a, a second high pressure pipe 27b, a third high pressure pipe 27c, a fourth high pressure pipe 27d, a fifth high pressure pipe 27e, a sixth high pressure pipe 27f, a seventh high pressure pipe 27g, and an eighth high pressure pipe.
  • a tube 27h, a ninth high-pressure tube 27i, a tenth high-pressure tube 27j, an eleventh high-pressure tube 27k, a twelfth high-pressure tube 271 and a thirteenth high-pressure tube 27m are provided.
  • the first high-pressure pipe 27a connects the discharge side of the high-stage compressor 25 and the first high-pressure water heat exchanger 51 via the high-stage discharge point E.
  • a high pressure sensor 27P for detecting the pressure of the passing primary refrigerant and a high pressure temperature sensor 27T for detecting the temperature of the passing primary refrigerant are attached to the first high pressure pipe 27a.
  • the second high-pressure pipe 27 b passes through the first high-pressure water heat exchanger 51 while flowing carbon dioxide as a primary refrigerant therein so as not to mix with hot water.
  • the third high-pressure pipe 27c connects the downstream end of the first high-pressure water heat exchanger 51 and the upstream end of the second high-pressure water heat exchanger 52 via the first high-pressure point F. Yes.
  • the fourth high-pressure pipe 27d passes through the second high-pressure water heat exchanger 52 while flowing carbon dioxide as the primary refrigerant therein so that it does not mix with water as the secondary refrigerant for heating.
  • the fifth high-pressure pipe 27e connects the downstream end of the second high-pressure water heat exchanger 52 and the upstream end of the third high-pressure water heat exchanger 53 via the second high-pressure point G. Yes.
  • the sixth high-pressure pipe 27f passes through the third high-pressure water heat exchanger 53 while flowing carbon dioxide as the primary refrigerant therein so as not to mix with water as the secondary refrigerant for heating.
  • the seventh high-pressure pipe 27g connects the downstream end of the third high-pressure water heat exchanger 53 and the third high-pressure point H.
  • the eighth high-pressure pipe 27h connects the third high-pressure point H and the upstream end in the flow direction of the primary refrigerant toward the expansion valve 5a side in the economizer heat exchanger 7.
  • the ninth high-pressure pipe 27i passes through the economizer heat exchanger 7 while flowing the primary refrigerant therein so as not to mix with the primary refrigerant flowing through the injection passage 70.
  • the tenth high pressure pipe 27j connects the downstream side end portion in the flow direction of the primary refrigerant toward the expansion valve 5a side in the economizer heat exchanger 7 and the fourth high pressure point I.
  • the eleventh high-pressure pipe 27k connects the fourth high-pressure point I and the upstream end in the flow direction of the primary refrigerant toward the expansion valve 5a in the primary refrigerant heat exchanger 8.
  • the twelfth high-pressure pipe 27l passes through the primary inter-refrigerant heat exchanger 8 while flowing the primary refrigerant therein so as not to mix with the primary refrigerant flowing through the low-pressure pipe 20.
  • the thirteenth high pressure pipe 27m connects the downstream end in the flow direction of the primary refrigerant toward the expansion valve 5a side in the heat exchanger 8 between the primary refrigerants and the expansion valve 5a via the fifth high pressure point J. is doing.
  • the low-pressure pipe 20 has a first low-pressure pipe 20a, a second low-pressure pipe 20b, a third low-pressure pipe 20c, a fourth low-pressure pipe 20d, and a fifth low-pressure pipe 20e.
  • the first low-pressure pipe 20a connects the expansion valve 5a and the third low-pressure point M via the first low-pressure point K.
  • the second low-pressure pipe 20 b connects the third low-pressure point M and the upstream end of the evaporator 4.
  • the third low-pressure pipe 20c is connected to the downstream end of the evaporator 4 and the upstream end in the flow direction of the primary refrigerant in the low-pressure pipe 20 of the primary refrigerant heat exchanger 8 via the fourth low-pressure point N. While connecting.
  • the fourth low-pressure pipe 20d passes through the primary inter-refrigerant heat exchanger 8 while flowing the primary refrigerant therein so as not to mix with the primary refrigerant flowing through the twelfth high-pressure pipe 271l.
  • the fifth low-pressure pipe 20 e connects the downstream end in the flow direction of the primary refrigerant in the low-pressure pipe 20 of the primary refrigerant heat exchanger 8 and the suction point A that is the suction side of the low-stage compressor 21. is doing.
  • the fifth low-pressure pipe 20e is provided with a low-pressure sensor 20P that detects the pressure of the passing primary refrigerant and a low-pressure temperature sensor 20T that detects the temperature of the passing primary refrigerant.
  • the injection path 70 includes an injection expansion valve 73, a first injection pipe 72, a second injection pipe 74, a third injection pipe 75, and a fourth injection pipe 76.
  • the first injection pipe 72 connects the third high pressure point H and the injection expansion valve 73.
  • the second injection pipe 74 connects the injection expansion valve 73 and the upstream end in the flow direction of the primary refrigerant flowing through the injection path 70 in the economizer heat exchanger 7 via the injection intermediate pressure point Q. Yes.
  • the third injection pipe 75 passes through the economizer heat exchanger 7 while flowing the primary refrigerant therein so as not to mix with the primary refrigerant flowing through the ninth high-pressure pipe 27i.
  • the fourth injection pipe 76 connects the downstream end in the flow direction of the primary refrigerant flowing through the injection path 70 in the economizer heat exchanger 7 and the injection confluence point D via the post-economizer heat exchange point R. ing.
  • the injection path 70 since the injection path 70 is employed, the coefficient of performance of the heat pump circuit can be improved. And even when the cooling effect of the primary refrigerant in the intermediate pressure water heat exchanger 40 for improving the efficiency of the heat pump circuit 10 cannot be sufficiently obtained, for example, when the heating load is small, the injection path 70 Driving efficiency can be improved by increasing the amount of injection that passes through.
  • the injection confluence point D is provided between the intermediate pressure water heat exchanger 40 and the high stage compressor 25. Therefore, the high-temperature primary refrigerant discharged from the low-stage compressor 21 is not cooled before reaching the intermediate-pressure water heat exchanger 40, and the intermediate-pressure water heat exchanger is maintained while maintaining the high-temperature state. 40.
  • the water for heating which passes the intermediate pressure water heat exchanger 40 can be made high temperature enough.
  • the third high pressure point H is provided at a position where a part of the primary refrigerant can be branched to the injection path 70 on the upstream side of the economizer heat exchanger 7. For this reason, it is possible to avoid a decrease in capacity due to overcooling of the primary refrigerant from the low-stage compressor 21 toward the high-stage compressor 25.
  • the primary bypass 80 has a fourteenth high-pressure pipe 27n, a sixth low-pressure pipe 20f, and a primary bypass expansion valve 5b.
  • the fourteenth high-pressure pipe 27n connects the fourth high-pressure point I and the primary bypass expansion valve 5b.
  • the sixth low-pressure pipe 20f is connected via the primary bypass expansion valve 5b, the third low-pressure point M, and the second low-pressure point L.
  • the control part 11 can adjust the quantity of the primary refrigerant
  • the control unit 11 increases the flow rate of the primary refrigerant passing through the primary inter-refrigerant heat exchanger 8, and the low-stage compressor 21. Therefore, the degree of superheat of the primary refrigerant sucked in can be increased, and thereby the compression ratio required for the discharge refrigerant temperature of the low-stage compressor 21 to be the target temperature can be kept small.
  • the control unit 11 reduces the flow rate of the primary refrigerant passing through the primary inter-refrigerant heat exchanger 8, and the low-stage compressor 21 sucks it. The degree of superheat of the primary refrigerant can be reduced, and this can prevent a situation in which the suction refrigerant density of the low-stage compressor 21 is significantly reduced and the circulation amount cannot be secured.
  • the control unit 11 includes the above-described intermediate pressure temperature sensor 23T, high stage suction pressure sensor 24P, high stage suction temperature sensor 24T, high pressure sensor 27P, high pressure sensor 27T, low pressure sensor 20P, and low pressure sensor 20T. Based on the detected value, the low-stage compressor 21, the high-stage compressor 25, the injection expansion valve 73, the expansion valve 5a, the primary bypass expansion valve 5b, the fan 4f, and the like are controlled. (Heating circuit 60) In the heating circuit 60, water as a secondary refrigerant circulates.
  • the heating circuit 60 includes a radiator 61, a diversion mechanism 62, a heating forward pipe 65, a heating return pipe 66, an intermediate pressure side branch path 67, and a high pressure side branch path 68.
  • the diversion mechanism 62 includes a heating mixing valve 64 and a heating pump 63.
  • the radiator 61 is installed in a space to be heated, and warm water as a secondary refrigerant flows inside to heat the air in the target space.
  • the radiator 61 is provided with a radiator temperature sensor 61T for detecting the temperature of the water for heating flowing inside.
  • the radiator 61 has an outlet for receiving warm water sent from the heating pump 63, and the intermediate-pressure water heat exchanger 40 and the second high-pressure water heat exchanger 40 that radiate heat after being radiated by the radiator 61.
  • the heating return pipe 66 connects the return port of the radiator 61 and the heating branch point X.
  • the intermediate pressure side branch path 67 that sends the water that has radiated heat from the radiator 61 to the intermediate pressure water heat exchanger 40 side, and the high pressure side branch path 68 that sends the water to the second high pressure water heat exchanger 52 side , Shunt.
  • the heating return pipe 66 is provided with a heating return temperature sensor 66T that detects the temperature of the passing secondary refrigerant for heating.
  • the intermediate pressure side branch path 67 has a first intermediate pressure side branch path 67a, a second intermediate pressure side branch path 67b, and a third intermediate pressure side branch path 67c.
  • the first intermediate pressure side branch path 67 a connects the branch point X and the upstream end portion in the water flow direction in the intermediate pressure side branch path 67 of the intermediate pressure water heat exchanger 40.
  • the second intermediate pressure side branching passage 67b flows while heating water as a secondary refrigerant flows inside so as not to mix with carbon dioxide as a primary refrigerant flowing in the second intermediate pressure pipe 23b. It passes through the pressure water heat exchanger 40.
  • the intermediate pressure water heat exchanger 40 carbon dioxide as the primary refrigerant flowing in the second intermediate pressure pipe 23b and heating for the secondary refrigerant flowing in the second intermediate pressure side branch passage 67b.
  • a counter flow type that flows in directions opposite to each other is adopted.
  • the third intermediate pressure side branch passage 67c connects the downstream end of the intermediate pressure side branch passage 67 of the intermediate pressure water heat exchanger 40 in the water flow direction and the heating junction point Y.
  • the third intermediate pressure side branch path 67c is provided with an intermediate pressure side branch path temperature sensor 67T for detecting the temperature of the heating water passing therethrough.
  • the high pressure side branch 68 has a first high pressure side branch 68a, a second high pressure side branch 68b, and a third high pressure side branch 68c.
  • the first high-pressure side branch 68a connects the branch point X and the upstream end in the water flow direction in the high-pressure side branch 68 of the second high-pressure water heat exchanger 52.
  • the second high-pressure side branch 68b allows the heating water as the secondary refrigerant to flow in the inside so as not to mix with carbon dioxide as the primary refrigerant flowing in the fourth high-pressure pipe 27d. 2 It passes through the high-pressure water heat exchanger 52.
  • the second high-pressure water heat exchanger 52 for heating as carbon dioxide as the primary refrigerant flowing in the fourth high-pressure pipe 27d and secondary refrigerant flowing in the second high-pressure side branch 68b.
  • the counter flow type which is flowing in the direction opposite to each other is adopted.
  • the third high-pressure side branch 68 c connects the downstream end of the second high-pressure water heat exchanger 52 in the high-pressure side branch 68 in the flow direction of water and the heating junction point Y.
  • the third high pressure side branch 68c is provided with a high pressure side branch temperature sensor 68T for detecting the temperature of the heating water passing therethrough.
  • the temperature of the water for heating flowing through the first intermediate pressure side branch passage 67a and the temperature of the water for heating flowing through the first high pressure side branch passage 68a are both branched at the heating branch point X. Since there is no heat exchange with the outside, the temperature distribution is the same. On the other hand, the temperature of the heating water flowing through the third intermediate pressure side branch passage 67c is equal to the amount of heat obtained by heat exchange with the primary refrigerant flowing through the second intermediate pressure pipe 23b in the intermediate pressure water heat exchanger 40. It becomes the corresponding temperature.
  • the temperature of the heating water flowing through the third high-pressure side branch 68 c is equal to the amount of heat obtained by heat exchange with the primary refrigerant flowing through the fourth high-pressure pipe 27 d in the second high-pressure water heat exchanger 52. It becomes the corresponding temperature. For this reason, the temperature of the water for heating which is flowing through the third intermediate pressure side branch passage 67c may be different from the temperature of the water for heating which is flowing through the third high pressure side branch passage 68c.
  • the heating outgoing pipe 65 connects the heating junction point Y and the outgoing outlet of the radiator 61.
  • a heating pump 63 that adjusts the flow rate of heating water passing through the heating forward pipe 65 is provided in the middle of the heating forward pipe 65.
  • the heating mixing valve 64 is provided at the heating sidestream point Y where the water for heating that has passed through the third intermediate pressure side branch passage 67c and the water for heating that has passed through the third high pressure side branch passage 68c merge. .
  • the heating mixing valve 64 adjusts the opening degree of the portion connected to the third intermediate pressure side branching passage 67c side and the opening degree of the portion connected to the third high pressure side branching passage 68c side, respectively.
  • the ratio of the flow rate of the heating water flowing through the branch path 67 and the flow rate of the heating water flowing through the third high-pressure side branch path 68c is adjusted.
  • the control part 11 is the secondary refrigerant
  • the flow rate of the heating pump 63 and the diversion ratio in the heating mixing valve 64 are controlled.
  • Hot water supply circuit 90 The hot water supply circuit 90 circulates water for hot water supply.
  • the hot water supply circuit 90 includes a hot water storage tank 91, a water supply pipe 94, a hot water supply pipe 98, a hot water supply bypass pipe 99, a hot water supply mixing valve 93, a hot water supply heat pump pipe 95, and a hot water supply pump 92.
  • the hot water storage tank 91 is provided with a circulation outlet and a circulation return port. After passing outside city water (not shown), normal temperature water is supplied from the vicinity of the lower end of the hot water storage tank 91 into the hot water storage tank 91 via the water supply pipe 94.
  • the hot water supply heat pump pipe 95 includes a first hot water supply heat pump pipe 95a, a second hot water supply heat pump pipe 95b, a third hot water supply heat pump pipe 95c, a fourth hot water supply heat pump pipe 95d, a fifth hot water supply heat pump pipe 95e, and a sixth hot water supply heat pump pipe 95f. Have.
  • the first hot water supply heat pump pipe 95 a connects the circulation outlet of the hot water storage tank 91 and the hot water supply pump 92.
  • the first hot water supply heat pump pipe 95a is provided with a hot water supply water temperature sensor 94T that detects the temperature of the hot water passing therethrough.
  • the second hot water supply heat pump pipe 95b connects the hot water supply pump 92 and the upstream end of the third high pressure water heat exchanger 53 in the hot water supply heat pump pipe 95 in the water flow direction.
  • the third hot water supply heat pump pipe 95c allows the third high pressure water heat exchanger to flow while supplying hot water therein so as not to be mixed with carbon dioxide as the primary refrigerant flowing in the sixth high pressure pipe 27f. 53.
  • the fifth hot water supply heat pump pipe 95e flows the first hot water supply heat exchanger while flowing hot water in it so that it does not mix with carbon dioxide as the primary refrigerant flowing in the second high pressure pipe 27b. Passing through 51.
  • carbon dioxide as the primary refrigerant flowing in the second high-pressure pipe 27b and hot-water supply water flowing in the fifth hot-water supply heat pump pipe 95e are mutually connected.
  • the counterflow type which is flowing in the opposite direction is adopted.
  • the sixth hot water supply heat pump pipe 95f connects the downstream end of the hot water supply heat pump pipe 95 of the first high-pressure water heat exchanger 51 in the flow direction of water with the circulation return port of the hot water storage tank 91.
  • the sixth hot water supply heat pump pipe 95f is provided with a hot water supply hot water temperature sensor 98T that detects the temperature of the hot water passing therethrough.
  • the hot water supply pipe 98 guides hot water stored in the hot water storage tank 91 from the vicinity of the upper end of the hot water storage tank 91 to a place to be used (not shown).
  • the water supply pipe 94 is provided with a water supply branch point W, which is a branch portion that branches off from the flow toward the hot water storage tank 91.
  • the hot water supply pipe 98 is provided with a hot water supply junction point Z that joins the flow from the hot water storage tank 91 toward the place used.
  • the hot water supply bypass pipe 99 connects the water supply branch point W and the hot water supply junction point Z.
  • a hot water supply mixing valve 93 that can adjust the mixing ratio between hot water sent from the hot water storage tank 91 through the hot water supply pipe 98 and normal temperature water supplied from city water through the hot water supply bypass pipe 99 is provided. It has been. By adjusting the mixing ratio in the hot water supply mixing valve 93, the temperature of the water sent to the place where it is used is adjusted.
  • the control unit 11 controls the flow rate of the hot water supply pump 92 based on the temperature detected by the hot water supply / incoming water temperature sensor 94T, the hot water supply intermediate temperature sensor 95T, the hot water supply hot water temperature sensor 98T, and the like.
  • FIG. 2 is a pressure-enthalpy diagram when the heat pump system 1 is operated.
  • FIG. 3 is a temperature-entropy diagram when the heat pump system 1 is operated.
  • the low-stage compressor 21 compresses the primary refrigerant (point A) of about 22 ° C. flowing through the low-pressure pipe 20 so that the target discharge temperature reaches about 90 ° C. (point B).
  • the pressure of the primary refrigerant flowing through the low-pressure pipe 20 is lowered to the pressure (evaporation) until the pressure at which the carbon dioxide as the primary refrigerant can be evaporated by the ambient temperature where the evaporator 4 is installed.
  • the pressure is adjusted by the control unit 11.
  • the primary refrigerant discharged from the low-stage compressor 21 flows into the second intermediate pressure pipe 23b in the intermediate pressure water heat exchanger 40 through the first intermediate pressure pipe 23a.
  • the primary refrigerant flowing into the intermediate pressure water heat exchanger 40 is cooled to about 35 ° C. by exchanging heat with water as the secondary refrigerant for heating passing through the second intermediate pressure side branch passage 67b. (Point C).
  • the radiator 61 It is cooled effectively by a secondary refrigerant of about 30 ° C. in a state of being cooled by releasing heat.
  • the primary refrigerant that has passed through the intermediate pressure water heat exchanger 40 is further cooled by joining with the primary refrigerant of about 27 ° C. that flows in through the injection passage 70 at the injection junction D of the third intermediate pressure pipe 23c, It becomes about 30 ° C. (point D).
  • the control unit 11 performs control so that the primary refrigerant after joining at the injection joining point D has a superheat degree or is in a supercritical state. Further, the control unit 11 drives the high-stage compressor 25 while driving the high-stage compressor 25 at the same compression ratio as that of the low-stage compressor 21 after the primary refrigerant merged at the injection junction D.
  • the primary refrigerant joined at the injection junction D is sucked into the high-stage compressor 25 so that the target discharge temperature reaches about 90 ° C., which is the same temperature as the target temperature of the discharge refrigerant of the low-stage compressor 21. Further, the primary refrigerant is compressed.
  • the high-stage compressor 25 is controlled by the control unit 11 so as to compress until the discharge refrigerant pressure of the primary refrigerant reaches a pressure exceeding the critical pressure of the primary refrigerant (point E).
  • the primary refrigerant discharged by the high-stage compressor 25 flows into the second high-pressure pipe 27b in the first high-pressure water heat exchanger 51 through the first high-pressure pipe 27a.
  • the primary refrigerant that has flowed into the first high-pressure water heat exchanger 51 is cooled to about 85 ° C. by exchanging heat with the hot-water supply water passing through the fifth hot-water supply heat pump pipe 95e. F). Since the primary refrigerant radiates heat while maintaining a state where the critical pressure is exceeded, the temperature continuously changes.
  • the primary refrigerant and the secondary refrigerant in the first high-pressure water heat exchanger 51 are flowing in a counterflow manner, they are still near the outlet of the second high-pressure pipe 27b in the first high-pressure water heat exchanger 51. It is cooled effectively by water for hot water supply of about 30 ° C. that is not sufficiently heated.
  • the primary refrigerant that has passed through the first high-pressure water heat exchanger 51 flows into the fourth high-pressure pipe 27d in the second high-pressure water heat exchanger 52 through the third high-pressure pipe 27c.
  • the primary refrigerant that has flowed into the second high-pressure water heat exchanger 52 exchanges heat with water as a secondary refrigerant for heating that passes through the second high-pressure side branch 68b, so that the temperature becomes approximately 35 ° C. It is cooled (point G).
  • the radiator 61 is effectively cooled by the secondary refrigerant of about 30 ° C. in a state of being cooled by releasing heat.
  • the primary refrigerant that has passed through the second high-pressure water heat exchanger 52 flows into the sixth high-pressure pipe 27f in the third high-pressure water heat exchanger 53 through the fifth high-pressure pipe 27e.
  • the primary refrigerant that has flowed into the third high-pressure water heat exchanger 53 is further cooled to about 30 ° C.
  • the high-pressure water heat exchanger 50 is divided into three heat exchangers, and since the primary refrigerant flowing through the high-pressure water heat exchanger 50 is in a bicritical state, a temperature change occurs in the heat dissipation process, and The temperature change range (30 ° C. to 65 ° C.) of water as a secondary refrigerant circulating in the heating circuit 60 is included in the temperature change range (20 ° C. to 90 ° C.) of hot water for the hot water supply circuit 90.
  • the primary refrigerant that has reached the third high pressure point H is divided into a flow toward the expansion valve 5a and a flow toward the injection path 70 through the eighth high pressure pipe 27h.
  • the degree of the diversion here is controlled by the control unit 11 adjusting the valve opening degree of the injection expansion valve 73.
  • the primary refrigerant that is diverted to the injection passage 70 side is reduced in pressure at the injection expansion valve 73 after passing through the first injection pipe 72, and the temperature of the primary refrigerant is lowered to about 23 ° C. (point Q).
  • the primary refrigerant decompressed in the injection expansion valve 73 flows into the third injection pipe 75 in the economizer heat exchanger 7 through the second injection pipe 74.
  • the primary refrigerant that has flowed into the economizer heat exchanger 7 exchanges heat with the primary refrigerant of about 30 ° C. flowing through the ninth high-pressure pipe 27i, and is heated to about 27 ° C. (point R).
  • the primary refrigerant that has flowed into the ninth high-pressure pipe 27i in the economizer heat exchanger 7 exchanges heat with the primary refrigerant that flows through the third injection pipe 75 at about 27 ° C. Then, it is further cooled to about 25 ° C. (point I).
  • the primary refrigerant that has passed through the ninth high-pressure pipe 27i in the economizer heat exchanger 7 reaches the fourth high-pressure point I through the tenth high-pressure pipe 27j.
  • the primary refrigerant that has reached the fourth high pressure point I is divided into a flow toward the primary bypass 80 side and a flow toward the eleventh high pressure pipe 27k side.
  • the degree of the diversion here is adjusted by the control unit 11 controlling the valve opening degree of the primary bypass expansion valve 5b.
  • the primary refrigerant that has flowed through the eleventh high-pressure pipe 27k flows into the twelfth high-pressure pipe 27l in the primary refrigerant heat exchanger 8.
  • the primary refrigerant having a temperature of about 25 ° C. flowing into the twelfth high-pressure pipe 271 in the heat exchanger 8 between the primary refrigerants exchanges heat with the primary refrigerant having a temperature of about ⁇ 3 ° C.
  • the degree of decompression of the passing primary refrigerant is adjusted by adjusting the valve opening degree by the control unit 11, the refrigerant pressure of the passing primary refrigerant is lowered, and the refrigerant temperature is also lowered to about ⁇ 3 ° C.
  • Point K the primary refrigerant is depressurized to a pressure equal to or lower than the critical pressure by adjusting the degree of depressurization by the control unit 11, and enters a gas-liquid two-phase state.
  • the primary refrigerant can be cooled not only by the economizer heat exchanger 7 but also by the primary refrigerant heat exchanger 8.
  • the primary refrigerant on the suction side of the low-stage compressor 21 through which the primary refrigerant at the lowest temperature flows in the heat pump circuit 10 can be used.
  • the density of the primary refrigerant passing through the expansion valve 5a can be increased, and the circulation amount of the primary refrigerant in the heat pump circuit 10 can be increased.
  • the primary refrigerant that has passed through the expansion valve 5a flows to the third low-pressure point M through the first low-pressure pipe 20a, and joins the primary refrigerant that flows through the sixth low-pressure pipe 20f (point M).
  • the primary refrigerant of about 25 ° C. that does not flow to the eleventh high-pressure pipe 27k side flows to the primary bypass 80 side, and the primary bypass expansion through the fourteenth high-pressure pipe 27n. It flows to the valve 5b.
  • the primary bypass expansion valve 5b is adjusted by the controller 11 so that the degree of pressure reduction of the passing primary refrigerant is adjusted, the refrigerant pressure of the passing primary refrigerant is lowered, and the refrigerant temperature is about -3 ° C. Lower (point L).
  • the primary refrigerant is depressurized to a pressure equal to or lower than the critical pressure by adjusting the depressurization degree by the control unit 11 to be in a gas-liquid two-phase state.
  • the primary refrigerant that has passed through the primary bypass expansion valve 5b flows to the third low-pressure point M through the sixth low-pressure pipe 20f, and joins the primary refrigerant that has flowed through the first low-pressure pipe 20a described above (point M).
  • the primary refrigerant of about ⁇ 3 ° C. joined at the third low pressure point M flows into the evaporator 4 through the second low pressure pipe 20b.
  • the primary refrigerant that has flowed into the evaporator 4 exchanges heat with the air that is actively supplied to the evaporator 4 by the fan 4f. By the heat exchange in the evaporator 4, the primary refrigerant in a gas-liquid two-phase state of about ⁇ 3 ° C.
  • the primary refrigerant that has passed through the evaporator 4 flows into the fourth low-pressure pipe 20d in the primary inter-refrigerant heat exchanger 8 through the third low-pressure pipe 20c.
  • the primary refrigerant flowing at about ⁇ 3 ° C. flowing through the fourth low-pressure pipe 20d in the heat exchanger 8 between the primary refrigerants exchanges heat with the primary refrigerant flowing at about 25 ° C. flowing through the twelfth high-pressure pipe 27l.
  • it will be heated to about 22 degreeC and will be in the state with the degree of superheat (point A).
  • the primary refrigerant circulates as described above.
  • the control unit 11 controls the radiator 61 so that water as a secondary refrigerant at about 65 ° C. is supplied. Is going.
  • the temperature distribution state of the secondary refrigerant for heating will be described with one specific example.
  • the water as the secondary refrigerant for heating that has dissipated heat while passing through the radiator 61 drops to a temperature of about 35 ° C., depending on the performance of the radiator 61 and the degree of the heating load, and passes through the heating return pipe 66. It flows to the heating branch point X.
  • the heating branch point X is divided into a flow toward the intermediate pressure side branch 67 and a flow toward the high pressure side branch 68.
  • the secondary refrigerant that flows from the heating branch point X toward the intermediate pressure side branch path 67 side flows into the second intermediate pressure side branch path 67b in the intermediate pressure water heat exchanger 40 through the first intermediate pressure side branch path 67a. Go.
  • the secondary refrigerant flowing through the second intermediate pressure side branch passage 67b in the intermediate pressure water heat exchanger 40 is heated by the primary refrigerant passing through the second intermediate pressure pipe 23b, so The temperature of the secondary refrigerant is raised to about 65 ° C.
  • the primary refrigerant and the secondary refrigerant in the intermediate pressure water heat exchanger 40 flow in a counterflow manner, and thus the second intermediate pressure side branch path 67b in the intermediate pressure water heat exchanger 40.
  • the vicinity of the outlet is efficiently heated by a primary refrigerant of about 90 ° C., which is a relatively high temperature.
  • the secondary refrigerant that has passed through the second intermediate pressure side branch passage 67b in the intermediate pressure water heat exchanger 40 and has been warmed to about 65 ° C. passes through the third intermediate pressure side branch passage 67c and passes through the heating junction point Y. It will flow to.
  • the primary refrigerant and the secondary refrigerant in the second high-pressure water heat exchanger 52 flow in a counterflow manner, and therefore the second high-pressure side branch in the second high-pressure water heat exchanger 52.
  • the vicinity of the outlet of the path 68b is efficiently heated by a primary refrigerant of about 85 ° C., which is a relatively high temperature.
  • the secondary refrigerant that has passed through the second high-pressure side branch path 68b in the second high-pressure water heat exchanger 52 and has been warmed to about 65 ° C. passes through the third high-pressure side branch path 68c and passes through the heating junction point. It flows to Y.
  • the control unit 11 adjusts the valve opening degree on the intermediate pressure side branch path 67 side and the valve opening degree on the high pressure side branch path 68 side in the heating mixing valve 64 so that the two flowing through the intermediate pressure side branch path 67 side.
  • the flow rate of the secondary refrigerant and the flow rate of the secondary refrigerant flowing through the high-pressure side branch path 68 can be adjusted.
  • the control unit 11 determines that the secondary refrigerant circulating in the heating circuit 60 is heated on the intermediate pressure water heat exchanger 40 side and heated on the second high pressure water heat exchanger 52 side.
  • the temperature of the secondary refrigerant merged at the heating merge point Y is controlled to be the temperature required in the radiator 61. Can do.
  • the secondary refrigerant heated to about 65 ° C. joined at the heating junction point Y is supplied to the radiator 61 through the heating forward pipe 65.
  • the secondary refrigerant circulates as described above. ⁇ 1-4> Operation of Hot Water Supply Circuit 90
  • the control unit 11 controls the flow rate of the hot water supply pump 92 so that hot water of about 90 ° C. can be stored in the hot water storage tank 91.
  • the relatively low temperature water below the hot water storage tank 91 into which the city water has flowed flows toward the hot water supply heat pump pipe 95 at a temperature of about 20 ° C.
  • the hot water supply water at about 20 ° C. that has passed through the first hot water supply heat pump pipe 95 a and the second hot water supply heat pump pipe 95 b flows into the third hot water supply heat pump pipe 95 c in the third high-pressure water heat exchanger 53.
  • the hot-water supply water flowing through the third hot-water supply heat pump pipe 95c in the third high-pressure water heat exchanger 53 passes through the sixth high-pressure pipe 27f in the third high-pressure water heat exchanger 53.
  • the temperature of the hot water supply at about 20 ° C. is raised to about 30 ° C.
  • the primary refrigerant and the secondary refrigerant in the third high-pressure water heat exchanger 53 are flowing in a counterflow manner, and thus the third hot water supply heat pump pipe in the third high-pressure water heat exchanger 53 is used.
  • the vicinity of the outlet of 95c is efficiently heated by a primary refrigerant at a relatively high temperature of about 35 ° C.
  • the hot-water supply water heated to about 30 ° C. in the third high-pressure water heat exchanger 53 passes through the fourth hot-water supply heat pump pipe 95d and enters the fifth hot-water supply heat pump pipe 95e in the first high-pressure water heat exchanger 51. Inflow.
  • the hot-water supply water flowing through the fifth hot-water supply heat pump pipe 95e in the first high-pressure water heat exchanger 51 passes through the second high-pressure pipe 27b in the first high-pressure water heat exchanger 51 at about 90 ° C.
  • the temperature of the hot water supply at about 30 ° C. is raised to about 90 ° C.
  • the primary refrigerant and the secondary refrigerant in the first high-pressure water heat exchanger 51 flow in a counterflow manner, and thus the fifth hot water supply heat pump pipe in the first high-pressure water heat exchanger 51.
  • the vicinity of the outlet of 95e is efficiently heated by a primary refrigerant of about 90 ° C., which is a relatively high temperature.
  • the hot water supply water heated to about 90 ° C. in the first high-pressure water heat exchanger 51 passes through the sixth hot water supply heat pump pipe 95 f and flows into the hot water storage tank 91.
  • the control unit 11 can cope with not only the heating load of the heating circuit 60 but also the hot water supply load of the hot water supply circuit 90. The operation is carried out so that the cycle efficiency can be kept as good as possible while supplying a sufficient amount of heat to each circuit.
  • the control part 11 is the temperature of the secondary refrigerant
  • the temperature of the primary refrigerant flowing into the second high-pressure water heat exchanger 52 is set to be higher than the temperature of the secondary refrigerant for heating flowing into the second high-pressure water heat exchanger 52.
  • the temperature of the primary refrigerant flowing into the intermediate pressure water heat exchanger 40 and the temperature of the primary refrigerant flowing into the second high pressure water heat exchanger 52 are both higher than the temperature required in the radiator 61. Control of the low stage side compressor 21, the high stage side compressor 25, the expansion valve 5a, etc. is performed.
  • control unit 11 makes the first high-pressure water heat from the target discharge temperature of the high-stage compressor 25 while making the target discharge temperature of the low-stage compressor 21 higher than the temperature required in the radiator 61. Control is performed so that the temperature after subtracting the heat released when passing through the exchanger 51 is higher than the temperature required in the radiator 61. In addition, the control unit 11 determines the evaporation temperature based on the installation environment of the evaporator 4 and equalizes the compression ratio of the low-stage compressor 21 and the compression ratio of the high-stage compressor 25 with the smallest possible compression ratio. Control is performed so as to be.
  • control unit 11 specifically includes the low-stage compressor 21, the high-stage compressor 25, the expansion valve 5a, the injection expansion valve 73, and the primary bypass expansion of the heat pump circuit 10. Control of the valve 5b and the fan 4f is performed.
  • the control unit 11 applies to the inner wall surface of the pipe through which the secondary refrigerant for heating that performs heat exchange flows or the inner wall surface of the water for hot water supply that performs heat exchange. Since scales (scales, etc.) may occur, the temperature of the primary refrigerant is controlled to be equal to or lower than a predetermined high temperature limit value.
  • the control unit 11 controls the temperature of the secondary refrigerant flowing through the third intermediate pressure side branch path 67c of the heating circuit 60 and the first temperature.
  • the secondary refrigerant temperature unified control is performed so that the temperature of the secondary refrigerant flowing through the three high-pressure side branch paths 68c becomes the same temperature.
  • the control unit 11 not only performs control so that the temperature of the secondary refrigerant flowing through the third intermediate pressure side branch 67c and the temperature of the secondary refrigerant flowing through the third high pressure side branch 68c are unified.
  • the control is performed so that the unified temperature coincides with the temperature required in the radiator 61.
  • control unit 11 controls the mixing ratio of the heating mixing valve 64 to control the flow rate of the secondary refrigerant for heating that flows through the intermediate pressure side branch passage 67 and the secondary for heating that flows through the high pressure side branch passage 68.
  • the control unit 11 In order to make the temperature of the secondary refrigerant for heating flowing through the third intermediate pressure side branch passage 67c the same as the temperature of the secondary refrigerant for heating flowing through the third high pressure side branch passage 68c, the control unit 11 Of the temperature detected by the intermediate pressure side branch temperature sensor 67T and the temperature detected by the high pressure side branch temperature sensor 68T, the flow rate of the secondary refrigerant on the low temperature side decreases and the flow rate of the secondary refrigerant on the high temperature side increases. Thus, the heating mixing valve 64 is controlled.
  • the flow rate is lowered by reducing the flow rate, and the time during which the secondary refrigerant receives heat from the primary refrigerant in the heat exchange with the primary refrigerant can be lengthened. Will go up.
  • the flow rate is increased by increasing the flow rate, and the time during which the secondary refrigerant receives heat from the primary refrigerant in the heat exchange with the primary refrigerant can be shortened, and the temperature is increased. Will go down.
  • the difference between the temperature of the secondary refrigerant for heating flowing through the third intermediate pressure side branch passage 67c and the temperature of the secondary refrigerant for heating flowing through the third high pressure side branch passage 68c becomes small. It will follow.
  • the temperature required in the radiator 61 refers to a temperature value having a certain range as described below.
  • the control part 11 controls the heating mixing valve 64 and the heating pump 63 so that the heat dissipation in the radiator 61 which a user requests
  • the temperature of the secondary refrigerant for heating is increased while the flow rate of the secondary refrigerant for heating passing through the heating pump 63 is decreased. That is, in the case where the same amount of heat is ensured, the temperature required as the temperature of the secondary refrigerant for heating when the flow rate of the heating pump 63 is increased to a certain value, the flow rate of the heating pump 63 is less than this certain value. When the temperature is reduced, the temperature becomes lower than the temperature required as the temperature of the secondary refrigerant for heating. On the contrary, when the same amount of heat is ensured, the temperature required as the temperature of the secondary refrigerant for heating when the flow rate of the heating pump 63 is reduced to another value is the same as the flow rate of the heating pump 63.
  • the temperature of the secondary refrigerant supplied to the radiator 61 is detected by the ambient temperature of the radiator 61 (the radiator temperature sensor 61T) because the purpose is to warm the air in the surrounding space where the radiator 61 is installed. Temperature).
  • the temperature required in the radiator 61 is higher than the temperature detected by the radiator temperature sensor 61T in this way, and has a temperature range corresponding to the flow rate range in which the heat radiation amount required in the radiator 61 can be secured. Yes. Further, the temperature range may be limited by reflecting the heat radiation performance of the radiator 61 itself.
  • the temperature of the secondary refrigerant for heating that flows toward the radiator 61 through the heating forward pipe 65 is equal to the secondary refrigerant for heating that has flowed through the intermediate pressure side branch path 67 and the heating secondary refrigerant that has flowed through the high pressure side branch path 68. It is the temperature after the secondary refrigerant merges at the heating merge point Y.
  • the heating junction point Y The temperature of the secondary refrigerant after merging is also the same as the temperature before merging, and is the temperature of the secondary refrigerant for heating supplied toward the radiator 61. (Energy increase processing)
  • the control unit 11 reduces the flow rate of the heating pump 63. Control heat increase.
  • both the flow rate of the secondary refrigerant flowing through the intermediate pressure side branch path 67 and the flow rate of the secondary refrigerant flowing through the high pressure side branch path 68 are selected.
  • both the time for which the secondary refrigerant flowing through the intermediate pressure side branch passage 67 receives heat from the primary refrigerant and the time for the secondary refrigerant flowing through the high pressure side branch passage 68 to receive heat from the primary refrigerant are selected.
  • the temperature of the secondary refrigerant for heating flowing through the third intermediate pressure side branch passage 67c and the temperature of the secondary refrigerant for heating flowing through the third high pressure side branch passage 68c are set at the temperatures required by the radiator 61.
  • the heat load on the radiator 61 can be dealt with.
  • Heat reduction processing When the temperature unified by the secondary refrigerant temperature unified control exceeds the temperature required in the radiator 61 while performing the secondary refrigerant temperature unified control, the controller 11 controls the flow rate of the heating pump 63. Control to reduce the amount of heat.
  • both the flow rate of the secondary refrigerant flowing through the intermediate pressure side branch path 67 and the flow rate of the secondary refrigerant flowing through the high pressure side branch path 68 are selected.
  • both the time for which the secondary refrigerant flowing through the intermediate pressure side branch passage 67 receives heat from the primary refrigerant and the time for the secondary refrigerant flowing through the high pressure side branch passage 68 to receive heat from the primary refrigerant are selected.
  • the temperature of the secondary refrigerant for heating flowing through the third intermediate pressure side branch passage 67c and the temperature of the secondary refrigerant for heating flowing through the third high pressure side branch passage 68c are set at the temperatures required by the radiator 61.
  • the control unit 11 flows through the temperature of the secondary refrigerant flowing through the third intermediate pressure side branch passage 67c and the third high pressure side branch passage 68c. Control is performed so that the temperature of the secondary refrigerant is unified.
  • the secondary refrigerant flowing through the third intermediate pressure side branch path 67 c and the secondary refrigerant flowing through the third high pressure side branch path 68 c are both lower than the ambient temperature until reaching the radiator 61. Heat is dissipated, resulting in heat dissipation loss.
  • the controller 11 unifies the temperature of the secondary refrigerant flowing through the third intermediate pressure side branch 67c and the temperature of the secondary refrigerant flowing through the third high pressure side branch 68c at the temperature required in the radiator 61. Control is performed so that For this reason, it is not necessary to perform temperature adjustment by heating or cooling so that the temperature of the secondary refrigerant for heating after merging at the heating merging point Y becomes the temperature required by the radiator 61. Thereby, such a temperature control heater or a cooler can be made unnecessary.
  • the primary refrigerant sucked by the high stage compressor 25 is cooled by the secondary refrigerant for heating when passing through the intermediate pressure water heat exchanger 40.
  • the primary refrigerant flowing through the injection passage 70 is further cooled. For this reason, the density of the primary refrigerant sucked by the high-stage compressor 25 can be increased, and the efficiency of the heat pump circuit 10 can be improved.
  • the heat obtained by the secondary refrigerant for heating by cooling the primary refrigerant sucked into the high-stage compressor 25 can be used for the heating load in the radiator 61. Further, even when the heat necessary for raising the hot water supply water to the required water temperature is obtained from the primary refrigerant flowing through the high-pressure water heat exchanger 50, the primary refrigerant flowing through the high-pressure water heat exchanger 50 still remains. The temperature is in a temperature range in which the secondary refrigerant for heating can be heated. For this reason, within the range in which the operation efficiency of the heat pump circuit 10 can be improved, the heat of the primary refrigerant flowing through the second high-pressure water heat exchanger 52 that is a part of the high-pressure water heat exchanger 50 is heated.
  • the heat of the primary refrigerant flowing through the high-pressure water heat exchanger 50 can be effectively utilized while improving the operation efficiency of the heat pump circuit 10. For example, when the secondary refrigerant for heating or the water for hot water supply is heated by the intermediate pressure water heat exchanger 40 and then further heated by the high pressure water heat exchanger 50, the high pressure water heat exchanger 50 is used. Since the secondary refrigerant for heating or the water for hot water supply that is about to flow into the water has already been warmed, the heat of the primary refrigerant flowing through the high-pressure water heat exchanger 50 cannot be used effectively.
  • the enthalpy change in the heat release process of the primary refrigerant cannot be sufficiently taken on the Mollier diagram.
  • the intermediate pressure water heat exchanger 40 is used.
  • the secondary refrigerant for heating or the water for hot water to be introduced has already been warmed. For this reason, the heat of the primary refrigerant flowing through the intermediate pressure water heat exchanger 40 cannot be fully utilized, and it may be difficult to improve the operating efficiency of the multistage compression heat pump circuit 10.
  • the heat pump system 201 according to the second embodiment includes a primary bypass 80 (fourteenth high-pressure pipe 27 n, primary bypass expansion valve 5 b, first bypass in the heat pump system 1 according to the first embodiment).
  • 6 is a system in which all of the circulating primary refrigerant passes through the primary inter-refrigerant heat exchanger 8 without providing the low pressure pipe 20f). Since other configurations are the same as those in the first embodiment, description thereof is omitted.
  • the heat pump system 301 of the third embodiment is the same as the heat pump system 1 of the first embodiment except that the economizer heat exchanger 7 and the injection path 70 (the injection expansion valve 73, the first injection pipe 72, the second injection pipe 74, the first 3 injection pipe 75, fourth injection pipe 76), eighth high pressure pipe 27h, ninth high pressure pipe 27i, tenth high pressure pipe 27j, third intermediate pressure pipe 23c, and fourth intermediate pressure pipe 23d are provided instead.
  • a 33rd intermediate pressure tube 323c and a 38th high pressure tube 327h are provided.
  • the 33rd intermediate pressure pipe 323 c connects the second intermediate pressure pipe 23 b in the intermediate pressure water heat exchanger 40 and the suction side of the high stage compressor 25.
  • the thirty-eighth high-pressure pipe 327h connects the sixth high-pressure pipe 27f in the third high-pressure water heat exchanger 53 and the fourth high-pressure point I. Since other configurations are the same as those in the first embodiment, description thereof is omitted.
  • this heat pump system 301 it is possible to avoid a state where the refrigerant sucked by the high-stage compressor 25 is so cooled that the refrigerant becomes wet, and the circuit configuration can be simplified by reducing the number of components. . Moreover, in this heat pump system 301, since the injection path 70 is not provided, even if the temperature of the primary refrigerant passing through the intermediate pressure water heat exchanger 40 is excessively lowered by the secondary refrigerant temperature unified control, the higher stage side It becomes possible to increase the amount of the primary refrigerant toward the high-pressure water heat exchanger 50 within a range in which the primary refrigerant sucked by the compressor 25 does not become wet.
  • a heat pump system 401 according to a fourth embodiment is a system in which a branch to the injection path 70 side is arranged on the downstream side of the economizer heat exchanger 7 as shown in FIG. That is, in the heat pump system 401 of the fourth embodiment, in the heat pump system 1 of the first embodiment, the 43rd high pressure point 4H is replaced with the third high pressure point H, and the 47th high pressure tube 427g is replaced with the seventh high pressure pipe 27g. 48th high-pressure pipe 427h instead of the eighth high-pressure pipe 27h, 49th high-pressure pipe 427i instead of the ninth high-pressure pipe 27i, and 410th high-pressure pipe 427j instead of the tenth high-pressure pipe 27j, respectively.
  • the 43rd high pressure point 4H is provided downstream of the economizer heat exchanger 7 and upstream of the fourth high pressure point I in the flow direction of the primary refrigerant in the heat pump circuit 10, and the injection path 70 branches off. Yes.
  • the 47th high pressure pipe 427g connects the sixth high pressure pipe 27f in the third high pressure water heat exchanger 53 and the 48th high pressure pipe 427h in the economizer heat exchanger 7.
  • the 49th high pressure pipe 427i connects the 48th high pressure pipe 427h in the economizer heat exchanger 7 and the 43rd high pressure point 4H.
  • the 410th high pressure pipe 427j connects the 43rd high pressure point 4H and the fourth high pressure point I. Since other configurations are the same as those in the first embodiment, description thereof is omitted.
  • the heat pump system 501 of the fifth embodiment is a system in which the third high-pressure water heat exchanger 53 is removed from the heat pump system 1 of the first embodiment. That is, the heat pump system 501 of the fifth embodiment is the same as the heat pump system 1 of the first embodiment, except that the second hot water supply heat pump pipe 95b, the third hot water supply heat pump pipe 95c, and the fourth hot water supply heat pump pipe 95d are replaced with the 52nd hot water supply heat pump pipe.
  • the 595b is a system in which a 55th high-pressure pipe 527e is provided in place of the fifth high-pressure pipe 27e, the sixth high-pressure pipe 27f, and the seventh high-pressure pipe 27g.
  • the hot water supply intermediate temperature sensor 95T used in the heat pump system 1 of the first embodiment is not necessary.
  • the 52nd hot water supply heat pump pipe 595b connects the hot water supply pump 92 and the upstream end of the flow of hot water for the 5th hot water supply heat pump pipe 95e in the first high-pressure water heat exchanger 51.
  • the 55th high pressure pipe 527e connects the downstream side end portion in the flow direction of the primary refrigerant in the fourth high pressure pipe 27d in the second high pressure water heat exchanger 52 and the third high pressure point H. Since other configurations are the same as those in the first embodiment, description thereof is omitted.
  • the temperature of hot water stored in the hot water storage tank 91 is rising, and the temperature of the hot water detected by the hot water incoming temperature sensor 94T is the second high-pressure water heat.
  • the temperature of the primary refrigerant passing through the outlet of the fourth high-pressure pipe 27d in the exchanger 52 is higher than that of the primary refrigerant toward the third high-pressure point H, the water for hot water supply is not heated. There is no cooling. For this reason, efficient operation is possible even in a situation where the hot water supply load is small.
  • Modified example (A) of the fifth embodiment As shown in FIG. 8, in the heat pump system 501 of the fifth embodiment, the 55th high pressure pipe 527e is used in place of the 47th high pressure pipe 427g while applying the injection path 470 described in the fourth embodiment.
  • the heat pump system 501A may be used.
  • the heat pump system 601 of the sixth embodiment is the same as the heat pump system 301 of the third embodiment that does not have the injection path 70, but the gas-liquid separation injection path 630.
  • the gas-liquid separation injection path 630 includes a pre-separation gas-liquid pipe 631, a gas-liquid separator 632, a post-separation liquid pipe 633, a post-separation air pipe 634, a post-separation tracheal opening / closing valve 635, and a gas-liquid separation expansion valve 605. ing.
  • the pre-separation gas-liquid pipe 631 extends from the third low pressure point M to the gas phase space above the gas-liquid separator 632.
  • the gas-liquid separator 632 separates the primary refrigerant flowing from the pre-separation gas-liquid pipe 631 into a gas phase region in the upper space and a liquid phase region in the lower space.
  • the post-separation liquid pipe 633 guides the primary refrigerant existing in the liquid phase region of the gas-liquid separator 632 to the gas-liquid separation expansion valve 605. In the gas-liquid separation expansion valve 605, the pressure of the passing primary refrigerant is further reduced.
  • the post-separation trachea 634 guides the primary refrigerant existing in the gas phase region of the gas-liquid separator 632 to the injection confluence point D.
  • the post-separation tracheal opening / closing valve 635 can switch between a state where the passage of the primary refrigerant in the post-separation trachea 634 is permitted and a state where the passage is not permitted. Since other configurations are the same as those in the first embodiment, description thereof is omitted.
  • the decompression of the primary refrigerant in the expansion valve 5a and / or the primary bypass expansion valve 5b is reduced to a pressure lower than the critical pressure equivalent to the primary refrigerant flowing through the intermediate pressure pipe 23, thereby causing a gas-liquid two-phase state. It becomes.
  • the primary refrigerant in the liquid state is lowered to the pressure of the primary refrigerant flowing through the low-pressure pipe 20 in the gas-liquid separation expansion valve 605. Since the post-separation trachea 634 extends from the gas phase region of the gas-liquid separator 632, the liquid primary refrigerant hardly mixes into the post-separation trachea 634, and the gaseous primary refrigerant flows.
  • the primary refrigerant sucked by the high-stage compressor 25 is unlikely to become wet. Thereby, it is possible to prevent liquid compression in the high-stage compressor 25 while increasing efficiency by increasing the density of refrigerant sucked by the high-stage compressor 25. Note that, when the primary refrigerant in the expansion valve 5a is depressurized, the pressure can be reduced only to the level of the primary refrigerant flowing in the intermediate pressure pipe 23 without being lowered to the pressure of the primary refrigerant flowing in the low pressure pipe 20.
  • the heat pump system 601 of the sixth embodiment may be a heat pump system 601A that does not have the third high-pressure water heat exchanger 53 as described in the fifth embodiment. Since other configurations are the same as those in the first embodiment, description thereof is omitted.
  • the heat pump system 701 of the seventh embodiment sets the position of the injection confluence point D in the heat pump system 1 of the first embodiment to the discharge side of the low-stage compressor 21. And an injection merging point 7D in the middle of the first intermediate pressure pipe 23a connecting the downstream end of the second intermediate pressure pipe 23b in the intermediate pressure water heat exchanger 40. Since other configurations are the same as those in the first embodiment, description thereof is omitted.
  • the compression ratio of the high stage compressor 25 is increased while the compression ratio of the high stage compressor 25 is increased so that the target temperature is obtained as the discharge refrigerant temperature of the high stage compressor 25.
  • the refrigerant discharged from the low-stage compressor 21 is heated in the intermediate pressure water heat exchanger 40. May become too high for the secondary refrigerant. Even in such a case, it is possible to suppress an excessive increase in the temperature of the secondary refrigerant for heating by providing the injection junction point 7D in the middle of the first intermediate pressure pipe 23a.
  • the high-stage compressor after the primary refrigerant passing through the injection path 70 joins at the injection joining point D and after passing through the intermediate pressure water heat exchanger 40 is also shown.
  • the temperature and pressure of the primary refrigerant to be sucked by 25 are values detected by the high-stage suction pressure sensor 24P and the high-stage suction temperature sensor 24T, and the control unit 11 grasps the temperature and pressure of the primary refrigerant. Control which suppresses that the primary refrigerant
  • the heat pump system 801 of the eighth embodiment changes the order of the economizer heat exchanger 7 and the primary inter-refrigerant heat exchanger 8 in the heat pump system 1 of the first embodiment. It is a reversed system. That is, in the heat pump system 801 of the eighth embodiment, an 83rd intermediate pressure point 8H on the downstream side of the third low pressure point M is provided instead of the third high pressure point H in the heat pump system 1 of the first embodiment. In this system, an injection path 870 is branched from the intermediate pressure point 8H.
  • the 810 high-pressure pipe 827j connects the downstream end of the sixth high-pressure pipe 27f in the third high-pressure water heat exchanger 53 and the fourth high-pressure point I.
  • the 87th high pressure pipe 827g connects the third low pressure point M and the 83rd intermediate pressure point 8H.
  • the 88th high pressure pipe 827h connects the 83rd intermediate pressure point 8H and the upstream end of the 89th high pressure pipe 827i in the economizer heat exchanger 7. Since other configurations are the same as those in the first embodiment, description thereof is omitted.
  • the primary refrigerant heat exchanger 8 can warm the primary refrigerant sucked by the low-stage compressor 21 by the relatively warm primary refrigerant before being cooled by the economizer heat exchanger 7. Thereby, even if the temperature of the primary refrigerant passing through the intermediate-pressure water heat exchanger 40 is excessively lowered by the secondary refrigerant temperature unified control, the primary refrigerant sucked by the high-stage compressor 25 does not become wet. It becomes possible to increase the amount of the primary refrigerant toward the high-pressure water heat exchanger 50.
  • the heat pump system 901 of the ninth embodiment warms water for hot water supply also in the second high-pressure water heat exchanger 52 in the heat pump system 1 of the first embodiment.
  • This is the system. That is, in the heat pump system 901 of the ninth embodiment, instead of the fourth hot water supply heat pump pipe 95d in the heat pump system 1 of the first embodiment, the 95th upstream connection pipe 995x, the 95th hot water supply heat pump pipe 995d, and the 95th downstream.
  • a connecting pipe 995y is provided, and an upstream connection temperature sensor 95Tx that detects the temperature of hot water passing through the 95th upstream connecting pipe 995x and a temperature of hot water passing through the 95th downstream connecting pipe 995y are detected.
  • This is a system provided with a downstream connection temperature sensor 95Ty. Since other configurations are the same as those in the first embodiment, description thereof is omitted.
  • the secondary refrigerant for heating flowing through the second high-pressure side branch 68b out of the heat released from the fourth high-pressure pipe 27d cannot be absorbed. Since water for hot water flowing through the 95th hot water supply heat pump pipe 995d can be absorbed, heat loss released from the fourth high pressure pipe 27d can be suppressed and used effectively. In addition, since a portion where both the secondary refrigerant for heating and the water for hot water supply receive the heat of the primary refrigerant at the same time is provided, it is necessary to heat the water for hot water supply to the required water temperature. The size of the heat exchanger can be made compact.
  • a heat pump system 1x according to a tenth embodiment is a system configured to remove the hot water supply circuit 90 in the heat pump system 1 according to the first embodiment, as shown in FIG. That is, the heat pump system 5x of the fourteenth embodiment removes the first high-pressure water heat exchanger 51, the third high-pressure water heat exchanger 53, and the hot water supply circuit 90 in the heat pump system 1 of the first embodiment, and the first high-pressure pipe 27a, the second high-pressure pipe 27b, and the third high-pressure pipe 27c are provided with a fourteenth upstream high-pressure pipe 127a, and the fifth high-pressure pipe 27e, the sixth high-pressure pipe 27f, and the seventh high-pressure pipe 27g are replaced with a fourteenth downstream high-pressure pipe 27a.
  • the fourteenth upstream high-pressure pipe 127a connects the discharge side of the high-stage compressor 25 and the upstream end of the fourth high-pressure pipe 27d in the second high-pressure water heat exchanger 52.
  • the fourteenth downstream high-pressure pipe 127e connects the downstream end of the fourth high-pressure pipe 27d in the second high-pressure water heat exchanger 52 and the third high-pressure point H. Since other configurations are the same as those in the first embodiment, description thereof is omitted.
  • the heat pump system 2x of the eleventh embodiment includes the second intermediate pressure water heat exchanger 153 that exchanges heat between the primary refrigerant that has passed through the intermediate pressure water heat exchanger 40 and the water for hot water supply.
  • the second branch hot water supply heat pump pipe 195b extends to the downstream end of the second intermediate pressure water heat exchanger 153 after branching in the middle of the second hot water supply heat pump pipe 95b.
  • the hot water supplying water flowing into the third branch hot water supply heat pump pipe 195 c through the second branch hot water supply heat pump pipe 195 b and the third intermediate pressure water heat exchanger 40 after passing through the intermediate pressure water heat exchanger 40 are used.
  • Heat exchange is performed with the primary refrigerant flowing into the eleventh intermediate pressure pipe 123c, which is a part of the intermediate pressure pipe 23c.
  • Water for hot water passing through the third branch hot water supply heat pump pipe 195c in the second intermediate pressure water heat exchanger 153 flows to the branch hot water mixing valve 193 through the fourth branch hot water supply heat pump pipe 195d, and the fourth hot water supply heat pump pipe 95d. It joins with water for hot water that has passed through.
  • the hot-water supply water that has joined at the branch hot-water supply mixing valve 193 flows into the fifth hot-water supply heat pump pipe 95e in the first high-pressure water heat exchanger 51 through the hot-water supply connection pipe 196. Since other configurations are the same as those in the first embodiment, description thereof is omitted.
  • the efficiency may be improved by further cooling in the range where liquid compression does not occur in the high stage compressor 25.
  • cold water for hot water supply is compressed not only on the high-pressure water heat exchanger 50 side but also on the downstream side and the high stage side of the intermediate-pressure water heat exchanger 40.
  • the heat of the primary refrigerant flowing between the suction side of the machine 25 can be used for heating.
  • the control unit 11 further performs branch hot water mixing.
  • the valve 193 By controlling the valve 193 to adjust the flow rate of the fourth branch hot water supply heat pump pipe 195d and the flow rate of the fourth hot water supply heat pump pipe 95d, the deterioration of the cycle efficiency of the heat pump circuit 10 can be kept small.
  • the control unit 11 may use the branch hot water mixing valve when the cycle efficiency of the heat pump circuit 10 is somewhat deteriorated.
  • the flow rate of the fourth branch hot water supply heat pump pipe 195d can be increased, and the deterioration of the cycle efficiency of the heat pump circuit 10 can be kept small.
  • the present invention is not limited to this, and may be a heat pump system capable of heat exchange as described below without departing from the gist of the present invention.
  • the primary refrigerant and the secondary refrigerant for heating in the high-pressure water heat exchanger 50 of the first embodiment may be performed at three locations, such as heat exchange between water and hot water.
  • heat exchange between the hot water supply water and the primary refrigerant flowing through the intermediate pressure pipe 23 is performed by heat exchange between the heating secondary refrigerant and the primary refrigerant.
  • a heat pump system 3x according to a twelfth embodiment is a system in which a bypass path is provided in the heating circuit 60 in the heat pump system 1 according to the first embodiment, as shown in FIG.
  • the heat pump system 3x of the twelfth embodiment is a heating circuit 60 in the heat pump system 1 of the first embodiment, in which the heating bypass branch point Z in the middle of the heating return pipe 66 and the heating junction point Y are connected.
  • This is a system in which a bypass passage 69 is further provided and a twelfth heating mixing valve 164 is provided instead of the heating mixing valve 64 in the first embodiment.
  • the twelfth heating mixing valve 164 the cold heating secondary refrigerant just radiated by the radiator 61 flowing from the heating bypass passage 69 and the heated heating flow flowing through the intermediate pressure side branch passage 67.
  • the mixing ratio of the secondary refrigerant and the warmed secondary refrigerant for heating flowing through the high-pressure side branch 68 is adjusted by an instruction from the control unit 11. Since other configurations are the same as those in the first embodiment, description thereof is omitted.
  • the control unit 11 operates the twelfth heating mixing valve 164 to open the heating bypass passage 69 even if the amount of heat to the radiator 61 is likely to be excessive.
  • the flow rate of the secondary refrigerant for heating flowing toward the heating junction point Y can be adjusted.
  • the secondary refrigerant having a temperature exceeding the temperature required in the radiator 61 and the secondary refrigerant having a temperature lower than the temperature required in the radiator 61 after the heat radiation in the radiator 61 is mixed. Is done.
  • the controller 11 adjusts the mixing ratio in the twelfth heating mixing valve 164 so that the temperature of the secondary refrigerant after mixing becomes the temperature required in the radiator 61.
  • the secondary refrigerant having the temperature required in the radiator 61 can be supplied to the radiator 61 while suppressing the occurrence of liquid compression in the high-stage compressor 25.
  • the heat pump system 4x of the thirteenth embodiment is the same as the heat pump system 1 of the first embodiment, except that the economizer heat exchanger 7 and the third high pressure point H are the third low pressure. This is a system configured to be sandwiched between a point and a portion branched by a flow toward the primary refrigerant heat exchanger 8 and a flow toward the primary bypass 80.
  • the fourth high pressure point I in the heat pump system 1 of the first embodiment is changed, and is upstream of the third high pressure point H and from the third high pressure water heat exchanger 53.
  • the seventh high pressure pipe 127g connects the downstream end of the sixth high pressure pipe 27f in the third high pressure water heat exchanger 53 and the thirteenth high pressure point 13I.
  • the bypass upstream economizer high-pressure pipe 127n connects the thirteenth high-pressure point 13I and the third high-pressure point H.
  • the bypass downstream economizer high-pressure pipe 127j connects between the downstream end of the ninth high-pressure pipe 27i in the economizer heat exchanger 7 and the primary bypass expansion valve 5b. Since other configurations are the same as those in the first embodiment, description thereof is omitted.
  • the primary refrigerant that is directed to the expansion valve 5a is divided into a flow path that is cooled by the economizer heat exchanger 7 and a flow path that is cooled by the heat exchanger 8 between the primary refrigerants. It becomes possible to adjust how much the primary refrigerant is cooled.
  • each heat pump system has been specifically described.
  • the present invention is not limited to this, and the present invention includes those in which the heat pump system of each embodiment is configured as described below without departing from the scope of the invention.
  • the case where carbon dioxide is used as the primary refrigerant has been described as an example.
  • ethylene, ethane, nitrogen oxide, or the like which is a refrigerant other than carbon dioxide
  • a refrigerant in which the discharge refrigerant pressure of the high stage compressor 25 is used exceeding the critical pressure and the driving force of each compressor can be kept small is preferable.
  • the secondary refrigerant is not limited to water, and brine or the like may be used as another heat medium.
  • a so-called single-shaft double-stage or single-shaft multi-stage type compression mechanism in which a common drive shaft is employed in the low-stage compressor 21 and the high-stage compressor 25 is provided. It may be done. In this case, it is possible to increase driving efficiency by providing a phase difference of 180 degrees in each compression mechanism.
  • the case where the low-stage compressor 21 and the high-stage compressor 25 are connected in series has been described as an example. However, in any of the above embodiments, a form in which three or more compression mechanisms are connected in series may be used. In that case, heat load processing may be performed using the heat of the primary refrigerant flowing between the compression mechanisms.
  • the optimization of the cycle efficiency in the heat pump circuit 10 may be absolutely prioritized over the supply of the amount of heat required in the radiator 61.
  • the supply of heat to the radiator 61 may be insufficient.
  • the heating that passes between the downstream side including the third high-pressure side branch path 68 c of the heating circuit 60 or the downstream side including the third intermediate-pressure side branch path 67 c to the radiator 61 it is good also as the heat pump system 5x provided with 60 A of external heat-source parts for heating the secondary refrigerant
  • a heat supply unit similar to the external heat source unit 60 ⁇ / b> A may be provided only in the hot water supply circuit 90, or may be provided in both the heating circuit 60 and the hot water supply circuit 90.
  • this external cooling source part 60B for example, a part of the water supply pipe 94 through which the outside normal city water flows flows is bypassed by the supply water branch valve 94B and the supply water branch 194, so The secondary refrigerant flowing through the heating forward pipe 65 may be cooled by exchanging heat with the secondary refrigerant for heating flowing through the pipe 65.
  • a change in the environment in which the evaporator 4 is installed, a change in the heating load, or a change in the hot water supply load occurs, so that the cycle efficiency of the heat pump circuit 10 can be maintained satisfactorily so that the heating load cannot be handled. Even when this occurs, it becomes possible to cope with the heating load while maintaining the cycle efficiency of the heat pump circuit 10 well.
  • the heat pump system 10 increases the efficiency as the heat pump system by recovering the heat that the heat pump circuit 10 has given to the secondary refrigerant of the heating circuit 60 as heat for water supply. You can also.
  • the heat supply unit similar to the external cooling source unit 60B may be provided only in the hot water supply circuit 90, or may be provided in both the heating circuit 60 and the hot water supply circuit 90.
  • the temperature required for the radiator 61 of the heating circuit 60 the temperature required for hot water flowing through the sixth hot water supply heat pump pipe 95f flowing into the hot water storage tank 91 in the hot water supply circuit 90, and the heat pump circuit
  • the relationship between the temperature of the primary refrigerant flowing through the 10 intermediate-pressure water heat exchanger 40 and the high-pressure water heat exchanger 50 and the temperature of the primary refrigerant is not particularly limited.
  • the control unit 11 controls the expansion valve 5a so that the temperature of the primary refrigerant flowing through the intermediate pressure water heat exchanger 40 exceeds the temperature required by the radiator 61 of the heating circuit 60.
  • the cycle efficiency of the heat pump circuit 10 is improved under the condition that the valve opening, the drive frequency of the low-stage compressor 21, the drive frequency of the high-stage compressor 25, etc. are controlled. May be.
  • the heating circuit 60 creates a secondary refrigerant having a temperature required in the radiator 61 only by the heat obtained by the secondary refrigerant flowing through the intermediate pressure side branch passage 67 side, which is the intermediate pressure water heat exchanger 40 side. It becomes possible.
  • ⁇ 14-7> In each of the above embodiments, the case where the compression ratio of the low-stage compressor 21 and the compression ratio of the high-stage compressor 25 are made equal in order to increase the cycle efficiency of the heat pump circuit 10 has been described as an example.
  • the compression ratio of the low-stage compressor 21 and the compression ratio of the high-stage compressor 25 are not necessarily the same. For example, the difference between the two compression ratios is reduced. Such control is also included.
  • the control unit 11 increases the flow rate of the heating pump 63 when the unified temperature exceeds the temperature required by the radiator 61. In some cases, the heat exchange time may be shortened. However, if control is performed to increase the flow rate of the heating pump 63 in this way, the primary refrigerant in the intermediate pressure water heat exchanger 40 is further cooled, and thus the primary suctioned by the high-stage compressor 25. There is a risk that the degree of superheat of the refrigerant will be reduced or that the refrigerant will become wet.
  • the control unit 11 does not change the target discharge temperature of the low-stage compressor 21 and does not change the target discharge temperature of the high-stage compressor 25.
  • the low-stage suction superheat degree control for increasing the superheat degree of the primary refrigerant sucked by the machine 21 may be performed. For example, assume that the cycle of the heat pump circuit 10 is executed and the flow rate of the heating pump 63 is increased, as indicated by the dotted line in the Mollier diagram of FIG.
  • the control unit 11 performs low-stage suction superheat degree control, so that the target discharge temperature of the high-stage compressor 25 is not changed without changing the target discharge temperature of the low-stage compressor 21.
  • the degree of superheat of the primary refrigerant sucked by the low stage compressor 21 is increased.
  • the cycle of the heat pump circuit 10 is executed as indicated by the solid line in the Mollier diagram of FIG.
  • the suction refrigerant density of the low-stage compressor 21 is slightly reduced, the degree of superheat of the primary refrigerant sucked by the high-stage compressor 25 is reduced due to changes in ambient conditions such as an increase in heating load.
  • the state of the primary refrigerant sucked by the high-stage compressor 25 is in a state where the degree of superheat is increased by moving in a direction away from the saturated vapor line. For this reason, liquid compression is unlikely to occur in the high-stage compressor 25.
  • the target discharge temperature of the low-stage compressor 21 and the target discharge temperature of the high-stage compressor 25 are not changed. . For this reason, heating of the secondary refrigerant for heating by heat exchange in the intermediate-pressure water heat exchanger 40 and heating of the secondary refrigerant for heating by heat exchange in the high-pressure water heat exchanger 50 are sufficiently performed. Is done.
  • both the compression ratio of the low stage side compressor 21 and the compression ratio of the high stage side compressor 25 can be made small, the efficiency of the heat pump circuit 10 can also be improved.
  • the above-described low-stage suction superheat degree control is performed, for example, in the heat pump circuit 10 having the primary bypass 80 and the primary bypass expansion valve 5b in the heat pump system shown in the embodiment and the modified example.
  • the degree of heat exchange in the primary refrigerant heat exchanger 8 can be adjusted by the control unit 11 controlling the valve opening degree of the bypass expansion valve 5b. In this way, the degree of superheat of the primary refrigerant sucked by the low-stage compressor 21 can be adjusted.
  • the control unit 11 drives the low-stage compressor 21 so that the target discharge temperature of the low-stage compressor 21 and the target discharge temperature of the high-stage compressor 25 are different. You may make it control a frequency, the drive frequency of the high stage side compressor 25, the valve opening degree of the expansion valve 5a, etc. FIG. In this case, low-stage discharge temperature reduction control may be performed to lower the target discharge temperature of the low-stage compressor 21.
  • the control unit 11 performs the low stage discharge temperature lowering control, thereby lowering the target discharge temperature of the low stage side compressor 21 and changing the target discharge temperature of the high stage side compressor 25 without changing the target discharge temperature.
  • the flow rate of the secondary refrigerant for heating flowing in the second high-pressure water heat exchanger 52 is increased while the flow rate of the secondary refrigerant for heating flowing in the pressure water heat exchanger 40 is lowered.
  • the target discharge temperature of the low-stage compressor 21 is set to, for example, 65 ° C.
  • the cycle of the heat pump circuit 10 is executed as indicated by the solid line in the Mollier diagram of FIG.
  • the dotted cycle and the solid cycle are compared, and the solid cycle is farther from the saturated vapor line. It is moving in the direction and the degree of superheat is increasing. Accordingly, even if the flow rate of the heating pump 63 is increased and the degree of superheat of the primary refrigerant sucked by the high stage compressor 25 is reduced, the primary refrigerant sucked by the high stage compressor 25 is reduced.
  • the state is that the degree of superheat is increased by moving in a direction away from the saturated vapor line, liquid compression is unlikely to occur in the high-stage compressor 25. Further, even when the cycle indicated by the solid line in the Mollier diagram of FIG. 23 is performed as described above, the target discharge temperature of the high stage compressor 25 is not changed. Further, although the target discharge temperature of the low-stage compressor 21 is lowered, the flow rate of the secondary refrigerant for heating that passes through the intermediate pressure water heat exchanger 40 is also lowered, so that it corresponds to the load. You can maintain a situation that you can do. Moreover, since both the compression ratio of the low stage side compressor 21 and the compression ratio of the high stage side compressor 25 can be made small, the efficiency of the heat pump circuit 10 can also be improved.
  • the control unit 11 controls the valve opening of the expansion valve 5a, the drive frequency of the low-stage compressor 21, the drive frequency of the high-stage compressor 25, and the like. This can be achieved.
  • the ambient temperature environment condition of the radiator 61 in which the heat pump system is used is not particularly limited has been described as an example.
  • the temperature of the secondary refrigerant radiated by the radiator 61 is a temperature range condition between the critical temperature of carbon dioxide as the primary refrigerant and a temperature about 5 degrees lower than the critical temperature. This condition may be limited as a use environment condition of the heat pump system.
  • the heat pump system When the heat pump system is used in such a use environment, it is used for a heat load at a temperature lower than the critical temperature of carbon dioxide as a primary refrigerant. For this reason, heat exchange can be performed in the high-pressure water heat exchanger 50 between the primary refrigerant in a state exceeding the critical pressure and the secondary refrigerant having a temperature lower than the critical temperature. Heat dissipation treatment can be performed in an area where the slope of the isotherm is gentle. For this reason, the driving
  • control unit 11 controls the flow rate of the heating mixing valve 64 and the heating pump 63 based on the temperatures detected by the intermediate pressure side branch temperature sensor 67T and the high pressure side branch temperature sensor 68T, and the heating circuit 60
  • the control unit 11 controls the flow rate of the heating mixing valve 64 and the heating pump 63 based on the temperatures detected by the intermediate pressure side branch temperature sensor 67T and the high pressure side branch temperature sensor 68T, and the heating circuit 60
  • a system in which the flow rate of the secondary refrigerant in the third intermediate pressure side branch path 67c and the third high pressure side branch path 68c may not be grasped is described as an example.
  • the secondary refrigerant for heating flowing through the intermediate pressure side branch 67 may include an intermediate pressure side branch flow meter 67Q that grasps the flow rate and a high pressure side branch flow meter 68Q that grasps the flow rate of the secondary refrigerant for heating that flows through the high pressure side branch 68.
  • the control unit 11 uses the flow rate grasped by the intermediate pressure side branch flow meter 67Q and the flow rate grasped by the high pressure side branch flow meter 68Q for heating through the third intermediate pressure side branch flow channel 67c.
  • the flow rate of the heating mixing valve 64 and / or the heating pump 63 is controlled so that the difference between the temperature of the secondary refrigerant and the temperature of the secondary refrigerant for heating flowing through the third high-pressure side branch 68c is reduced.
  • the temperature of the secondary refrigerant for heating flowing through the third intermediate pressure side branch path 67c and the temperature of the secondary refrigerant for heating flowing through the third high pressure side branch path 68c are the same temperature. May be controlled.
  • the control unit 11 grasps the temperature of the primary refrigerant flowing through the intermediate pressure water heat exchanger 40 with the intermediate pressure temperature sensor 23T, and drives the flow rate of the primary refrigerant flowing through the intermediate pressure water heat exchanger 40 to the low-stage compressor 21.
  • the frequency, the detected temperature of the intermediate pressure temperature sensor 23T, and the detected pressure of the high stage suction pressure sensor 24P are grasped.
  • the control part 11 grasps
  • the control unit 11 further grasps the flow rate of the secondary refrigerant flowing through the intermediate pressure side branch path 67 by the intermediate pressure side branch path flow meter 67Q. Thus, the control unit 11 calculates the amount of heat obtained by the heating secondary refrigerant based on the temperature difference between the primary refrigerant and the heating secondary refrigerant in the intermediate-pressure water heat exchanger 40 and each flow rate, and The expected value is calculated as the temperature of the secondary refrigerant for heating that passes through the third intermediate pressure side branch passage 67c.
  • the control unit 11 controls the second high pressure water heat exchanger 52 based on the driving frequency of the high pressure sensor 27T, the high pressure sensor 27P and the high stage compressor 25, the flow rate of the hot water supply intermediate temperature sensor 95T and the hot water supply pump 92, and the like. Know the temperature and flow rate of the flowing primary refrigerant. Moreover, the control part 11 grasps
  • the control part 11 calculates the calorie
  • the control unit 11 calculates the temperature of the secondary refrigerant for heating passing through the third intermediate pressure side branch 67c calculated as described above and the temperature of the secondary refrigerant for heating passing through the third high pressure side branch 68c.
  • the heating mixing valve 64 and / or the heating pump 63 is controlled so that the difference from the temperature becomes small.
  • the temperature of the secondary refrigerant for heating passing through the third intermediate pressure side branch passage 67c calculated here and the temperature of the secondary refrigerant for heating passing through the third high pressure side branch passage 68c are used.
  • the content of the general control is the same as the content described in the above embodiment.
  • the secondary refrigerant for heating that passes through the third intermediate pressure side branch path 67c can be reduced.
  • a heat pump system 8x provided with the forward pipe flow meter 65Q may be used instead of providing the high-pressure side branch flow meter 65Q.
  • the forward pipe flow meter 65Q can grasp the flow rate of the secondary refrigerant for heating that passes through the heating forward pipe 65.
  • the intermediate pressure side branch flow meter 67Q and the forward pipe flow meter 65Q also provide a high pressure by subtracting the flow rate grasped by the intermediate pressure side branch flow meter 67Q from the flow rate of the heating forward pipe 65 that can be grasped from the forward flow meter 65Q.
  • the flow rate of the secondary refrigerant for heating flowing through the side branch 68 can be grasped.
  • Other control methods and calculation methods can be the same as those of the modified example ⁇ 14-11>.
  • the forward pipe flow meter 65Q may be provided instead of providing the low pressure side branch flow meter 67Q instead of replacing the high pressure side branch flow meter 68Q.
  • the heat pump system 9x which provided the outgoing pipe temperature sensor 65T instead of the high voltage
  • the forward pipe temperature sensor 65T can grasp the temperature of the secondary refrigerant for heating that passes through the heating forward pipe 65.
  • the intermediate pressure side branch path temperature sensor 67T and the forward pipe temperature sensor 65T also calculate the amount of heat of the secondary refrigerant for heating flowing through the heating forward pipe 65 from the temperature of the heating forward pipe 65 that can be grasped from the forward pipe temperature sensor 65T.
  • the secondary refrigerant for heating flowing through the high pressure side branch path 68 The amount of heat can be grasped.
  • the flow rate of the secondary refrigerant for heating that flows through the high-pressure side branch 68 can be grasped, the amount of heat of the secondary refrigerant for heating that flows through the high-pressure side branch 68 that is grasped in this manner is used.
  • the temperature of the secondary refrigerant flowing through the branch path 68 can be grasped.
  • control after the temperature of the secondary refrigerant for heating flowing through the intermediate pressure side branch path 67 and the temperature of the secondary refrigerant for heating flowing through the high pressure side branch path 68 are as described above. It can be made to be the same as that explained in.
  • the forward pipe temperature sensor 65T may be provided instead of providing the low-pressure side branch temperature sensor 67T instead of replacing the high-pressure side branch temperature sensor 68T.
  • the control unit 11 detects the temperature of the secondary refrigerant for heating detected by the forward pipe temperature sensor 65T and other temperature sensors (for example, The heating mixing valve 64 and the heating pump 63 may be controlled so that the difference between the temperature and the temperature of the secondary refrigerant for heating grasped by the intermediate pressure side branch path temperature sensor 67T) is reduced. Even in this case, the same effects as those of the above embodiments can be obtained.
  • the present invention is not limited to the case where the temperatures are completely the same, but simply the temperature of the secondary refrigerant flowing through the third intermediate pressure side branch path 67c and the third high pressure side branch.
  • the control may be such that the difference between the temperature of the secondary refrigerant flowing through the path 68c is reduced. Furthermore, the difference between the temperature of the secondary refrigerant flowing through the third intermediate pressure side branch path 67c and the temperature of the secondary refrigerant flowing through the third high pressure side branch path 68c is not reduced, but the difference is less than a predetermined value. Control may be performed so as to satisfy the condition. ⁇ 14-15> In each of the above embodiments, the case where the flow rate ratio in the heating and mixing valve 64 is controlled when performing the secondary refrigerant temperature unified control has been described as an example.
  • the temperature of the secondary refrigerant for heating that flows through the third intermediate pressure side branch 67c and the temperature for heating that flows through the third high pressure side branch 68c by controlling the flow rate ratio in the heating mixing valve 64.
  • the control is not limited to reducing the difference from the temperature of the secondary refrigerant.
  • the control unit 11 controls the third intermediate pressure side branch passage 67c by increasing the flow rate of the heating pump 63 or decreasing the flow rate of the heating pump 63.
  • the present invention also includes a case where the difference between the temperature of the flowing secondary refrigerant for heating and the temperature of the secondary refrigerant for heating flowing in the third high-pressure side branch 68c is reduced.
  • heat exchange is performed in the second high pressure water heat exchanger 52.
  • the temperature difference between the primary refrigerant that performs heating and the secondary refrigerant for heating is greater than the temperature difference between the primary refrigerant that performs heat exchange in the intermediate pressure water heat exchanger 40 and the secondary refrigerant for heating. It is also possible to reduce the temperature difference by controlling the flow rate of the heating pump 63 by the unit 11. In this case, reducing the flow rate of the heating pump 63 increases the time for receiving heat from the primary refrigerant in any of the heat exchangers. This is because the secondary refrigerant for heating passes through the second high-pressure water heat exchanger 52 side having a large temperature difference from the secondary refrigerant.
  • the time for receiving heat from the primary refrigerant in any heat exchanger is shortened. This is because the secondary refrigerant for heating passes through the second high-pressure water heat exchanger 52 side having a large temperature difference from the secondary refrigerant. Further, when the temperature of the secondary refrigerant flowing through the third high-pressure side branch 68c is lower than the temperature of the secondary refrigerant flowing through the third intermediate-pressure side branch 67c, heat exchange is performed in the second high-pressure water heat exchanger 52.
  • the unit 11 increases the flow rate of the heating pump 63.
  • the time for receiving heat from the primary refrigerant in any heat exchanger is shortened. This is because the secondary refrigerant for heating passes through the intermediate pressure water heat exchanger 40 side having a large temperature difference from the secondary refrigerant.
  • heat exchange is performed in the second high pressure water heat exchanger 52.
  • the temperature difference between the primary refrigerant that performs heating and the secondary refrigerant for heating is smaller than the temperature difference between the primary refrigerant that performs heat exchange in the intermediate pressure water heat exchanger 40 and the secondary refrigerant for heating. It is also possible to reduce the temperature difference by performing the control in which the unit 11 reduces the flow rate of the heating pump 63.
  • the temperature of the primary refrigerant flowing into the second high-pressure water heat exchanger 52 is adjusted by adjusting the flow rate of hot water passing through the first high-pressure water heat exchanger 51.
  • the controller 11 may control the hot water supply pump 92 so as to approach the temperature of the primary refrigerant flowing into the intermediate pressure water heat exchanger 40. For example, when the target discharge temperature of the high stage side compressor 25 is set higher than the target discharge temperature of the low stage side compressor 21, the temperature of the primary refrigerant discharged from the high stage side compressor 25 is set.
  • the hot water supply water necessary for the control unit 11 to cool the primary refrigerant in the first high pressure water heat exchanger 51 is supplied based on the temperature detected by the hot water supply intermediate temperature sensor 95T.
  • the hot water supply pump 92 may be controlled.
  • the temperature in the vicinity of the inlet of the primary refrigerant of the intermediate pressure water heat exchanger 40 corresponding to the outlet side of the secondary refrigerant for heating and the second high-pressure water heat corresponding to the outlet of the secondary refrigerant for heating Since the temperature in the vicinity of the inlet of the primary refrigerant in the exchanger 52 is a close value, the temperature of the secondary refrigerant for heating flowing through the third intermediate pressure side branch 67c and the temperature for heating flowing through the third high pressure side branch 68c. It becomes easy to make the temperature of the secondary refrigerant close. For example, when the flow rate of the heating pump 63 is lowered, it is easier to unify the temperatures.
  • the operation state changes by performing the secondary refrigerant temperature unified control in the heating circuit 60 the deterioration of the cycle efficiency of the heat pump circuit 10 may be suppressed or improved in some cases.
  • the target discharge temperature of the low-stage compressor 21 is increased in order to cope with the heating load
  • the compression ratio is a tendency for the compression ratio to increase (see change from dotted line to alternate long and short dash line).
  • the compression ratio of the high-stage compressor 25 that attempts to make the compression ratio uniform also increases. For this reason, the required driving force increases and the energy consumption increases.
  • the control unit 11 may change the operation state from a dotted line cycle to a solid line cycle (see change from a dotted line to a solid line). . That is, when the target discharge temperature of the low-stage compressor 21 is increased, the low-stage intake superheat degree control is performed so that the superheat degree of the primary refrigerant sucked by the low-stage compressor 21 increases. Good. Thereby, the compression ratio of the low stage side compressor 21 required in order to achieve the target discharge temperature of the low stage side compressor 21 can be suppressed small. Accompanying this, the compression ratio of the high-stage compressor 25 can also be kept small. As a result, the required driving force can be further reduced.
  • the low-stage intake superheat that reduces the superheat degree of the primary refrigerant sucked by the low-stage compressor 21 is reduced.
  • the increase in the compression ratio of the low-stage compressor 21 is also suppressed, and the specific volume of the primary refrigerant sucked by the low-stage compressor 21 is reduced. Can do. For this reason, it is possible to increase the capacity by securing the circulation amount while suppressing the increase in the compression ratio.
  • the above-described control is performed by the primary bypass expansion valve 5b.
  • the degree of heat exchange in the primary refrigerant heat exchanger 8 can be adjusted by the control unit 11 controlling the valve opening. In this way, the degree of superheat of the primary refrigerant sucked by the low-stage compressor 21 can be adjusted.
  • the operation state changes by performing the secondary refrigerant temperature unified control in the heating circuit 60
  • the deterioration of the cycle efficiency of the heat pump circuit 10 may be suppressed or improved in some cases.
  • the control unit 11 may change the operation state from a dotted line cycle to a solid line cycle (see change from a dotted line to a solid line).
  • the control may be performed so that the degree of superheat of the primary refrigerant sucked by the low-stage compressor 21 is also lowered while the target discharge temperature of the low-stage compressor 21 is lowered.
  • the compression ratio of the high-stage compressor 25 and the compression ratio of the low-stage compressor 21 are approximately the same, and the driving force of the low-pressure compressor 21 and the high-stage compressor 25 is suppressed to be small. Driving becomes possible. And even if the target discharge temperature of the low stage side compressor 21 is lowered in this way, since the thermal load required in the radiator 61 is small, it is possible to cope with the load. As a result, the compression driving force can be further reduced while accommodating load fluctuations.
  • the above-described control is performed by the primary bypass expansion valve 5b.
  • the degree of heat exchange in the primary refrigerant heat exchanger 8 can be adjusted by the control unit 11 controlling the valve opening. In this way, the degree of superheat of the primary refrigerant sucked by the low-stage compressor 21 can be adjusted.
  • the heat pump system is used to process the heat load using a heat pump circuit including a multistage compression type compression element. It is particularly useful when applied to.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

L'invention porte sur un système de pompe à chaleur ayant un rendement de cycle accru dans le traitement d'une charge de chaleur par un réfrigérant secondaire. Le circuit de pompe à chaleur (10) dans lequel circule un réfrigérant de dioxyde de carbone comprend un compresseur basse pression (21), un compresseur haute pression (25), une soupape d'expansion (5), et un évaporateur (4). Un circuit de chauffage (60) dans lequel circule de l'eau comme réfrigérant secondaire comprend un radiateur (61). Le circuit de chauffage dans lequel circule l'eau comme milieu de chaleur pour le chauffage comprend un trajet de branchement à pression intermédiaire (67) et un trajet de branchement haute pression (68) qui sont disposés parallèlement l'un à l'autre. Une section de commande (11) actionne une soupape de mélange (64) destinée au chauffage, de telle sorte que la température du réfrigérant secondaire dans la partie du trajet de branchement à pression intermédiaire (67), ladite partie étant chauffée par un échangeur de chaleur à eau de pression intermédiaire (40), et la température du réfrigérant secondaire dans la partie du trajet de branchement haute pression (68), ladite partie étant chauffée par un échangeur de chaleur à eau de haute pression (52), soient identiques.
PCT/JP2010/001698 2009-03-13 2010-03-10 Système de pompe à chaleur WO2010103825A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US13/256,270 US20120000237A1 (en) 2009-03-13 2010-03-10 Heat pump system
CN201080012689XA CN102348942A (zh) 2009-03-13 2010-03-10 热泵系统
EP10750582A EP2407734A1 (fr) 2009-03-13 2010-03-10 Système de pompe à chaleur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009061902A JP2010216685A (ja) 2009-03-13 2009-03-13 ヒートポンプシステム
JP2009-061902 2009-03-13

Publications (1)

Publication Number Publication Date
WO2010103825A1 true WO2010103825A1 (fr) 2010-09-16

Family

ID=42728121

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2010/001698 WO2010103825A1 (fr) 2009-03-13 2010-03-10 Système de pompe à chaleur

Country Status (5)

Country Link
US (1) US20120000237A1 (fr)
EP (1) EP2407734A1 (fr)
JP (1) JP2010216685A (fr)
CN (1) CN102348942A (fr)
WO (1) WO2010103825A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018124036A (ja) * 2017-02-03 2018-08-09 株式会社デンソー ヒートポンプ装置

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120103280A1 (en) * 2010-10-08 2012-05-03 Dan Russell Wells Variable flow heating system with heating accessories placed in series
JP2011021882A (ja) * 2010-11-01 2011-02-03 Daikin Industries Ltd ヒートポンプシステム
EP2673585B1 (fr) * 2011-02-08 2018-11-28 Carrier Corporation Échangeur de chaleur à plaques brazé pour dissipation thermique refroidie à l'eau dans un circuit de réfrigération
JP5796588B2 (ja) * 2013-02-27 2015-10-21 三菱電機株式会社 オープンショーケース
US9995509B2 (en) * 2013-03-15 2018-06-12 Trane International Inc. Cascading heat recovery using a cooling unit as a source
NZ714420A (en) 2013-05-03 2018-11-30 Hill Phoenix Inc Systems and methods for pressure control in a co2 refrigeration system
SE537589C2 (sv) * 2013-05-14 2015-07-07 Energy Machines S A Värmeanläggning
ES2545696B1 (es) * 2014-03-11 2016-06-29 Hpd Process Engineering, S.A.U. Procedimiento de optimización energética en sistemas de evaporación y cristalización de sales
US20160047558A1 (en) * 2014-08-18 2016-02-18 Rinnai Corporation Hot water supply and heating system
CN104266399B (zh) * 2014-10-16 2017-03-22 珠海格力电器股份有限公司 热泵系统
EP3341662B1 (fr) 2015-08-03 2024-06-05 Hill Phoenix Inc. Système de réfrigération au co2 à échange de chaleur direct de co2
CN105115012B (zh) * 2015-09-16 2017-10-03 江苏天舒电器有限公司 一种用于暖气片采暖的热泵机组及其控制方法
CN105222219B (zh) * 2015-09-16 2017-08-29 江苏天舒电器有限公司 一种热泵机组变温采暖水温控制方法及其控制装置
US11125483B2 (en) 2016-06-21 2021-09-21 Hill Phoenix, Inc. Refrigeration system with condenser temperature differential setpoint control
US10605494B2 (en) * 2017-01-03 2020-03-31 Heatcraft Refrigeration Product LLC System and method for reusing waste heat of a transcritical refrigeration system
CN108662799A (zh) * 2017-03-31 2018-10-16 开利公司 多级制冷系统及其控制方法
WO2019171485A1 (fr) * 2018-03-07 2019-09-12 三菱電機株式会社 Système de pompe à chaleur
US11796227B2 (en) 2018-05-24 2023-10-24 Hill Phoenix, Inc. Refrigeration system with oil control system
US11397032B2 (en) 2018-06-05 2022-07-26 Hill Phoenix, Inc. CO2 refrigeration system with magnetic refrigeration system cooling
US10663201B2 (en) 2018-10-23 2020-05-26 Hill Phoenix, Inc. CO2 refrigeration system with supercritical subcooling control
EP3699513A1 (fr) * 2019-02-19 2020-08-26 Panasonic Intellectual Property Management Co., Ltd. Appareil de réfrigération
CN112424542A (zh) * 2019-06-06 2021-02-26 开利公司 制冷剂蒸气压缩系统
WO2021018314A1 (fr) * 2019-07-30 2021-02-04 青岛海信日立空调系统有限公司 Système de pompe à chaleur à co2 et procédé de commande de dégivrage associé
JP7411929B2 (ja) * 2020-02-25 2024-01-12 パナソニックＩｐマネジメント株式会社 冷凍装置
JP2021134954A (ja) * 2020-02-25 2021-09-13 パナソニックＩｐマネジメント株式会社 冷凍装置
JP6958692B1 (ja) * 2020-08-28 2021-11-02 ダイキン工業株式会社 熱源ユニット及び冷凍装置
CN112325509B (zh) * 2020-10-28 2023-06-27 青岛理工大学 中间冷却热回收三联供热泵系统

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6477067A (en) 1987-09-18 1989-03-23 Ricoh Kk Power unit
JPH024A (ja) 1987-02-04 1990-01-05 Asahi Optical Co Ltd カメラの自動焦点検出装置
JP2002106988A (ja) * 2000-09-28 2002-04-10 Sanyo Electric Co Ltd ヒートポンプ給湯機
JP2003240369A (ja) * 2002-02-13 2003-08-27 Denso Corp 多機能給湯装置
JP2003269788A (ja) * 2002-03-15 2003-09-25 Hitachi Ltd ヒートポンプ式給湯機
JP2004177067A (ja) 2002-11-29 2004-06-24 Hitachi Home & Life Solutions Inc ヒートポンプ式空気調和機
JP2006258397A (ja) * 2005-03-18 2006-09-28 Mitsubishi Electric Corp 冷凍装置
JP2006275494A (ja) * 2005-03-30 2006-10-12 Sanyo Electric Co Ltd 冷凍装置、冷蔵庫及び圧縮機
JP2007322077A (ja) * 2006-06-01 2007-12-13 Hitachi Appliances Inc ヒートポンプ給湯床暖房装置
JP2008209012A (ja) * 2007-02-23 2008-09-11 Matsushita Electric Ind Co Ltd 冷凍サイクル装置
WO2009001535A1 (fr) * 2007-06-22 2008-12-31 Panasonic Corporation Appareil à cycle de réfrigération

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3826092A1 (de) * 1988-08-01 1990-02-08 Henkel Kgaa Granulares, bleichaktivatoren enthaltendes bleichhilfsmittel mit verbesserten eigenschaften
JP2004156845A (ja) * 2002-11-07 2004-06-03 Matsushita Electric Ind Co Ltd ヒートポンプ給湯装置
JP4407689B2 (ja) * 2006-11-13 2010-02-03 三菱電機株式会社 ヒートポンプ給湯機

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH024A (ja) 1987-02-04 1990-01-05 Asahi Optical Co Ltd カメラの自動焦点検出装置
JPS6477067A (en) 1987-09-18 1989-03-23 Ricoh Kk Power unit
JP2002106988A (ja) * 2000-09-28 2002-04-10 Sanyo Electric Co Ltd ヒートポンプ給湯機
JP2003240369A (ja) * 2002-02-13 2003-08-27 Denso Corp 多機能給湯装置
JP2003269788A (ja) * 2002-03-15 2003-09-25 Hitachi Ltd ヒートポンプ式給湯機
JP2004177067A (ja) 2002-11-29 2004-06-24 Hitachi Home & Life Solutions Inc ヒートポンプ式空気調和機
JP2006258397A (ja) * 2005-03-18 2006-09-28 Mitsubishi Electric Corp 冷凍装置
JP2006275494A (ja) * 2005-03-30 2006-10-12 Sanyo Electric Co Ltd 冷凍装置、冷蔵庫及び圧縮機
JP2007322077A (ja) * 2006-06-01 2007-12-13 Hitachi Appliances Inc ヒートポンプ給湯床暖房装置
JP2008209012A (ja) * 2007-02-23 2008-09-11 Matsushita Electric Ind Co Ltd 冷凍サイクル装置
WO2009001535A1 (fr) * 2007-06-22 2008-12-31 Panasonic Corporation Appareil à cycle de réfrigération

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018124036A (ja) * 2017-02-03 2018-08-09 株式会社デンソー ヒートポンプ装置
WO2018142796A1 (fr) * 2017-02-03 2018-08-09 株式会社デンソー Appareil de pompe à chaleur

Also Published As

Publication number Publication date
CN102348942A (zh) 2012-02-08
EP2407734A1 (fr) 2012-01-18
US20120000237A1 (en) 2012-01-05
JP2010216685A (ja) 2010-09-30

Similar Documents

Publication Publication Date Title
WO2010103825A1 (fr) Système de pompe à chaleur
KR101213257B1 (ko) 냉동 장치
JP4959800B2 (ja) 冷凍サイクル装置の運転制御方法
US7131294B2 (en) Method and apparatus for control of carbon dioxide gas cooler pressure by use of a capillary tube
KR101214343B1 (ko) 냉동 장치
KR101201062B1 (ko) 냉동 장치
JP6019837B2 (ja) ヒートポンプシステム
JP5375919B2 (ja) ヒートポンプ
JP2006071137A (ja) 冷凍装置
JP2010216687A (ja) ヒートポンプシステム
JP6598882B2 (ja) 冷凍サイクル装置
WO2012090579A1 (fr) Système de source de chaleur et procédé de commande pour celui-ci
JP2007225140A (ja) ターボ冷凍機およびその制御装置ならびにターボ冷凍機の制御方法
JP2011052838A (ja) 冷凍空調装置
JP2009014208A (ja) 冷凍装置
JP2011021882A (ja) ヒートポンプシステム
JP2010197007A (ja) ヒートポンプシステム
JP2010216686A (ja) ヒートポンプシステム
JP2006145144A (ja) 冷凍サイクル装置
JP5790675B2 (ja) ヒートポンプ
JP7375167B2 (ja) ヒートポンプ
JP7241866B2 (ja) 冷凍サイクル装置
JP2013092369A5 (fr)
JP5991196B2 (ja) 冷凍装置
JP6021379B2 (ja) ヒートポンプの制御装置、ヒートポンプ、及びヒートポンプの制御方法

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 201080012689.X

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 10750582

Country of ref document: EP

Kind code of ref document: A1

DPE1 Request for preliminary examination filed after expiration of 19th month from priority date (pct application filed from 20040101)
DPE1 Request for preliminary examination filed after expiration of 19th month from priority date (pct application filed from 20040101)
NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 13256270

Country of ref document: US

WWE Wipo information: entry into national phase

Ref document number: 2010750582

Country of ref document: EP