US20110036110A1 - Refrigeration apparatus - Google Patents

Refrigeration apparatus Download PDF

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Publication number
US20110036110A1
US20110036110A1 US12/989,440 US98944009A US2011036110A1 US 20110036110 A1 US20110036110 A1 US 20110036110A1 US 98944009 A US98944009 A US 98944009A US 2011036110 A1 US2011036110 A1 US 2011036110A1
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United States
Prior art keywords
refrigerant
temperature
water
tube
heat exchanger
Prior art date
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Abandoned
Application number
US12/989,440
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English (en)
Inventor
Shuji Fujimoto
Atsushi Yoshimi
Takahiro Yamaguchi
Tooru Inazuka
Kazuhiro Furusho
Mitsuharu Uchida
Hidehiko Kataoka
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Daikin Industries Ltd
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Daikin Industries Ltd
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Assigned to DAIKIN INDUSTRIES, LTD. reassignment DAIKIN INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KATAOKA, HIDEHIKO, UCHIDA, MITSUHARU, FURUSHO, KAZUHIRO, INAZUKA, TOORU, FUJIMOTO, SHUJI, YAMAGUCHI, TAKAHIRO, YOSHIMI, ATSUSHI
Publication of US20110036110A1 publication Critical patent/US20110036110A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/18—Hot-water central heating systems using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/02—Domestic hot-water supply systems using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/16—Waste heat
    • F24D2200/24—Refrigeration
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0405—Refrigeration circuit bypassing means for the desuperheater
    • 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
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/12—Hot water central heating systems using heat pumps

Definitions

  • the present invention relates to a refrigeration apparatus, and particularly relates to a refrigeration apparatus which performs a multi-stage compression-type refrigeration cycle using refrigerant that operates including the process of a supercritical state.
  • one example of a refrigeration apparatus which performs a multi-stage compression-type refrigeration cycle using refrigerant that operates in a supercritical range is an air-conditioning apparatus which performs a two-stage compression-type refrigeration cycle using carbon dioxide as a refrigerant, such as the apparatus disclosed in Patent Literature 1 (Japanese Laid-open Patent Application No. 2007-232263).
  • An example of an apparatus that uses such a two-stage compression-type refrigeration cycle as a water heater is a water heater such as the one disclosed in Patent Literature 2 (Japanese Laid-open Patent Application No. 2002-106988), for example.
  • a conventional technique is used for improving compression efficiency by using an intercooler to cool refrigerant heading from a low-stage compression element to a high-stage compression element.
  • the intercooler can be used as a heater of hot water and also as a cooler of refrigerant drawn into the high-stage compression element, and energy efficiency can be improved.
  • An object of the present invention is to provide a refrigeration apparatus which uses refrigerant that operates including the process of a supercritical state, wherein it is possible to more reliably improve compression efficiency and make the heating of water for a hot water supply more efficient.
  • a refrigeration apparatus is refrigeration apparatus which performs heat exchange on a water tube system having a water inlet tube for leading water supplied from the exterior to a water branching point, first branching water tubes and second branching water tubes extending from the water branching point, and a water outlet tube leading out to the exterior from a convergent point where the first branching water tubes and the second branching water tubes converge, wherein the active refrigerant is in a supercritical state in at least part of the refrigeration cycle; the refrigeration apparatus comprising a main expansion mechanism, an evaporator, a first compression element, a second compression element, a first refrigerant tube, a first heat exchanger, second refrigerant tubes, and a second heat exchanger.
  • the main expansion mechanism depressurizes the refrigerant.
  • the evaporator is connected with the main expansion mechanism and the evaporator evaporates the refrigerant.
  • the first compression element draws in refrigerant that has passed through the evaporator and compresses and discharges the refrigerant.
  • the second compression element draws in the refrigerant discharged from the first compression element and further compresses and discharges the refrigerant.
  • the first refrigerant tube draws the refrigerant discharged from the first compression element into the second compression element.
  • the first heat exchanger performs heat exchange between the refrigerant passing through the first refrigerant tube and the water flowing through the first branching water tubes.
  • the second refrigerant tubes connect the discharge side of the second compression element and the main expansion mechanism.
  • the second heat exchanger subjects the refrigerant passing through the second refrigerant tubes to heat exchange with the water flowing through the second branching water tubes, and not to heat exchange with the water flowing through the water inlet tube.
  • the first compression element and the second compression element may be either housed within the same casing or the like and controlled together, or disposed separately and controlled independently of each other.
  • the temperature will sometimes be higher than the temperature of the refrigerant flowing through the first heat exchanger due to the water already being warmed before flowing into the first heat exchanger. In this case, there is a risk that it will not be possible to cool the refrigerant by heat exchange in the first heat exchanger, and that the water will be deprived of its heat by the refrigerant.
  • the second heat exchanger does not subject the refrigerant passing through the second refrigerant tube to heat exchange with the water flowing through the water inlet tube. Therefore, the water can be made to flow in during a state of low temperature in which not only is the water flowing into the second heat exchanger not yet heated by heat exchange with the refrigerant, but neither is the water flowing into the first heat exchanger.
  • the refrigerant heading from the first compression element toward the second compression element is cooled to reliably improve compression efficiency, heat exchanging which can raise the water temperature can be reliably performed by both the first heat exchanger and the second heat exchanger, and the coefficient of performance of the refrigeration apparatus can be improved.
  • a refrigeration apparatus is the refrigeration apparatus according to the first aspect of the present invention, further comprising a flow rate ratio adjustment mechanism capable of adjusting the ratio between a quantity of water flowing through the first branching water tubes and a quantity of water flowing through the second branching water tubes.
  • a refrigeration apparatus is the refrigeration apparatus according to the second aspect of the present invention, further comprising a heating capacity detection unit and a water distribution quantity control unit.
  • the heating capacity detection unit is capable of detecting the capacity of the refrigerant passing through the first heat exchanger to heat the water and the capacity of the refrigerant passing through the second heat exchanger to heat the water.
  • the water distribution quantity control unit adjusts the ratio between the quantity of water flowing through the first branching water tubes and the quantity of water flowing through the second branching water tubes by controlling the flow rate adjustment mechanism in accordance with the ratio between the heating capacities of the first heat exchanger and the second heat exchanger detected by the heating capacity detection unit.
  • the control by this water distribution quantity control unit may involve, for example, adjusting the ratio between the quantity of water flowing through the first branching water tubes and the quantity of water flowing through the second branching water tubes, either so as to achieve equality with the ratio between a first specific enthalpy obtained by subtracting the specific enthalpy of the refrigerant discharged from the first compression element from the specific enthalpy of the refrigerant drawn into the second compression element, and a second specific enthalpy obtained by subtracting the specific enthalpy of the refrigerant drawn into the second compression element from the specific enthalpy of the refrigerant discharged from the second compression element, or so as to approach this ratio.
  • the control by this water distribution quantity control unit may otherwise involve, for example, adjusting the ratio between the quantity of water flowing through the first branching water tubes and the quantity of water flowing through the second branching water tubes, so that the water temperature in the outlet of the first heat exchanger in the first branching water tubes and the water temperature in the outlet of the second heat exchanger in the second branching water tubes are substantially equal.
  • heat exchange for cooling the refrigerant and heating the water can be performed by both the first heat exchanger and the second heat exchanger, and flow rate control for improving the coefficient of performance of the refrigeration apparatus can be performed automatically.
  • a refrigeration apparatus is the refrigeration apparatus according to any of the first through third aspects of the present invention, wherein the second refrigerant tubes have a third refrigerant tube for connecting the second heat exchanger and the main expansion mechanism.
  • the refrigeration apparatus further comprises a fourth refrigerant tube for connecting the evaporator and an intake side of the first compression element, a third heat exchanger for performing heat exchange between the refrigerant flowing through the third refrigerant tube and the refrigerant flowing through the fourth refrigerant tube, a third heat exchange bypass tube for connecting one end and another end of a portion of the third refrigerant tube that passes through the third heat exchanger, and a heat exchanger switching mechanism capable of switching between a state in which refrigerant flows through the portion of the third refrigerant tube that passes through the third heat exchanger, and a state in which refrigerant flows through the third heat exchange bypass tube.
  • the coefficient of performance can be improved by raising the degree of supercooling of the refrigerant headed to the main expansion mechanism. Furthermore, through heat exchange in the third heat exchanger, the refrigerant drawn into the first compression element can be subjected to an appropriate amount of superheating, liquid compression in the first compression element can be suppressed, and the discharge temperature can be increased to keep the resulting water temperature high.
  • a refrigeration apparatus is the refrigeration apparatus according to the fourth aspect of the present invention, further comprising temperature sensory units and a heat exchange quantity control unit.
  • the temperature sensory units sense at least the air temperature surrounding the evaporator or the discharged refrigerant temperature of at least the first compression element or the second compression element.
  • the heat exchange quantity control unit controls the heat exchanger switching mechanism and increases the quantity of refrigerant flowing through the portion of the third refrigerant tube that passes through the third heat exchanger when the following condition is fulfilled: the air temperature is higher than a predetermined high-temperature air temperature when the value sensed by the temperature sensory units is an air temperature, or the refrigerant temperature is lower than a predetermined low-temperature refrigerant temperature when the value sensed by the temperature sensory units is a refrigerant temperature.
  • the quantity of refrigerant flowing through the portion of the third refrigerant tube that passes through the third heat exchanger can be increased even in cases in which it appears that the air temperature surrounding the evaporator could increase or that the temperature of the refrigerant discharged from the compression element could decrease.
  • the refrigerant drawn into the first compression element can be subjected to the appropriate degree of superheating, it is possible to impede liquid compression from occurring in the first compression element.
  • the degree of superheating of the refrigerant drawn into the first compression element can be increased, it is possible to conform to cases in which the temperature required in the radiator is high.
  • a refrigeration apparatus is the refrigeration apparatus according to any of the first through third aspects of the present invention, wherein the second refrigerant tubes have a third refrigerant tube connecting the second heat exchanger and the main expansion mechanism.
  • the refrigeration apparatus further comprises a branching expansion mechanism, a fifth refrigerant tube, sixth refrigerant tubes, and a fourth heat exchanger.
  • the branching expansion mechanism depressurizes refrigerant.
  • the fifth refrigerant tube branches off from the third refrigerant tube and extends to the branching expansion mechanism.
  • the sixth refrigerant tubes extend from the branching expansion mechanism to the first refrigerant tube.
  • the fourth heat exchanger performs heat exchange between refrigerant flowing through the third refrigerant tube and refrigerant flowing through the sixth refrigerant tubes.
  • the quantity of refrigerant passing through the second heat exchanger can be increased.
  • a refrigeration apparatus is the refrigeration apparatus according to the sixth aspect of the present invention, further comprising temperature sensory units and a branched quantity control unit.
  • the temperature sensory units sense at least the air temperature surrounding the evaporator or the discharged refrigerant temperature of at least the first compression element or the second compression element.
  • the branched quantity control unit controls the branching expansion mechanism and increases the quantity of refrigerant passing through when the following condition is fulfilled: the air temperature is lower than a predetermined low-temperature air temperature when the value sensed by the temperature sensory units is an air temperature, or the refrigerant temperature is higher than a predetermined high-temperature refrigerant temperature when the value sensed by the temperature sensory units is a refrigerant temperature.
  • the control by the branched quantity control unit for increasing the quantity of refrigerant passing through the branching expansion mechanism herein includes control for creating a flow from conditions of a flow rate of zero (no flow), for example.
  • a refrigeration apparatus is the refrigeration apparatus according to the sixth or seventh aspect of the present invention, further comprising a water temperature sensory unit, a first refrigerant temperature sensory unit, and a refrigerant distribution quantity control unit.
  • the water temperature sensory unit senses the temperature of water flowing through any position in the water tube system.
  • the first refrigerant temperature sensory unit senses the temperature of refrigerant passing through the first refrigerant tube.
  • the refrigerant distribution quantity control unit controls the branching expansion mechanism and increases the quantity of refrigerant passing through when the difference between the temperature sensed by the water temperature sensory unit and the temperature sensed by the first refrigerant temperature sensory unit is less than a predetermined value.
  • a refrigeration apparatus is the refrigeration apparatus according to any of the first through third aspects of the present invention, wherein the second refrigerant tubes have a third refrigerant tube connecting the second heat exchanger and the main expansion mechanism.
  • the refrigeration apparatus further comprises a branching expansion mechanism, a fourth refrigerant tube, a third heat exchanger, a fifth refrigerant tube, sixth refrigerant tubes, and a fourth heat exchanger.
  • the branching expansion mechanism depressurizes refrigerant.
  • the fourth refrigerant tubes connect the evaporator and an intake side of the first compression element.
  • the third heat exchanger performs heat exchange between refrigerant flowing through the third refrigerant tube and refrigerant flowing through the fourth refrigerant tubes.
  • the fifth refrigerant tube branches off from the third refrigerant tube and extends to the branching expansion mechanism.
  • the sixth refrigerant tubes connect the branching expansion mechanism and the first refrigerant tube.
  • the fourth heat exchanger performs heat exchange between refrigerant flowing through the third refrigerant tube and refrigerant flowing through the sixth refrigerant tubes.
  • a refrigeration apparatus is the refrigeration apparatus according to the ninth aspect of the present invention, further comprising temperature sensory units and a branched heat quantity control unit.
  • the temperature sensory units sense at least the air temperature surrounding the evaporator or the discharged refrigerant temperature of at least the first compression element or the second compression element.
  • the branched heat quantity control unit controls the branching expansion mechanism and increases the quantity of refrigerant passing through when the following condition is fulfilled: the air temperature is lower than a predetermined low-temperature air temperature when the value sensed by the temperature sensory units is an air temperature, or the refrigerant temperature is higher than a predetermined high-temperature refrigerant temperature when the value sensed by the temperature sensory units is a refrigerant temperature.
  • the control by the branched quantity control unit for increasing the quantity of refrigerant passing through the branching expansion mechanism herein includes control for creating a flow from conditions of a flow rate of zero (no flow), for example.
  • a refrigeration apparatus is the refrigeration apparatus according to the ninth or tenth aspect of the present invention, further comprising a first heat exchange bypass tube and a bypass switching mechanism.
  • the first heat exchange bypass tube connects one end and another end of the portion of the first refrigerant tube that passes through the first heat exchanger.
  • the bypass switching mechanism is capable of switching between a state in which refrigerant flows through the portion of the first refrigerant tube that passes through the first heat exchanger, and a state in which refrigerant flows through the first heat exchange bypass tube.
  • the switching of the bypass switching mechanism makes it possible to switch between a state of allowing and a state of not allowing the passage of refrigerant in the heat exchange bypass tube, and also to adjust the usage condition of the first heat exchanger.
  • a refrigeration apparatus is the refrigeration apparatus according to the eleventh aspect of the present invention, further comprising temperature sensory units and a bypass control unit.
  • the temperature sensory units sense at least the air temperature surrounding the evaporator or the discharged refrigerant temperature of at least the first compression element or the second compression element.
  • the bypass control unit controls the bypass switching mechanism and increases the quantity of refrigerant flowing through the portion of the first refrigerant tube that passes through the first heat exchanger when the following condition is fulfilled: the air temperature is higher than a predetermined high-temperature air temperature when the value sensed by the temperature sensory units is an air temperature, or the refrigerant temperature is lower than a predetermined low-temperature refrigerant temperature when the value sensed by the temperature sensory units is a refrigerant temperature.
  • the control by the bypass control unit for increasing the quantity of refrigerant passing through the portion of the first refrigerant tube herein includes control for creating a flow from conditions of a flow rate of zero (no flow), for example.
  • the degree of superheating of the refrigerant drawn into the second compression element can be raised by reducing the quantity of refrigerant flowing through the portion of the first refrigerant tube that passes through the first heat exchanger, and it is possible to comply with a high temperature requirement in the radiator.
  • a refrigeration apparatus is the refrigeration apparatus according to any of the ninth through twelfth aspects of the present invention, further comprising a water temperature sensory unit, a first refrigerant temperature sensory unit, and a water-correspondent refrigerant quantity control unit.
  • the water temperature sensory unit senses the temperature of water flowing through any position in the water tube system.
  • the first refrigerant temperature sensory unit senses the temperature of refrigerant passing through the first refrigerant tube.
  • the water-correspondent refrigerant quantity control unit controls the branching expansion mechanism and increases the quantity of refrigerant passing through when the difference between the temperature sensed by the water temperature sensory unit and the temperature sensed by the first refrigerant temperature sensory unit is less than a predetermined value.
  • a refrigeration apparatus is the refrigeration apparatus according to any of the first through thirteenth aspects of the present invention, further comprising a first drive unit for driving the first compression element, and a second drive unit for driving the second compression element independently of the first compression element.
  • the capacity of the first compression element and the capacity of the second compression element can be adjusted so as to be different, during control for mixing the water flowing through the first branching water tube and the water flowing through the second branching water tube and attempting to bring the temperature of the water flowing through the output water tube to a target temperature, the coefficient of performance can be made satisfactory and the effect of minimizing the compression work can be further improved by separately adjusting the capacity of the first compression element and the capacity of the second compression element.
  • a refrigeration apparatus is the refrigeration apparatus according to any of the first through thirteenth aspects of the present invention, wherein the first compression element and the second compression element have a shared rotating shaft for performing compression work by rotatably driving each of the compression elements.
  • a refrigeration apparatus is the refrigeration apparatus according to any of the first through fifteenth aspects of the present invention, wherein the active refrigerant is carbon dioxide.
  • the refrigerant heading from the first compression element toward the second compression element is cooled to reliably improve compression efficiency, heat exchanging which can raise the water temperature can be reliably performed by both the first heat exchanger and the second heat exchanger, and the coefficient of performance of the refrigeration apparatus can be improved.
  • flow rate control for improving the coefficient of performance of the refrigeration apparatus can be performed automatically.
  • the fourth aspect it is possible to improve the coefficient of performance, to suppress liquid compression in the first compression element, and to increase the discharge temperature to keep the resulting water temperature high.
  • the seventh aspect it is possible to improve the reliability of the first compression element or the second compression element.
  • the ninth aspect it is possible to improve the coefficient of performance, and to prevent liquid compression in the first compression element and/or cool the refrigerant flowing through the third refrigerant tube.
  • the coefficient of performance can be made satisfactory and the effect of minimizing the compression work can be further improved.
  • the occurrence of vibrations and/or fluctuations in torque load can be suppressed by driving the compression elements while causing their centrifugal forces to cancel each other out.
  • the efficiency of the refrigeration apparatus can be improved by a small amount of compression work.
  • FIG. 1 is a schematic structural diagram of an air-conditioning apparatus as an embodiment of the refrigeration apparatus according to the first embodiment of the present invention.
  • FIG. 2 is a pressure-enthalpy graph representing the refrigeration cycle of the air-conditioning apparatus according to the first embodiment.
  • FIG. 3 is a temperature-entropy graph representing the refrigeration cycle of the air-conditioning apparatus according to the first embodiment.
  • FIG. 4 is a schematic structural diagram of an air-conditioning apparatus according to Modification 1 of the first embodiment.
  • FIG. 5 is a schematic structural diagram of an air-conditioning apparatus according to Modification 2 of the first embodiment.
  • FIG. 6 is a schematic structural diagram of an air-conditioning apparatus according to Modification 3 of the first embodiment.
  • FIG. 7 is a schematic structural diagram of an air-conditioning apparatus according to Modification 7 of the first embodiment.
  • FIG. 8 is a schematic structural diagram of an air-conditioning apparatus as an embodiment of the refrigeration apparatus according to the second embodiment of the present invention.
  • FIG. 9 is a pressure-enthalpy graph representing the refrigeration cycle of the air-conditioning apparatus according to the second embodiment.
  • FIG. 10 is a temperature-entropy graph representing the refrigeration cycle of the air-conditioning apparatus according to the second embodiment.
  • FIG. 11 is a schematic structural diagram of an air-conditioning apparatus according to Modification 1 of the second embodiment.
  • FIG. 12 is a schematic structural diagram of an air-conditioning apparatus according to Modification 5 of the second embodiment.
  • FIG. 13 is a schematic structural diagram of an air-conditioning apparatus as an embodiment of a refrigeration apparatus according to the third embodiment of the present invention.
  • FIG. 14 is a pressure-enthalpy graph representing the refrigeration cycle of an air-conditioning apparatus according to the third embodiment.
  • FIG. 15 is a temperature-entropy graph representing the refrigeration cycle of an air-conditioning apparatus according to the third embodiment.
  • FIG. 16 is a schematic structural diagram of an air-conditioning apparatus according to Modification 1 of the third embodiment.
  • FIG. 17 is a schematic structural diagram of an air-conditioning apparatus according to Modification 4 of the third embodiment.
  • FIG. 18 is a schematic structural diagram of an air-conditioning apparatus as an embodiment of a refrigeration apparatus according to the fourth embodiment of the present invention.
  • FIG. 19 is a pressure-enthalpy graph representing the refrigeration cycle of an air-conditioning apparatus according to the fourth embodiment.
  • FIG. 20 is a temperature-entropy graph representing the refrigeration cycle of an air-conditioning apparatus according to the fourth embodiment.
  • FIG. 21 is a schematic structural diagram of an air-conditioning apparatus according to Modification 1 of the fourth embodiment.
  • FIG. 22 is a schematic structural diagram of an air-conditioning apparatus according to Modification 2 of the fourth embodiment.
  • FIG. 23 is a schematic structural diagram of an air-conditioning apparatus according to Modification 3 of the fourth embodiment.
  • FIG. 24 is a schematic structural diagram of an air-conditioning apparatus according to Modification 4 of the fourth embodiment.
  • FIG. 25 is a schematic structural diagram of an air-conditioning apparatus according to Modification 8 of the fourth embodiment.
  • FIG. 1 is a schematic structural diagram of a water heater 1 as an embodiment of the refrigeration apparatus according to the present invention.
  • the water heater 1 is an apparatus for producing heated water by using refrigerant that operates in a supercritical range (carbon dioxide in this case) to perform a two-stage compression-type refrigeration cycle.
  • refrigerant that operates in a supercritical range (carbon dioxide in this case) to perform a two-stage compression-type refrigeration cycle.
  • the water heater 1 has a water circuit 910 and a refrigerant circuit 10 .
  • the water circuit 910 has a water inlet tube 901 for leading water supplied from the exterior to a water branching point W, heat source water tubes 902 , 903 and intermediate water tubes 904 , 905 extending from the branching point W, and a water outlet tube 906 leading out to the exterior from a convergent point Z where the heat source water tubes 902 , 903 and the intermediate water tubes 904 , 905 converge, as shown in FIG. 1 .
  • a pump 921 capable of adjusting the quantity of water passing through is provided to the water inlet tube 901 .
  • This pump 921 is provided with a motor 921 m , the rotational speed is adjusted by a control unit 99 , and the flow rate of the pump is adjusted.
  • the water circuit 910 is also provided with a water temperature sensor 910 T for detecting the temperature of the water passing through the water inlet tube 901 . Through the water temperature sensor 910 T, the control unit 99 can perceive the temperature of the supplied water, the control unit 99 perceives the difference from the output water temperature requested by the user, and a refrigeration cycle of the refrigerant circuit 10 is adjusted.
  • the heat source water tube 902 extends from the branching point W to a heat source-side heat exchanger 4 of the refrigerant circuit 10 , described hereinafter.
  • the heat source water tube 903 extends so as to lead water flowing out of the heat source-side heat exchanger 4 to the convergent point Z.
  • the water flowing through the heat source water tubes 902 , 903 is warmed in the heat source-side heat exchanger 4 by heat exchange with the refrigerant flowing through the refrigerant circuit 10 , and heated water is produced.
  • a tube configuration is created so that the refrigerant and water flow opposite each other in an intercooler 7 , and the heat exchange efficiency is improved.
  • the intermediate water tube 904 extends from the branching point W to the intercooler 7 of the refrigerant circuit 10 , described hereinafter.
  • the intermediate water tube 905 extends so as to lead the water flowing out of the intercooler 7 to the convergent point Z.
  • the water flowing through the intermediate water tubes 904 , 905 is warmed in the intercooler 7 by heat exchange with the refrigerant flowing through the refrigerant circuit 10 , and heated water is produced.
  • a tube configuration is created so that the refrigerant and water flow opposite each other in the heat source-side heat exchanger 4 , and the heat exchange efficiency is improved.
  • the intermediate water tubes 904 , 905 are designed to be smaller in diameter than the heat source water tubes 902 , 903 in order to ensure that the water heating will take place primarily in the heat source-side heat exchanger 4 .
  • Hot water which has been warmed in the heat source water tubes 902 , 903 and in the intermediate water tubes 904 , 905 and mixed at the convergent point Z is then supplied to the user through the water outlet tube 906 .
  • the refrigerant circuit 10 has primarily a low-stage compression element 2 c , a high-stage compression element 2 d , the heat source-side heat exchanger 4 , an expansion mechanism 5 , a usage-side heat exchanger 6 , an intermediate refrigerant tube 22 , an intercooler 7 , connection tubes 71 , 72 , 76 or the like connecting these components, and a usage-side temperature sensor 6 T.
  • the low-stage compression element 2 c and the high-stage compression element 2 d compress the refrigerant sequentially in two stages.
  • the low-stage compression element 2 c has a hermetically sealed structure in which a compressor drive motor 21 b and a drive shaft 21 c are housed within a casing 21 a .
  • the compressor drive motor 21 b is linked to the drive shaft 21 c .
  • This drive shaft 21 c is linked to the compression element 2 c .
  • the compression element 2 c is a rotary-type, scroll-type, or another type of positive displacement compression element in the present embodiment.
  • the low-stage compression element 2 c draws refrigerant in from an intake tube 2 a , compresses the drawn-in refrigerant, and discharges the refrigerant toward the intermediate refrigerant tube 22 .
  • the intermediate refrigerant tube 22 connects the discharge side of the low-stage compression element 2 c and the intake side of the high-stage compression element 2 d via the intercooler 7 .
  • a discharge tube 2 b is a refrigerant tube for feeding the refrigerant discharged from the low-stage compression element 2 c to the high-stage compression element 2 d via the intercooler 7 , and the discharge tube 2 b is provided with a non-return mechanism 42 c and a mechanism for separating the refrigerant from refrigeration oil which accompanies the refrigerant discharged from the low-stage compression element 2 c and returning the refrigeration oil to the intake side of the low-stage compression element 2 c .
  • the mechanism for returning the refrigeration oil has primarily an oil separator 41 a for separating the refrigerant from the refrigeration oil accompanying the refrigerant discharged from the low-stage compression element 2 c , and an oil return tube 41 b which is connected to the oil separator 41 a and which returns the refrigeration oil separated from the refrigerant to the intake tube 2 a of the low-stage compression element 2 c .
  • the oil return tube 41 b is provided with a depressurization mechanism 41 c for depressurizing the refrigeration oil flowing through the oil return tube 41 b .
  • a capillary tube is used as the depressurization mechanism 41 c in the present embodiment.
  • the non-return mechanism 42 c is a mechanism for allowing the flow of refrigerant from the discharge side of the low-stage compression element 2 c to the intercooler 7 and blocking the flow of refrigerant from the intercooler 7 to the discharge side of the low-stage compression element 2 c , and a non-return valve is used in the present embodiment.
  • the high-stage compression element 2 d is similar to the low-stage compression element 2 c , and has a hermetically sealed structure in which a compressor drive motor 21 e and a drive shaft 21 f are housed within a casing 21 d .
  • the compressor drive motor 21 e is linked to the drive shaft 21 f .
  • This drive shaft 21 f is linked to the compression element 2 d .
  • the compression element 2 d is a rotary-type, scroll-type, or another type of positive displacement compression element in the present embodiment.
  • the high-stage compression element 2 d draws refrigerant in from the intermediate refrigerant tube 22 , compresses the drawn-in refrigerant, and discharges the refrigerant toward a discharge tube 2 e .
  • the discharge tube 2 e connects the discharge side of the high-stage compression element 2 d and the heat source-side heat exchanger 4 .
  • the discharge tube 2 e is provided with a non-return mechanism 42 d and a mechanism for separating the refrigerant from refrigeration oil which accompanies the refrigerant discharged from the high-stage compression element 2 d and returning the refrigeration oil to the intake side of the high-stage compression element 2 d .
  • the mechanism for returning the refrigeration oil has primarily an oil separator 41 d for separating the refrigerant from the refrigeration oil accompanying the refrigerant discharged from the high-stage compression element 2 d , and an oil return tube 41 e which is connected to the oil separator 41 d and which returns the refrigeration oil separated from the refrigerant to the intermediate refrigerant tube 22 , which is on the intake side of the high-stage compression element 2 d .
  • the oil return tube 41 e is provided with a depressurization mechanism 41 f for depressurizing the refrigeration oil flowing through the oil return tube 41 e .
  • a capillary tube is used as the depressurization mechanism 41 f in the present embodiment.
  • the non-return mechanism 42 d is a mechanism for allowing the flow of refrigerant from the discharge side of the high-stage compression element 2 d to the heat source-side heat exchanger 4 and blocking the flow of refrigerant from the heat source-side heat exchanger 4 to the discharge side of the high-stage compression element 2 d , and a non-return valve is used in the present embodiment.
  • the two compression elements 2 c , 2 d are connected to each other in series and are linked to their respective individual drive shafts 21 c , 21 f , and the two compression elements 2 c , 2 d have two-stage compression structures in which they are rotatably driven individually by respective compressor drive motors 21 b , 21 e.
  • the intercooler 7 warms the water flowing through the intermediate water tubes 904 , 905 by the heat of the refrigerant flowing through the intermediate refrigerant tube 22 , and cools the refrigerant flowing through the intermediate refrigerant tube 22 by the water flowing through the intermediate water tubes 904 , 905 .
  • the degree of superheating of the refrigerant drawn into the high-stage compression element 2 d can thereby be reduced, and the temperature of the refrigerant discharged from the high-stage compression element 2 d is prevented from increasing excessively.
  • the refrigeration capacity can also be improved because the density of the refrigerant drawn into the high-stage compression element 2 d is increased by lowering the temperature of the refrigerant flowing through the intermediate refrigerant tube 22 in this manner.
  • the heat source-side heat exchanger 4 is a heat exchanger which has air as a heat source and functions as a radiator of refrigerant.
  • the heat source-side heat exchanger 4 is connected at one end to the discharge side of the high-stage compression element 2 d via the connection tube 71 and the non-return mechanism 42 , and is connected at the other end to the expansion mechanism 5 via the connection tube 72 .
  • the water flowing through the heat source water tubes 902 , 903 is heated by the refrigerant heading from the connection tube 71 to the connection tube 72 , and the refrigerant heading from the connection tube 71 to the connection tube 72 is cooled by the water flowing through the heat source water tubes 902 , 903 .
  • the expansion mechanism 5 is connected at one end to the connection tube 72 , and is connected at the other end to the usage-side heat exchanger 6 via the connection tube 76 .
  • the expansion mechanism 5 is a mechanism for depressurizing the refrigerant, and an electric expansion valve is used in the present embodiment.
  • the expansion mechanism 5 depressurizes the high-pressure refrigerant cooled in the heat source-side heat exchanger 4 nearly to the saturation pressure of the refrigerant before feeding the refrigerant to the usage-side heat exchanger 6 .
  • the usage-side heat exchanger 6 is a heat exchanger which functions as an evaporator of refrigerant.
  • the usage-side heat exchanger 6 is connected at one end to the expansion mechanism 5 via the connection tube 76 , and is connected at the other end to the intake side of the low-stage compression element 2 c via the intake tube 2 a .
  • the usage-side heat exchanger 6 is supplied with water and/or air as a heating source for performing heat exchange with the refrigerant flowing through the usage-side heat exchanger 6 .
  • the usage-side temperature sensor 6 T detects the temperature of the water and/or air supplied as a heating source in order to perform heat exchange with the refrigerant flowing through the usage-side heat exchanger 6 described above.
  • the water heater 1 is provided with a control unit 99 which perceives the temperature sensed by the usage-side temperature sensor 6 T, and which controls the actions of the low-stage compression element 2 c , the high-stage compression element 2 d , the expansion mechanism 5 , the pump 921 , and other components constituting the water heater 1 .
  • FIG. 2 is a pressure-enthalpy graph representing the refrigeration cycle
  • FIG. 3 is a temperature-entropy graph representing the refrigeration cycle.
  • the states of the refrigerant at the points indicated by A, B, C, D, K, and M in the refrigerant circuit 10 of FIG. 1 correspond to the same points in the pressure-enthalpy graph shown in FIG. 2 and the temperature-entropy graph shown in FIG. 3 .
  • the refrigerant flowing through the intermediate refrigerant tube 22 is cooled by the refrigerant flowing through the intermediate water tubes 904 , 905 of the water circuit 910 when passing through the intercooler 7 (refer to point B point C in FIGS. 2 and 3 ).
  • control unit 99 performs target capacity output control as follows.
  • control unit 99 receives an input value of output water temperature and an input value of a required output water quantity from the user via a controller or the like (not shown).
  • the control unit 99 controls the flow rate of water by controlling the rotational speed of the motor 921 m of the pump 921 on the basis of the input value of the required output water quantity.
  • the control unit 99 then perceives the water temperature detected by the water temperature sensor 910 T and the flow rate controlled by the motor 921 m of the pump 921 , and calculates emitted heat quantity required for the refrigerant supplied to the heat source-side heat exchanger 4 . Based on this required emitted heat quantity, the control unit 99 then calculates the target discharge pressure for the pressure of the refrigerant discharged from the high-stage compression element 2 d.
  • a case of a target discharge pressure being the target value in the target capacity output control is herein described as an example, but instead of the target discharge pressure, target values of the discharged refrigerant pressure and the discharged refrigerant temperature may be established so that the value obtained by multiplying the discharged refrigerant temperature by the discharged refrigerant pressure is within a predetermined range. This is because in cases in which the load has changed, the density of the discharged refrigerant decreases when the degree of superheating of the drawn-in refrigerant is high; therefore, even if it is possible to maintain the temperature of the refrigerant discharged from the high-stage compression element 2 d , it becomes impossible to guarantee the emitted heat quantity required in the heat source-side heat exchanger 4 .
  • the control unit 99 establishes a target evaporation temperature and a target evaporation pressure (a pressure equal to or less than the critical pressure). This setting of the target evaporation pressure is performed every time the temperature sensed by the usage-side temperature sensor 6 T changes.
  • the control unit 99 Based on this target evaporation temperature value, the control unit 99 performs superheat degree control so that the degree of superheating of the refrigerant drawn in by the low-stage compression element 2 c is a target value x (degree of superheating target value) of 5° C. or less.
  • the control unit 99 then controls the low-stage compression element 2 c so as to raise the refrigerant pressure and refrigerant temperature while causing isentropic change for maintaining the entropy value at the degree of superheating established in this manner, and refrigerant is discharged to the intermediate refrigerant tube 22 .
  • the intercooler 7 provided to the intermediate refrigerant tube 22 heat exchange is performed while the water and refrigerant flow against each other, the refrigerant is cooled by the water flowing through the intermediate water tubes 904 , 905 , and the water flowing through the intermediate water tubes 904 , 905 is heated.
  • the refrigerant flowing through the intermediate refrigerant tube 22 is cooled in the intercooler 7 and drawn into the high-stage compression element 2 d .
  • the high-stage compression element 2 d refrigerant is discharged at a pressure exceeding the critical pressure due to the operating capacity being controlled by controlling the rotational speed. Having been increased in temperature by being further compressed by the high-stage compression element 2 d in this manner, the refrigerant is fed to the heat source-side heat exchanger 4 .
  • heat exchange is performed while the high-temperature, high-pressure refrigerant in a supercritical state and the water flow against each other, and water having the target output water temperature is obtained.
  • the refrigerant temperature continuously decreases while the pressure is being changed such that the refrigerant is maintained at the target discharge pressure as an isobaric change.
  • the refrigerant flowing through the heat source-side heat exchanger 4 has a temperature equal to or greater than the temperature of the water supplied as a heating target through the heat source water tubes 902 , 903 , and the refrigerant is cooled to a value y near the water supplied as a heating target.
  • the value of y changes due to the supplied quantity being controlled by the motor 921 m of the pump 921 .
  • the refrigerant cooled in the heat source-side heat exchanger 4 in this manner is depressurized to the target evaporation pressure (a pressure equal to or less than the critical pressure) by the expansion mechanism 5 , and the refrigerant flows into the usage-side heat exchanger 6 .
  • the refrigerant flowing through the usage-side heat exchanger 6 absorbs heat from the water and/or air supplied as a heating source, whereby the dryness of the refrigerant is progressively improved while isobaric-isothermal change is conducted such that the target evaporation temperature and the target evaporation pressure are maintained.
  • the control unit 99 controls the quantity supplied by a heating source supply device (not shown) (a pump in the case of water, and a fan or the like in the case of air) so that the degree of superheating reaches the degree of superheating target value.
  • the control unit 99 calculates the value of x and the value of y so that the coefficient of performance (COP) in the refrigeration cycle will be as high as possible, and performs the target capacity output control described above.
  • the control unit 99 performs the calculation on the basis of the properties (a Mollier diagram or the like) of carbon dioxide as the active refrigerant.
  • a condition may be established at which the coefficient of performance can be satisfactorily maintained to a certain extent, and if this condition is met, the value of x and the value of y may be determined such that the compression work will be a smaller value.
  • Another option is to use a precondition that the compression work is suppressed to a predetermined value or lower, and to determine the value of x and the value of y which yield the best coefficient of performance while this precondition is being met.
  • the relationship between heat radiation quantity control guaranteed in the heat source-side heat exchanger 4 and/or the intermediate refrigerant tube 22 of the refrigerant circuit 10 and flow rate control of the pump 921 , which are performed by the control unit 99 , includes a large adjustment of the flow rate of the pump 921 of the water circuit 910 or another action when the refrigerant circuit 10 is controlled so that the heat radiation quantity in the heat source-side heat exchanger 4 and/or the intermediate refrigerant tube 22 increases, for example.
  • This relationship between heat radiation quantity control and flow rate control also includes control for minimizing the flow rate of the pump 921 of the water circuit 910 when, conversely, a large heat radiation quantity cannot be achieved in the heat source-side heat exchanger 4 and/or the intermediate refrigerant tube 22 .
  • the control unit 99 gives less priority to controlling the output water quantity than to the output water temperature while achieving the output water temperature requested by the user.
  • the water that has branched off in the branching point W and that flows through the intermediate water tubes 904 , 905 is water that has not been heated in the heat source-side heat exchanger 4 , and this water has the same temperature as the temperature of the refrigerant flowing through the water inlet tube 901 .
  • degree of superheating control is performed so that the degree of superheating reaches a target value x of 5° C. or less, and the compression ratio in the low-stage compression element 2 c and the compression ratio in the high-stage compression element 2 d are adjusted so as to be equal.
  • the temperature of the refrigerant flowing through the heat source-side heat exchanger 4 is inevitably higher than the temperature of the refrigerant flowing through the intercooler 7 .
  • the temperature of the refrigerant flowing through the intercooler 7 and the temperature of the refrigerant flowing through the heat source-side heat exchanger 4 are different and the temperature of the refrigerant flowing through the intercooler 7 is the lower of the two, in order to achieve the refrigeration cycle effect by way of the intercooler 7 , i.e., effect of cooling the refrigerant drawn into the high-stage compression element 2 d , the refrigeration cycle is limited to cases in which the temperature of the water flowing through the intermediate water tubes 904 , 905 is lower than the temperature of the refrigerant flowing through the intermediate refrigerant tube 22 .
  • the water flowing into the intercooler 7 can be made to flow into the intercooler 7 via the intermediate water tube 904 without taking heat from the exterior after the water has branched off at the branching point W.
  • the effect of cooling the refrigerant drawn into the high-stage compression element 2 d can be achieved merely due to the temperature of the water flowing through the water inlet tube 901 at least being lower than the temperature of the refrigerant flowing through the intermediate refrigerant tube 22 , and it is possible to prevent this effect from lessening or to prevent the reverse effect from occurring due to the water flowing through the intermediate water tubes 904 , 905 being heated before flowing into the intercooler 7 .
  • control by the control unit 99 in the embodiment described above the following type of control can be performed, for example.
  • the design pressure resistance of the low-stage compression element 2 c and the high-stage compression element 2 d is 12 MPa, and the discharged refrigerant pressure must be maintained at or below this design pressure resistance.
  • the target discharge pressure and target discharge temperature are established so as to achieve a refrigerant pressure and refrigerant temperature which are equal to or less than the design pressure described above and which can guarantee a heat radiation quantity of the refrigerant supplied to the heat source-side heat exchanger 4 .
  • the target state of the discharged refrigerant thereby converges at one point in a Mollier diagram of the refrigeration cycle which uses carbon dioxide as the active refrigerant.
  • the target evaporation pressure of the refrigeration cycle is established according to the temperature sensed by the usage-side temperature sensor 6 T.
  • the target intermediate pressure flowing through the intermediate refrigerant tube 22 is established according to the above-described relationship between the target discharge pressure and the evaporation pressure.
  • the degree of superheating of the refrigerant drawn into the low-stage compression element 2 c is set at 5° C.
  • the discharged refrigerant temperature and pressure are established by causing isentropic change in the low-stage compression element 2 c .
  • isentropic change takes place in the high-stage compression element 2 d so that the target discharge pressure and target discharge temperature can be achieved, the temperature of the refrigerant drawn into the high-stage compression element 2 d is established.
  • control unit 99 may control the flow rate of the pump 921 on the basis of the value detected by the water temperature sensor 910 T so that this cold energy quantity can be supplied.
  • the degree of superheating is not limited to 5° C., and can be selected within a range of 0 to 5° C.
  • the temperature of the refrigerant flowing into the expansion mechanism 5 is also adjustable, and the value of x and the value of y may be established so as to yield the best coefficient of performance of the refrigeration cycle while these values are being adjusted.
  • a refrigerant circuit 10 A may be used which has a discharged refrigerant temperature sensor 2 T for sensing the temperature of the refrigerant discharged from the high-stage compression element 2 d.
  • control unit 99 may therefore perform control for reducing the flow rate of the pump 921 while reducing the discharged refrigerant temperature.
  • the diameters of the intermediate water tubes 904 , 905 are designed to be smaller than the diameters of the heat source water tubes 902 , 903 .
  • the present invention is not limited to this example, and another option is to use a refrigerant circuit 10 B provided with a flow rate ratio adjustment mechanism 911 capable of adjusting the ratio between the quantity of water flowing through the intermediate water tubes 904 , 905 and the quantity of water flowing through the heat source water tubes 902 , 903 , as shown in FIG. 5 , for example.
  • the flow rate ratio adjustment mechanism 911 can be provided at an intermediate point in the intermediate water tubes 904 , 905 .
  • the flow rate ratio can thereby be adjusted even if the diameters of the intermediate water tubes 904 , 905 and the diameters of the heat source water tubes 902 , 903 are the same.
  • control unit 99 may control the flow rate ratio so as to achieve equality between the ratio of the heating amount in the heat source-side heat exchanger 4 and the heating amount in the intercooler 7 as obtained from the Mollier diagram, and the ratio of the quantity of water flowing through the heat source water tubes 902 , 903 and the quantity of water flowing through the intermediate water tubes 904 , 905 , for example.
  • the heating amount in the intercooler 7 in this case can be perceived according to an intermediate specific enthalpy (point B ⁇ point C in the Mollier diagram) obtained by subtracting the specific enthalpy of the refrigerant discharged from the low-stage compression element 2 c from the specific enthalpy of the refrigerant drawn into the high-stage compression element 2 d .
  • the heating amount in the heat source-side heat exchanger 4 can be perceived according to a heat source specific enthalpy (point D ⁇ point K in the Mollier diagram) obtained by subtracting the specific enthalpy of the refrigerant discharged from the high-stage compression element 2 d from the specific enthalpy of the refrigerant in the outlet of the heat source-side heat exchanger 4 .
  • control unit 99 performs a control so that the ratio of the quantity of water flowing through the heat source water tubes 902 , 903 and the quantity of water flowing through the intermediate water tubes 904 , 905 is equal to the ratio of the heat source specific enthalpy and the intermediate specific enthalpy.
  • the control unit 99 may perform feedback control in accordance with predetermined time intervals (or a predetermined degree of ratio deviation) so as to adapt to the ratio between the heat source specific enthalpy and the intermediate specific enthalpy at the point in time of the change.
  • the control unit 99 may control the ratio between the quantity of water flowing through the heat source water tubes 902 , 903 and the quantity of water flowing through the intermediate water tubes 904 , 905 so that the outlet temperature of the heat source-side heat exchanger 4 in the heat source water tube 903 and the outlet temperature of the intercooler 7 in the intermediate water tube 905 are substantially equal, for example.
  • the control unit 99 may cause the outlet temperatures to coincide through a predetermined feedback control in this case as well.
  • control unit 99 it is possible for the control unit 99 to also make adjustments for increasing the quantity of water flowing through the heat source water tubes 902 , 903 while maintaining a constant quantity of water flowing through the intermediate water tubes 904 , 905 , by increasing the rotational speed of the motor of the pump 921 to increase the flow rate and by narrowing the opening degree of the flow rate ratio adjustment mechanism 911 .
  • the control unit 99 can thereby perform control for bringing the coefficient of performance of the refrigeration cycle to a satisfactory value in an operation for achieving not only the user's desired output water temperature but the user's desired output water quantity as well.
  • a refrigerant circuit 10 C which is provided with a heat source refrigerant temperature sensor 4 T for detecting the temperature of the refrigerant passing through the heat source-side heat exchanger 4 , a heat source refrigerant pressure sensor 4 P for detecting the pressure of the refrigerant passing through the heat source-side heat exchanger 4 , an intermediate refrigerant temperature sensor 22 T for detecting the temperature of the refrigerant passing through the intermediate refrigerant tube 22 , an intermediate refrigerant pressure sensor 22 P for detecting the pressure of the refrigerant passing through the intermediate refrigerant tube 22 , and the flow rate ratio adjustment mechanism 911 shown in Modification 3.
  • the radiated heat quantity that can be supplied to the water from the refrigerant in the heat source-side heat exchanger 4 can be perceived according to the values sensed by the heat source refrigerant temperature sensor 4 T for detecting the temperature of the refrigerant passing through the heat source-side heat exchanger 4 and the heat source refrigerant pressure sensor 4 P for detecting the pressure of the refrigerant passing through the heat source-side heat exchanger 4
  • the heat radiation quantity that can be supplied to the water from the refrigerant in the intercooler 7 can be perceived according to the values sensed by intermediate refrigerant temperature sensor 22 T for detecting the temperature of the refrigerant passing through the intermediate refrigerant tube 22 and the intermediate refrigerant pressure sensor 22 P for detecting the pressure of the refrigerant passing through the intermediate refrigerant tube 22 .
  • control unit 99 can adjust the opening degree of the flow rate ratio adjustment mechanism 911 so as to adapt to the radiated heat quantity that can be supplied to the water from the refrigerant in the heat source-side heat exchanger 4 and the heat radiation quantity that can be supplied to the water from the refrigerant in the intercooler 7 , and the control unit 99 can perform control so as to achieve an efficient flow rate ratio for obtaining the required output water temperature.
  • the present invention is not limited to this example, and a water circuit may be used in which an on/off valve is provided to the heat source water tubes 902 , 903 and an on/off valve is also provided to the intermediate water tubes 904 , 905 , instead of the flow rate ratio adjustment mechanism 911 , for example.
  • the present invention is not limited to this example; another possibility is to use a refrigerant circuit wherein the aforementioned two-stage compression mechanisms which perform compression in two stages are provided in parallel to each other, for example.
  • a plurality of usage-side heat exchangers 6 may be disposed in parallel to each other.
  • a refrigerant circuit may be used in which expansion mechanisms are disposed immediately ahead of the respective usage-side heat exchangers so that the quantity of refrigerant supplied to the usage-side heat exchangers 6 can be controlled, and the expansion mechanisms are also disposed in parallel to each other.
  • the present invention is not limited to this example; another possibility is a refrigerant circuit 10 D which uses a compression mechanism 2 having a shared drive shaft 121 c which is a drive shaft shared by the low-stage compression element 2 c and the high-stage compression element 2 d , wherein one shared compressor drive motor 121 b is used to transmit drive force to the shared drive shaft 121 c , as shown in FIG. 7 , for example.
  • This compression mechanism 2 has a hermetically sealed structure in which the compressor drive motor 121 b , the shared drive shaft 121 c , and the compression elements 2 c , 2 d are housed within a casing 21 a .
  • the shared compressor drive motor 121 b is linked to the shared drive shaft 121 c .
  • This shared drive shaft 121 c is linked to the two compression elements 2 c , 2 d . That is, the compression mechanism has a so-called single-shaft two-stage compression structure in which the two compression elements 2 c , 2 d are linked to a single shared drive shaft 121 c , and the two compression elements 2 c , 2 d are both rotatably driven by the shared compressor drive motor 121 b .
  • the compression elements 2 c , 2 d are rotary-type, scroll-type, or another type of positive displacement compression elements.
  • the low-stage compression element 2 c draws refrigerant in from an intake tube 2 a , compresses the drawn-in refrigerant, and discharges the refrigerant toward the intermediate refrigerant tube 22 .
  • the intermediate refrigerant tube 22 connects the discharge side of the low-stage compression element 2 c and the intake side of the high-stage compression element 2 d via the intercooler 7 .
  • the high-stage compression element 2 d further compresses the refrigerant drawn in via the intermediate refrigerant tube 22 and then discharges the refrigerant to the discharge tube 2 b .
  • the discharge tube 2 b is a refrigerant tube for feeding the refrigerant discharged from the compression mechanism 2 to the heat source-side heat exchanger 4 , and the discharge tube 2 b is provided with an oil separation mechanism 41 and a non-return mechanism 42 .
  • the oil separation mechanism 41 is a mechanism for separating the refrigerant from refrigeration oil which accompanies the refrigerant discharged from the compression mechanism 2 and returning the refrigeration oil to the intake side of the compression mechanism 2 , and the oil separation mechanism 41 has primarily an oil separator 41 a for separating the refrigerant from the refrigeration oil accompanying the refrigerant discharged from the compression mechanism 2 , and an oil return tube 41 b which is connected to the oil separator 41 a and which returns the refrigeration oil separated from the refrigerant to the intake tube 2 a of the compression mechanism 2 .
  • the oil return tube 41 b is provided with a depressurization mechanism 41 c for depressurizing the refrigeration oil flowing through the oil return tube 41 b .
  • a capillary tube is used as the depressurization mechanism 41 c .
  • the non-return mechanism 42 is a mechanism for allowing the flow of refrigerant from the discharge side of the compression mechanism 2 to the heat source-side heat exchanger 4 and blocking the flow of refrigerant from the heat source-side heat exchanger 4 to the discharge side of the compression mechanism 2 , and a non-return valve is used.
  • the compression mechanism 2 has two compression elements 2 c , 2 d , and the compression mechanism 2 is configured so that refrigerant discharged from the first-stage compression element of these compression elements 2 c , 2 d is sequentially compressed by the second-stage compression element.
  • the control unit 99 drives the low-stage compression element 2 c and the high-stage compression element 2 d while causing their centrifugal forces to cancel each other out to suppress vibrations and/or fluctuations in torque load, and the control unit 99 can perform control so that the operating capacity of the low-stage compression element 2 c and the operating capacity of the high-stage compression element 2 d are balanced, and the compression ratios are equal in the low-stage and high-stage elements.
  • FIG. 8 is a schematic structural diagram of a water heater 201 as a refrigeration apparatus according to the second embodiment of the present invention.
  • the water circuit 910 is the water circuit of the embodiment described above, but further having the flow rate ratio adjustment mechanism 911 disposed at an intermediate point in the intermediate water tubes 904 , 905 .
  • the opening degree of this flow rate ratio adjustment mechanism 911 is controlled by the control unit 99 , and the ratio between the quantity of water flowing through the heat source water tubes 902 , 903 and the quantity of water flowing through the intermediate water tubes 904 , 905 can be adjusted.
  • the refrigerant circuit 210 is the refrigerant circuit of the embodiment described above, but further having a liquid-gas heat exchanger 8 , a liquid-gas three-way valve 8 C, a liquid-gas bypass tube 8 B, and connecting tubes 71 , 72 , 73 , 74 , 75 , 76 , 77 , and the like connecting these components together.
  • the liquid-gas heat exchanger 8 has a liquid-side liquid-gas heat exchanger 8 L through which passes the refrigerant flowing from the connecting tube 73 to the connecting tube 74 , and a gas-side liquid-gas heat exchanger 8 G through which passes the refrigerant flowing from the connecting tube 77 to the intake tube 2 a .
  • the liquid-gas heat exchanger 8 performs heat exchange between the refrigerant flowing through the liquid-side liquid-gas heat exchanger 8 L and the refrigerant flowing through the gas-side liquid-gas heat exchanger 8 G.
  • the refrigerant passing through the liquid-side liquid-gas heat exchanger 8 L is not limited to a liquid state, and may be refrigerant in a supercritical state, for example.
  • the refrigerant flowing through the gas-side liquid-gas heat exchanger 8 G limited to refrigerant in a gas state, and refrigerant as moisture may flow through, for example.
  • the liquid-gas bypass tube 8 B connects one switching port of the liquid-gas three-way valve 8 C connected to the connecting tube 73 , which is on the upstream side of the liquid-side liquid-gas heat exchanger 8 L, and an end of the connecting tube 74 extending downstream of the liquid-side liquid-gas heat exchanger 8 L.
  • the liquid-gas three-way valve 8 C can switch between a liquid-gas usage connection state in which the connection tube 72 extending from the heat source-side heat exchanger 4 is connected to the connecting tube 73 extending from the liquid-side liquid-gas heat exchanger 8 L, and a liquid-gas non-usage connection state in which the connection tube 72 extending from the heat source-side heat exchanger 4 is not connected to the connecting tube 73 extending from the liquid-side liquid-gas heat exchanger 8 L but is connected to the liquid-gas bypass tube 8 B.
  • FIG. 9 is a pressure-enthalpy graph representing the refrigeration cycle
  • FIG. 10 is a temperature-entropy graph representing the refrigeration cycle.
  • connection state of the liquid-gas three-way valve 8 C is switchably controlled by the control unit 99 so that heat exchange is performed in the liquid-gas heat exchanger 8 between the refrigerant passing through the liquid-side liquid-gas heat exchanger 8 L and the refrigerant passing through the gas-side liquid-gas heat exchanger 8 G.
  • the refrigerant drawn in from the intake tube 2 a of the low-stage compression element 2 c (refer to point A in FIGS. 9 and 10 ) is compressed by the low-stage compression element 2 c (refer to point B in FIGS. 9 and 10 ), and the refrigerant flowing through the intermediate refrigerant tube 22 is cooled in the intercooler 7 by the water flowing through the intermediate water tubes 904 , 905 (refer to point C in FIGS. 9 and 10 ).
  • the refrigerant is fed to the heat source-side heat exchanger 4 .
  • the water flowing through the heat source water tubes 902 , 903 is then heated, whereby the heat within the refrigerant itself is radiated.
  • carbon dioxide is used here as the active refrigerant and the refrigerant flows into the heat source-side heat exchanger 4 in a supercritical state, heat is radiated to the exterior by the change in sensible heat while the refrigerant pressure remains constant in the heat radiation step, and the temperature of the refrigerant itself continuously decreases (refer to point K in FIGS.
  • the refrigerant flows into the liquid-side liquid-gas heat exchanger 8 L, where heat is further radiated due to heat exchange with the low-temperature, low-pressure gas refrigerant flowing through the gas-side liquid-gas heat exchanger 8 G, and the temperature of the refrigerant itself continuously decreases further (refer to point L in FIGS. 9 and 10 ).
  • the refrigerant is depressurized by the expansion mechanism 5 (refer to point M in FIGS. 9 and 10 ), and the refrigerant flows into the usage-side heat exchanger 6 .
  • the refrigerant evaporates while the heat taken from the exterior is consumed in a change of latent heat, whereby the dryness of the refrigerant increases (refer to point P in FIGS. 9 and 10 ).
  • the refrigerant evaporates further while undergoing a change in latent heat in the gas-side liquid-gas heat exchanger 8 G due this time to the heat taken by heat exchange with the high-temperature, high-pressure refrigerant passing through the liquid-side liquid-gas heat exchanger 8 L while the pressure remains constant, and the refrigerant reaches a superheated state above the dry saturated vapor curve at this pressure.
  • This refrigerant in a superheated state is then drawn into the low-stage compression element 2 c through the intake tube 2 a (point A in FIGS. 9 and 10 ). This refrigerant circulation is repeated in the liquid-gas usage connection state.
  • control unit 99 controls the connection state of the liquid-gas three-way valve 8 C and creates a state in which the connection tube 72 and the liquid-gas bypass tube 8 B are connected, so that heat exchange is not performed in the liquid-gas heat exchanger 8 .
  • the refrigerant that has exited the heat source-side heat exchanger 4 herein flows through the liquid-gas bypass tube 8 B to be depressurized in the expansion mechanism 5 without flowing into the liquid-side liquid-gas heat exchanger 8 L (refer to point L′ in FIGS. 9 and 10 ).
  • the refrigerant is then depressurized in the expansion mechanism 5 , and the refrigerant flows into the usage-side heat exchanger 6 (refer to point M′ in FIGS. 9 and 10 ).
  • the refrigerant evaporates while the heat taken from the exterior is consumed in a latent heat change, whereby the refrigerant reaches a superheated state above the dry saturated vapor curve at this pressure.
  • This refrigerant in a superheated state is then drawn into the low-stage compression element 2 c through the intake tube 2 a (refer to point P′ in FIGS. 9 and 10 ). This refrigerant circulation is repeated in the liquid-gas non-usage connection state.
  • the control unit 99 performs the same control as the target capacity output control described in Embodiment 1 above, and also performs liquid-gas heat exchanger switching control for switching between the above-described liquid-gas usage connection state and liquid-gas non-usage connection state.
  • control unit 99 switches the connection state of the liquid-gas three-way valve 8 C in accordance with the temperature sensed by the usage-side temperature sensor 6 T.
  • the target evaporation temperature is established based on the temperature sensed by the usage-side temperature sensor 6 T, but when the temperature sensed by the usage-side temperature sensor 6 T decreases and the target evaporation temperature is set to be even lower, the discharged refrigerant temperature increases under the control condition that the target discharge pressure of the high-stage compression element 2 d does not change (under the condition that the required radiated heat quantity must be guaranteed in the heat source-side heat exchanger 4 ). The reliability of the high-stage compression element 2 d is compromised when the discharged refrigerant temperature increases too much in this manner.
  • control unit 99 herein performs a control for bringing the connection state of the liquid-gas three-way valve 8 C to the liquid-gas non-usage connection state.
  • the target evaporation temperature is established based on the temperature sensed by the usage-side temperature sensor 6 T, but when the temperature sensed by the usage-side temperature sensor 6 T increases and the target evaporation temperature is set to be even higher, the discharged refrigerant temperature decreases under the control condition that the target discharge pressure of the high-stage compression element 2 d does not change (under the condition that the required radiated heat quantity must be guaranteed in the heat source-side heat exchanger 4 ). In this case, it will sometimes not be possible to supply the heat source-side heat exchanger 4 with refrigerant having the required heat radiation quantity.
  • control unit 99 is capable of switching the connection state of the liquid-gas three-way valve 8 C to the liquid-gas usage connection state, raising the degree of superheating of the refrigerant drawn into the high-stage compression element 2 d , and guaranteeing the heat radiation quantity required in the heat source-side heat exchanger 4 .
  • the control unit 99 is capable of switching the connection state of the liquid-gas three-way valve 8 C to the liquid-gas usage connection state, raising the degree of superheating of the refrigerant drawn into the high-stage compression element 2 d , and guaranteeing the heat radiation quantity required in the heat source-side heat exchanger 4 .
  • control unit 99 is capable of guaranteeing the required heat radiation quantity and improving the coefficient of performance by switching the connection state of the liquid-gas three-way valve 8 C to the liquid-gas usage connection state, lowering the specific enthalpy of the refrigerant drawn into the expansion mechanism 5 , and improving the refrigerating capacity of the refrigeration cycle. Since the refrigerant drawn into the low-stage compression element 2 c can be guaranteed to have the appropriate degree of superheating, it is possible to prevent the risk of liquid compression occurring in the low-stage compression element 2 c.
  • control unit 99 switches the connection state of the liquid-gas three-way valve 8 C on the basis of the temperature sensed by the usage-side temperature sensor 6 T (on the basis of the established target evaporation temperature).
  • the present invention is not limited to this example; another possibility is to use a refrigerant circuit 210 A having a discharged refrigerant temperature sensor 2 T for sensing the temperature of the refrigerant discharged from the high-stage compression element 2 d , instead of the usage-side temperature sensor 6 T, as shown in FIG. 11 , for example.
  • an increase in the temperature sensed by the usage-side temperature sensor 6 T described above corresponds to a decrease in the temperature sensed by the discharged refrigerant temperature sensor 2 T
  • a decrease in the temperature sensed by the usage-side temperature sensor 6 T described above corresponds to an increase in the temperature sensed by the discharged refrigerant temperature sensor 2 T.
  • the control unit 99 will therefore bring the connection state of the liquid-gas three-way valve 8 C to the liquid-gas non-usage connection state, preventing the degree of superheating of the refrigerant drawn into the low-stage compression element 2 c from increasing.
  • the control unit 99 will bring the connection state of the liquid-gas three-way valve 8 C to the liquid-gas usage connection state and increase the degree of superheating of the refrigerant drawn into the low-stage compression element 2 c , guaranteeing a capacity.
  • the control unit 99 brings the connection state of the liquid-gas three-way valve 8 C to the liquid-gas usage connection state and lowers the specific enthalpy of the refrigerant fed to the expansion mechanism 5 to improve the refrigerating capacity of the refrigeration cycle, thereby raising the coefficient of performance.
  • connection state of the liquid-gas three-way valve 8 C is switched to switch between the liquid-gas usage connection state and the liquid-gas non-usage connection state.
  • the present invention is not limited to this example; another possibility is to cause refrigerant to flow to both the liquid-gas bypass tube 8 B and the liquid-gas heat exchanger 8 L and control the refrigerant flow rate ratio of both refrigerant passages by adjusting the switched state of the liquid-gas three-way valve 8 C, for example.
  • the present invention is not limited to this example; another possibility is to use a refrigerant circuit which has an on/off valve provided to the connecting tube 73 and an on/off valve also provided to the liquid-gas bypass tube 8 B, instead of the liquid-gas three-way valve 8 C, for example.
  • the present invention is not limited to this example; another possibility is to use a refrigerant circuit wherein the aforementioned two-stage compression mechanisms which perform compression in two stages are provided in parallel to each other, for example.
  • a plurality of usage-side heat exchangers 6 may be disposed in parallel to each other.
  • a refrigerant circuit may be used in which expansion mechanisms are disposed immediately ahead of the respective usage-side heat exchangers and the expansion mechanisms are also disposed in parallel to each other so that the quantity of refrigerant supplied to the usage-side heat exchangers 6 can be controlled.
  • the present invention is not limited to this example; another possibility is a refrigerant circuit 210 B which uses a compression mechanism 2 having a shared drive shaft 121 c which is a drive shaft shared by the low-stage compression element 2 c and the high-stage compression element 2 d , wherein one shared compressor drive motor 121 b is used to transmit drive force to the shared drive shaft 121 c , as shown in FIG. 12 , for example.
  • This compression mechanism 2 has a hermetically sealed structure in which the compressor drive motor 121 b , the shared drive shaft 121 c , and the compression elements 2 c , 2 d are housed within a casing 21 a .
  • the shared compressor drive motor 121 b is linked to the shared drive shaft 121 c .
  • This shared drive shaft 121 c is linked to the two compression elements 2 c , 2 d . That is, the compression mechanism has a so-called single-shaft two-stage compression structure in which the two compression elements 2 c , 2 d are linked to a single shared drive shaft 121 c , and the two compression elements 2 c , 2 d are both rotatably driven by the shared compressor drive motor 121 b .
  • the compression elements 2 c , 2 d are rotary-type, scroll-type, or another type of positive displacement compression elements.
  • the low-stage compression element 2 c draws refrigerant in from an intake tube 2 a , compresses the drawn-in refrigerant, and discharges the refrigerant toward the intermediate refrigerant tube 22 .
  • the intermediate refrigerant tube 22 connects the discharge side of the low-stage compression element 2 c and the intake side of the high-stage compression element 2 d via the intercooler 7 .
  • the high-stage compression element 2 d further compresses the refrigerant drawn in via the intermediate refrigerant tube 22 and then discharges the refrigerant to the discharge tube 2 b .
  • the discharge tube 2 b is a refrigerant tube for feeding the refrigerant discharged from the compression mechanism 2 to the heat source-side heat exchanger 4 , and the discharge tube 2 b is provided with an oil separation mechanism 41 and a non-return mechanism 42 .
  • the oil separation mechanism 41 is a mechanism for separating the refrigerant from refrigeration oil which accompanies the refrigerant discharged from the compression mechanism 2 and returning the refrigeration oil to the intake side of the compression mechanism 2 , and the oil separation mechanism 41 has primarily an oil separator 41 a for separating the refrigerant from the refrigeration oil accompanying the refrigerant discharged from the compression mechanism 2 , and an oil return tube 41 b which is connected to the oil separator 41 a and which returns the refrigeration oil separated from the refrigerant to the intake tube 2 a of the compression mechanism 2 .
  • the oil return tube 41 b is provided with a depressurization mechanism 41 c for depressurizing the refrigeration oil flowing through the oil return tube 41 b .
  • a capillary tube is used as the depressurization mechanism 41 c .
  • the non-return mechanism 42 is a mechanism for allowing the flow of refrigerant from the discharge side of the compression mechanism 2 to the heat source-side heat exchanger 4 and blocking the flow of refrigerant from the heat source-side heat exchanger 4 to the discharge side of the compression mechanism 2 , and a non-return valve is used.
  • the compression mechanism 2 has two compression elements 2 c , 2 d , and the compression mechanism 2 is configured so that refrigerant discharged from the first-stage compression element of these compression elements 2 c , 2 d is sequentially compressed by the second-stage compression element.
  • the control unit 99 drives the low-stage compression element 2 c and the high-stage compression element 2 d while causing their centrifugal forces to cancel each other out to suppress vibrations and/or fluctuations in torque load, and the control unit 99 can perform control so that the operating capacity of the low-stage compression element 2 c and the operating capacity of the high-stage compression element 2 d are balanced, and the compression ratios are equal in the low-stage and high-stage elements.
  • FIG. 13 is a schematic structural diagram of a water heater 301 , which is a refrigeration apparatus according to the third embodiment of the present invention.
  • the water circuit 910 is the water circuit of the embodiment described above, but further having the flow rate ratio adjustment mechanism 911 disposed at an intermediate point in the intermediate water tubes 904 , 905 .
  • the opening degree of this flow rate ratio adjustment mechanism 911 is controlled by the control unit 99 , and the ratio between the quantity of water flowing through the heat source water tubes 902 , 903 and the quantity of water flowing through the intermediate water tubes 904 , 905 can be adjusted.
  • the refrigerant circuit 310 is the refrigerant circuit of the embodiment described above, but further having an economizer circuit 9 , and connecting tubes 73 c , 74 c , etc. connecting the other components.
  • the economizer circuit 9 has a branching upstream tube 9 a branching off from a branching point X between the connection tube 72 and the connecting tube 73 c , an economizer expansion mechanism 9 e for depressurizing refrigerant, a branching midstream tube 9 b for leading the refrigerant depressurized in the economizer expansion mechanism 9 e to the economizer heat exchanger 20 , and a branching downstream tube 9 c for leading the refrigerant that has flowed out of the economizer heat exchanger 20 to a convergent point Y in the intermediate refrigerant tube 22 .
  • the connecting tube 73 c leads refrigerant through the economizer heat exchanger 20 to a connecting tube 75 c .
  • This connecting tube 75 c is connected to the expansion mechanism 5 .
  • the configuration is otherwise the same as that of the water heater 1 of the first embodiment described above.
  • FIG. 14 is a pressure-enthalpy graph representing the refrigeration cycle
  • FIG. 15 is a temperature-entropy graph representing the refrigeration cycle.
  • refrigerant is caused to flow to the economizer circuit 9 by adjusting the opening degree of the economizer expansion mechanism 9 e.
  • refrigerant that has branched off from the branching point X and flowed into the branching upstream tube 9 a is depressurized in the economizer expansion mechanism 9 e (refer to point R in FIGS. 13 , 14 , and 15 ), and the refrigerant flows into the economizer heat exchanger 20 via the branching midstream tube 9 b.
  • heat exchange takes place between the refrigerant flowing through the connecting tube 73 c and the connecting tube 75 c (refer to point X ⁇ point Q in FIGS. 13 , 14 , and 15 ), and the refrigerant flowing into the economizer heat exchanger 20 via the branching midstream tube 9 b (refer to point R ⁇ point Y in FIGS. 13 , 14 , and 15 ).
  • the refrigerant flowing through the connecting tube 73 c and the connecting tube 75 c is cooled by the refrigerant flowing through the branching midstream tube 9 b , which is being depressurized and reduced in temperature in the economizer heat exchanger 20 , and the specific enthalpy decreases (refer to point X point Q in FIGS. 13 , 14 , and 15 ).
  • the degree of supercooling of the refrigerant fed to the expansion mechanism 5 increases, whereby the refrigeration capacity of the refrigeration cycle increases and the coefficient of performance improves.
  • the refrigerant whose specific enthalpy has decreased is depressurized by passing through the expansion mechanism 5 , and the refrigerant flows into the usage-side heat exchanger 6 (refer to point Q point M in FIGS. 13 , 14 , and 15 ).
  • the refrigerant evaporates in the usage-side heat exchanger 6 , and the refrigerant is drawn into the low-stage compression element 2 c (refer to point M point A in FIGS. 13 , 14 , and 15 ).
  • the refrigerant drawn into the low-stage compression element 2 c is compressed and increased in temperature, creating a state in which refrigerant increased in pressure to an intermediate pressure flows through the intermediate refrigerant tube 22 .
  • the refrigerant flowing through the intermediate refrigerant tube 22 passes through the intercooler 7 , the refrigerant radiates heat upon heating the water flowing through the intermediate water tubes 904 , 905 , and the refrigerant temperature decreases (refer to point B ⁇ point S in FIGS. 13 , 14 , and 15 ).
  • the refrigerant flowing into the economizer heat exchanger 20 via the branching midstream tube 9 b is heated by the refrigerant flowing through the connecting tube 73 c and the connecting tube 75 c , whereby the dryness of the refrigerant improves (refer to point R ⁇ point Y in FIGS. 13 , 14 , and 15 ).
  • refrigerant that has passed through the economizer circuit 9 mixes with refrigerant that has been cooled in the intercooler 7 while flowing through the intermediate refrigerant tube 22 (refer to point S in FIGS. 13 , 14 , and 15 ) at the convergent point Y in the intermediate refrigerant tube 22 described above, the refrigerant temperature decreases while the intermediate pressure is maintained, the degree of superheating of the refrigerant discharged from the low-stage compression element 2 c is reduced, and the refrigerant is drawn into the high-stage compression element 2 d (refer to points Y, S, and C in FIGS.
  • the temperature of the refrigerant drawn into the high-stage compression element 2 d thereby decreases, and it is therefore possible to prevent the temperature of the refrigerant discharged from the high-stage compression element 2 d from increasing excessively.
  • the refrigerant density also increases due to the temperature of the refrigerant drawn into the high-stage compression element 2 d decreasing, and the quantity of refrigerant circulating through the heat source-side heat exchanger 4 is increased by the refrigerant injected via the economizer circuit 9 ; therefore, the capacity to supply refrigerant to the heat source-side heat exchanger 4 can be greatly improved.
  • the economizer expansion mechanism 9 e in the economizer circuit 9 is brought to a fully closed state.
  • a state thereby arises in which the flow of refrigerant in the branching midstream tube 9 b ceases and the economizer heat exchanger 20 does not function (refer to points Q′, M′, and D′ in FIGS. 13 , 14 , and 15 ).
  • the control unit 99 performs the same control as the target capacity output control described in Embodiment 1 described above, and performs economizer switching control for switching between the economizer usage state and the economizer non-usage state described above.
  • control unit 99 controls the opening degree of the economizer expansion mechanism 9 e in accordance with the temperature sensed by the usage-side temperature sensor 6 T.
  • the target evaporation temperature is established based on the temperature sensed by the usage-side temperature sensor 6 T, but when the temperature sensed by the usage-side temperature sensor 6 T decreases and the target evaporation temperature is set to be even lower, the discharged refrigerant temperature increases under the control condition that the target discharge pressure of the high-stage compression element 2 d does not change (under the condition that the required radiated heat quantity must be guaranteed in the heat source-side heat exchanger 4 ). The reliability of the high-stage compression element 2 d is compromised when the discharged refrigerant temperature increases too much in this manner.
  • control unit 99 herein performs a control for creating the economizer usage state, wherein the economizer heat exchanger 20 is made to function by opening the economizer expansion mechanism 9 e and causing refrigerant to flow to the economizer circuit 9 .
  • the target evaporation temperature is established based on the temperature sensed by the usage-side temperature sensor 6 T, but when the temperature sensed by the usage-side temperature sensor 6 T increases and the target evaporation temperature is set to be even higher, the discharged refrigerant temperature decreases under the control condition that the target discharge pressure of the high-stage compression element 2 d does not change (under the condition that the required radiated heat quantity must be guaranteed in the heat source-side heat exchanger 4 ). In this case, it will sometimes not be possible to supply the heat source-side heat exchanger 4 with refrigerant having the required heat radiation quantity.
  • control unit 99 is capable of creating the economizer non-usage state in which the economizer expansion mechanism 9 e is fully closed, ensuring that the degree of superheating of the refrigerant drawn in by the high-stage compression element 2 d does not decrease, and guaranteeing the heat radiation quantity required in the heat source-side heat exchanger 4 .
  • control unit 99 is capable of guaranteeing the required heat radiation quantity and improving the coefficient of performance by opening the economizer expansion mechanism 9 e to create the economizer usage state, lowering the specific enthalpy of the refrigerant drawn into the expansion mechanism 5 , and improving the refrigerating capacity of the refrigeration cycle.
  • control unit 99 switches the opening degree of the economizer expansion mechanism 9 e on the basis of the temperature sensed by the usage-side temperature sensor 6 T (on the basis of the established target evaporation temperature).
  • the present invention is not limited to this example; another possibility is to use a refrigerant circuit 310 A having a discharged refrigerant temperature sensor 2 T for sensing the temperature of the refrigerant discharged from the high-stage compression element 2 d , instead of the usage-side temperature sensor 6 T, as shown in FIG. 16 , for example.
  • an increase in the temperature sensed by the usage-side temperature sensor 6 T described above corresponds to a decrease in the temperature sensed by the discharged refrigerant temperature sensor 2 T
  • a decrease in the temperature sensed by the usage-side temperature sensor 6 T described above corresponds to an increase in the temperature sensed by the discharged refrigerant temperature sensor 2 T.
  • the control unit 99 will therefore increase the opening degree of the economizer expansion mechanism 9 e to bring about the economizer usage state, preventing the discharged refrigerant temperature of the high-stage compression element 2 d from increasing excessively by reducing the degree of superheating of the refrigerant drawn into the low-stage compression element 2 c .
  • the control unit 99 will fully close the economizer expansion mechanism 9 e to bring about the economizer non-usage state and guarantee a capacity without reducing the degree of superheating of the refrigerant drawn into the high-stage compression element 2 d .
  • the control unit 99 increases the opening degree of the economizer expansion mechanism 9 e to bring about the economizer usage state and lowers the specific enthalpy of the refrigerant fed to the expansion mechanism 5 to improve the refrigerating capacity of the refrigeration cycle, thereby raising the coefficient of performance.
  • the present invention is not limited to this example; another possibility is to control the flow rate ratio of the refrigerants flowing to the economizer circuit 9 and the connecting tubes 73 c , 75 c by adjusting the valve opening degree of the economizer expansion mechanism 9 e , for example.
  • the present invention is not limited to this example; another possibility is to use a refrigerant circuit wherein the aforementioned two-stage compression mechanisms which perform compression in two stages are provided in parallel to each other, for example.
  • a plurality of usage-side heat exchangers 6 may be disposed in parallel to each other.
  • a refrigerant circuit may be used in which expansion mechanisms are disposed immediately ahead of the respective usage-side heat exchangers and the expansion mechanisms are also disposed in parallel to each other so that the quantity of refrigerant supplied to the usage-side heat exchangers 6 can be controlled.
  • the present invention is not limited to this example; another possibility is a refrigerant circuit 310 B which uses a compression mechanism 2 having a shared drive shaft 121 c which is a drive shaft shared by the low-stage compression element 2 c and the high-stage compression element 2 d , wherein one shared compressor drive motor 121 b is used to transmit drive force to the shared drive shaft 121 c , as shown in FIG. 17 , for example.
  • This compression mechanism 2 has a hermetically sealed structure in which the compressor drive motor 121 b , the shared drive shaft 121 c , and the compression elements 2 c , 2 d are housed within a casing 21 a .
  • the shared compressor drive motor 121 b is linked to the shared drive shaft 121 c .
  • This shared drive shaft 121 c is linked to the two compression elements 2 c , 2 d . That is, the compression mechanism has a so-called single-shaft two-stage compression structure in which the two compression elements 2 c , 2 d are linked to a single shared drive shaft 121 c , and the two compression elements 2 c , 2 d are both rotatably driven by the shared compressor drive motor 121 b .
  • the compression elements 2 c , 2 d are rotary-type, scroll-type, or another type of positive displacement compression elements.
  • the low-stage compression element 2 c draws refrigerant in from an intake tube 2 a , compresses the drawn-in refrigerant, and discharges the refrigerant toward the intermediate refrigerant tube 22 .
  • the intermediate refrigerant tube 22 connects the discharge side of the low-stage compression element 2 c and the intake side of the high-stage compression element 2 d via the intercooler 7 .
  • the high-stage compression element 2 d further compresses the refrigerant drawn in via the intermediate refrigerant tube 22 and then discharges the refrigerant to the discharge tube 2 b .
  • the discharge tube 2 b is a refrigerant tube for feeding the refrigerant discharged from the compression mechanism 2 to the heat source-side heat exchanger 4 , and the discharge tube 2 b is provided with an oil separation mechanism 41 and a non-return mechanism 42 .
  • the oil separation mechanism 41 is a mechanism for separating the refrigerant from refrigeration oil which accompanies the refrigerant discharged from the compression mechanism 2 and returning the refrigeration oil to the intake side of the compression mechanism 2 , and the oil separation mechanism 41 has primarily an oil separator 41 a for separating the refrigerant from the refrigeration oil accompanying the refrigerant discharged from the compression mechanism 2 , and an oil return tube 41 b which is connected to the oil separator 41 a and which returns the refrigeration oil separated from the refrigerant to the intake tube 2 a of the compression mechanism 2 .
  • the oil return tube 41 b is provided with a depressurization mechanism 41 c for depressurizing the refrigeration oil flowing through the oil return tube 41 b .
  • a capillary tube is used as the depressurization mechanism 41 c .
  • the non-return mechanism 42 is a mechanism for allowing the flow of refrigerant from the discharge side of the compression mechanism 2 to the heat source-side heat exchanger 4 and blocking the flow of refrigerant from the heat source-side heat exchanger 4 to the discharge side of the compression mechanism 2 , and a non-return valve is used.
  • the compression mechanism 2 has the two compression elements 2 c , 2 d , and the compression mechanism 2 is configured so that refrigerant discharged from the first-stage compression element of these compression elements 2 c , 2 d is sequentially compressed by the second-stage compression element.
  • the control unit 99 drives the low-stage compression element 2 c and the high-stage compression element 2 d while causing their centrifugal forces to cancel each other out to suppress vibrations and/or fluctuations in torque load, and the control unit 99 can perform control so that the operating capacity of the low-stage compression element 2 c and the operating capacity of the high-stage compression element 2 d are balanced, and the compression ratios are equal in the low-stage and high-stage elements.
  • FIG. 18 is a schematic structural diagram of a water heater 401 , which is a refrigeration apparatus according to the fourth embodiment of the present invention.
  • the water circuit 910 is the water circuit of the embodiment described above, but further having the flow rate ratio adjustment mechanism 911 disposed at an intermediate point in the intermediate water tubes 904 , 905 .
  • the opening degree of this flow rate ratio adjustment mechanism 911 is controlled by the control unit 99 , and the ratio between the quantity of water flowing through the heat source water tubes 902 , 903 and the quantity of water flowing through the intermediate water tubes 904 , 905 can be adjusted.
  • the refrigerant circuit 410 is the refrigerant circuit of the embodiment described above, but further having the liquid-gas heat exchanger 8 , a switching three-way valve 28 C, the liquid-gas bypass tube 8 B, the economizer circuit 9 , and connecting tubes 74 g , 75 g , etc. connecting these components.
  • the liquid-gas heat exchanger 8 has a liquid-side liquid-gas heat exchanger 8 L through which passes the refrigerant flowing from the connecting tube 73 to the connecting tube 74 , and a gas-side liquid-gas heat exchanger 8 G through which passes the refrigerant flowing from the connecting tube 77 to the intake tube 2 a .
  • the liquid-gas heat exchanger 8 performs heat exchange between the refrigerant flowing through the liquid-side liquid-gas heat exchanger 8 L and the refrigerant flowing through the gas-side liquid-gas heat exchanger 8 G.
  • the refrigerant passing through the liquid-side liquid-gas heat exchanger 8 L is not limited to a liquid state, and may be refrigerant in a supercritical state, for example.
  • the refrigerant flowing through the gas-side liquid-gas heat exchanger 8 G limited to refrigerant in a gas state, and refrigerant as moisture may flow through, for example.
  • An expansion mechanism 95 e is provided at an intermediate point in the connecting tube 74 .
  • the liquid-gas bypass tube 8 B connects one switching port of the switching three-way valve 28 C connected to the connecting tube 73 , which is on the upstream side of the liquid-side liquid-gas heat exchanger 8 L, and an end of the connecting tube 74 extending downstream of the liquid-side liquid-gas heat exchanger 8 L.
  • the switching three-way valve 28 C can switch between a liquid-gas state in which the connection tube 72 extending from the heat source-side heat exchanger 4 is connected to the connecting tube 73 extending from the liquid-side liquid-gas heat exchanger 8 L, and an economizer state in which the connection tube 72 extending from the heat source-side heat exchanger 4 is not connected to the connecting tube 73 extending from the liquid-side liquid-gas heat exchanger 8 L but is connected to the liquid-gas bypass tube 8 B.
  • a dual-function non-usage state can be brought about in which neither the economizer circuit 9 nor the liquid-gas heat exchanger 8 are used.
  • the economizer circuit 9 has a branching upstream tube 9 a branching off from a branching point X between the liquid-gas bypass tube 8 B and the connecting tube 74 g , an economizer expansion mechanism 9 e for depressurizing refrigerant, a branching midstream tube 9 b for leading the refrigerant depressurized in the economizer expansion mechanism 9 e to the economizer heat exchanger 20 , and a branching downstream tube 9 c for leading the refrigerant that has flowed out of the economizer heat exchanger 20 to a convergent point Y in the intermediate refrigerant tube 22 .
  • the connecting tube 74 g leads refrigerant through the economizer heat exchanger 20 to a connecting tube 75 g .
  • This connecting tube 75 g is connected to the expansion mechanism 5 .
  • the refrigerant that has passed through the liquid-side liquid-gas heat exchanger 8 L and the refrigerant that has passed through the economizer heat exchanger 20 mix together at a convergent point L and flow into the usage-side heat exchanger 6 via the connection tube 76 .
  • the control unit 99 can switch between the economizer state, the liquid-gas state, and the dual-function non-usage stage by adjusting the connection state of the switching three-way valve 28 C and the opening degree of the economizer expansion mechanism 9 e.
  • the configuration otherwise has the same specifics as those described in the above-described water heater 1 of the first embodiment, the water heater 201 of the second embodiment, and/or the water heater 301 of the third embodiment.
  • FIG. 19 is a pressure-enthalpy graph representing the refrigeration cycle
  • FIG. 20 is a temperature-entropy graph representing the refrigeration cycle.
  • the control unit 99 switches the connection state of the switching three-way valve 28 C so that refrigerant does not flow to the connecting tube 73 but refrigerant does flow to the liquid-gas bypass tube 8 B, increases the opening degree of the economizer expansion mechanism 9 e , and performs the refrigeration cycle so that the refrigerant flows to the economizer circuit 9 .
  • the same refrigeration cycle as in the economizer usage state in Embodiment 3 described above is performed here, as shown by points A, B, C, D, K, X, R, Y, Q, L, and P in FIGS. 18 , 19 , and 20 .
  • the specific enthalpy of the refrigerant flowing through the connecting tube 75 g into the expansion mechanism 5 herein can be lowered by heat exchange in the economizer heat exchanger 20 , and the refrigerating capacity of the refrigeration cycle can be improved to bring the coefficient of performance to a satisfactory value.
  • the degree of superheating of the refrigerant drawn into the high-stage compression element 2 d can be further reduced by the refrigerant passing through the economizer circuit 9 and mixing at the convergent point Y of the intermediate refrigerant tube 22 , rather than by the intercooler 7 alone, the density of the refrigerant drawn into the compression element 2 d can be raised to improve compression efficiency, and abnormal increases in the discharged refrigerant temperature can be prevented.
  • injection into the intermediate refrigerant tube 22 via the economizer circuit 9 makes it possible to increase the quantity of refrigerant supplied to the heat source-side heat exchanger 4 and to increase the quantity of heat supplied as well.
  • the control unit 99 switches the connection state of the switching three-way valve 28 C so that refrigerant does not flow to the liquid-gas bypass tube 8 B but does flow to the connecting tube 73 , and performs a refrigeration cycle that makes the liquid-gas heat exchanger 8 function.
  • the same refrigeration cycle as in the liquid-gas usage connection state in Embodiment 2 described above is performed here, as shown by points A, B, C′, D, K, T, L′, and P′ in FIGS. 18 , 19 , and 20 .
  • the specific enthalpy of the refrigerant flowing into the expansion mechanism 95 e here can be lowered; therefore, the refrigerating capacity in the refrigeration cycle can be improved to bring the coefficient of performance to a satisfactory value, a degree of superheating can be guaranteed in the refrigerant drawn into the low-stage compression element 2 c to prevent liquid compression, and the discharge temperature can be increased to guarantee the heat quantity required in the heat source-side heat exchanger 4 .
  • the control unit 99 switches the connection state of the switching three-way valve 28 C so that refrigerant does not flow to the connecting tube 73 but does flow to the liquid-gas bypass tube 8 B, fully closes the economizer expansion mechanism 9 e , and performs the refrigeration cycle so that neither the economizer circuit 9 nor the liquid-gas heat exchanger 8 are used.
  • a simple refrigeration cycle is performed here, as shown by points A, B, C, D′′, K, X, Q′′, L′′, and P in FIGS. 18 , 19 , and 20 .
  • the temperature of the refrigerant discharged from the high-stage compression element 2 d can be increased here, it is possible to supply the required heat quantity even in cases in which the radiated heat quantity required in the heat source-side heat exchanger 4 has increased.
  • the control unit 99 performs a control for switching the above-described states such that the first priority is that the discharged refrigerant temperature be within a range of not increasing abnormally and the discharged refrigerant pressure be a pressure equal to or less than the pressure capacity of the low-stage compression element 2 c and the high-stage compression element 2 d , the second priority is that the output water temperature and output water quantity requested by the user be achieved, and the third priority is that the operating efficiency be satisfactory (that an appropriate balance can be established between improving the coefficient of performance and increasing compression efficiency).
  • control is performed such that the liquid-gas state goes into effect if the discharge temperature is within a range of not increasing abnormally, and the dual-function non-usage state goes into effect if an abnormal increase in the discharge temperature is avoided.
  • the economizer state goes into effect, the opening degree of the economizer expansion mechanism 9 e is controlled, the valve opening degree is increased within a margin whereby the heat radiation quantity required in the heat source-side heat exchanger 4 can be supplied, the coefficient of performance is brought to a satisfactory value by improving the refrigerating capacity of the refrigeration cycle, and control is performed for increasing the supplied heat quantity by increasing the quantity of refrigerant that can be supplied to the heat source-side heat exchanger 4 .
  • the heat radiation quantity herein is determined by the control unit 99 on the basis of the temperature sensed by the water temperature sensor 910 T, as well as the output water temperature and the output water quantity required by the user. Whether or not the discharge temperature has increased abnormally is determined by the control unit 99 on the basis of (the evaporation temperature established corresponding to) the temperature sensed by the usage-side temperature sensor 6 T.
  • control unit 99 performs a control for switching between the economizer state, the liquid-gas state, and the dual-function non-usage state.
  • the present invention is not limited to this example; another possibility is to allow the use of a dual-usage state in which the economizer circuit 9 is used while the liquid-gas heat exchanger 8 is used as well, for example.
  • the control unit 99 herein may control the ratio between the flow rate of refrigerant flowing through the economizer circuit 9 and the flow rate of the liquid-gas heat exchanger 8 L while refrigerant is flowing simultaneously to both the economizer circuit 9 and the liquid-gas heat exchanger 8 L, rather than simply alternately switching the connection state of the switching three-way valve 28 C, so that the operating efficiency can be made satisfactory (an appropriate balance can be established between improving the coefficient of performance and increasing compression efficiency).
  • the configuration which can adjust the ratio herein is not limited to the switching three-way valve 28 C, and an expansion mechanism may be provided immediately ahead of the liquid-gas heat exchanger 8 L to
  • the control unit 99 herein ensures that the discharged refrigerant temperature of the high-stage compression element 2 d is within a range of not increasing abnormally (under conditions such as the temperature of the refrigerant discharged from the high-stage compression element 2 d being equal to or less than a predetermined temperature) when the target evaporation temperature is established based on the temperature sensed by the usage-side temperature sensor 6 T, and also that the discharged refrigerant pressure is equal to or less than the pressure capacity of the low-stage compression element 2 c and the high-stage compression element 2 d ; and the control unit 99 calculates a heat quantity sufficient to guarantee the output water temperature and output water quantity requested by the user.
  • the control unit 99 calculates a flow rate of the liquid-gas heat exchanger 8 L needed in order to guarantee a radiated heat quantity, whereby abnormal increases in the discharged refrigerant temperature at the target evaporation temperature can be prevented, and the discharge pressure is equal to or less than a predetermined pressure corresponding to the pressure capacity of the low-stage compression element 2 c and the high-stage compression element 2 d .
  • the control unit 99 controls the flow rate ratio so that the respective compression ratios of the low-stage compression element 2 c and the high-stage compression element 2 d are within a predetermined range and the coefficient of performance is within a predetermined range, while taking into account the decrease in the refrigerating capacity resulting from the increase in specific enthalpy accompanying the decrease in the flow rate of the liquid-gas heat exchanger 8 , the increase in the refrigerating capacity resulting from the decrease in specific enthalpy accompanying the increase in the flow rate of the economizer circuit 9 , the increase in the compression ratio of the compression mechanism resulting from the high pressure increasing in order to guarantee the heat radiation quantity by increasing the flow rate of the economizer circuit 9 , and the increase in the supplied heat amount accompanying the increase in the refrigerant density supplied to the heat source-side heat exchanger
  • an intermediate pressure at which the compression ratio of the low-stage compression element 2 c and the compression ratio of the high-stage compression element 2 d are equal may be calculated as the intermediate pressure for minimizing the compression work, and the economizer expansion mechanism 9 e may be controlled so that the extent of depressurization in the economizer expansion mechanism 9 e yields this intermediate pressure (and pressures within a predetermined range from this intermediate pressure), whereupon the flow rate ratio in the switching three-way valve 28 C may be adjusted so that the coefficient of performance is satisfactory.
  • control unit 99 switches the opening degree of the switching three-way valve 28 C and/or the economizer expansion mechanism 9 e on the basis of the temperature sensed by the usage-side temperature sensor 6 T (on the basis of the established target evaporation temperature).
  • the present invention is not limited to this example; another possibility is to use a refrigerant circuit 410 A having a discharged refrigerant temperature sensor 2 T for sensing the temperature of the refrigerant discharged from the high-stage compression element 2 d , instead of the usage-side temperature sensor 6 T, as shown in FIG. 21 , for example.
  • an increase in the temperature sensed by the usage-side temperature sensor 6 T described above corresponds to a decrease in the temperature sensed by the discharged refrigerant temperature sensor 2 T
  • a decrease in the temperature sensed by the usage-side temperature sensor 6 T described above corresponds to an increase in the temperature sensed by the discharged refrigerant temperature sensor 2 T.
  • connection state of the switching three-way valve 28 C is switched to switch between the liquid-gas state, the economizer state, and the dual-function non-usage state.
  • the present invention is not limited to this example; another possibility is to use a refrigerant circuit which has an on/off valve provided to the connecting tube 73 g and an on/off valve also provided to the connecting tube 73 , instead of the switching three-way valve 28 C, for example.
  • the present invention is not limited to this example; another possibility is to use a refrigerant circuit 410 B having a dual-use expansion mechanism 405 B which can be used both in control during the economizer state and control during the liquid-gas state, as shown in FIG. 22 , for example.
  • This dual-use expansion mechanism 405 B is provided at an intermediate point in a connecting tube 76 g extending from the convergent point L to the usage-side heat exchanger 6 .
  • the number of expansion mechanisms can be reduced to fewer than that of the refrigerant circuit 410 in the fourth embodiment described above.
  • the present invention is not limited to this example; another possibility is to use a refrigerant circuit 410 C in which the branching point X which branches in the economizer circuit 9 is provided between a dual-use expansion mechanism 405 C and a convergent point V between the connecting tube 74 and the liquid-gas bypass tube 8 B which extends from the liquid-gas three-way valve 8 C for switching between the liquid-gas state and the economizer state, as shown in FIG. 23 , for example.
  • a refrigerant circuit 410 D in which the branching point X which branches in the economizer circuit 9 is provided between the liquid-gas three-way valve 8 C and the heat source-side heat exchanger 4 , as shown in FIG. 24 .
  • this refrigerant circuit 410 D the connection in the liquid-gas three-way valve 8 C is switched between leading to the connecting tube 73 and leading to the liquid-gas bypass tube 8 B.
  • the refrigerant that has passed through the liquid-gas heat exchanger 8 L then passes through the connecting tube 74 and mixes at the convergent point L with the liquid-gas bypass tube 8 B.
  • the connecting tube 76 g and a dual-use expansion mechanism 405 D are provided between this convergent point L and the usage-side heat exchanger 6 .
  • the present invention is not limited to this example; another possibility is to use a refrigerant circuit wherein the above-described two-stage compression mechanisms which perform compression in two stages are provided in parallel to each other, for example.
  • a plurality of usage-side heat exchangers 6 may be disposed in parallel to each other.
  • a refrigerant circuit may be used in which expansion mechanisms are disposed immediately ahead of the respective usage-side heat exchangers and the expansion mechanisms are also disposed in parallel to each other so that the quantity of refrigerant supplied to the usage-side heat exchangers 6 can be controlled.
  • the present invention is not limited to this example; another possibility is a refrigerant circuit 410 E which uses a compression mechanism 2 having a shared drive shaft 121 c which is a drive shaft shared by the low-stage compression element 2 c and the high-stage compression element 2 d , wherein one shared compressor drive motor 121 b is used to transmit drive force to the shared drive shaft 121 c , as shown in FIG. 25 , for example.
  • This compression mechanism 2 has a hermetically sealed structure in which the compressor drive motor 121 b , the shared drive shaft 121 c , and the compression elements 2 c , 2 d are housed within a casing 21 a .
  • the shared compressor drive motor 121 b is linked to the shared drive shaft 121 c .
  • This shared drive shaft 121 c is linked to the two compression elements 2 c , 2 d . That is, the compression mechanism has a so-called single-shaft two-stage compression structure in which the two compression elements 2 c , 2 d are linked to a single shared drive shaft 121 c , and the two compression elements 2 c , 2 d are both rotatably driven by the shared compressor drive motor 121 b .
  • the compression elements 2 c , 2 d are rotary-type, scroll-type, or another type of positive displacement compression elements.
  • the low-stage compression element 2 c draws refrigerant in from an intake tube 2 a , compresses the drawn-in refrigerant, and discharges the refrigerant toward the intermediate refrigerant tube 22 .
  • the intermediate refrigerant tube 22 connects the discharge side of the low-stage compression element 2 c and the intake side of the high-stage compression element 2 d via the intercooler 7 .
  • the high-stage compression element 2 d further compresses the refrigerant drawn in via the intermediate refrigerant tube 22 and then discharges the refrigerant to the discharge tube 2 b .
  • the discharge tube 2 b is a refrigerant tube for feeding the refrigerant discharged from the compression mechanism 2 to the heat source-side heat exchanger 4 , and the discharge tube 2 b is provided with an oil separation mechanism 41 and a non-return mechanism 42 .
  • the oil separation mechanism 41 is a mechanism for separating the refrigerant from refrigeration oil which accompanies the refrigerant discharged from the compression mechanism 2 and returning the refrigeration oil to the intake side of the compression mechanism 2 , and the oil separation mechanism 41 has primarily an oil separator 41 a for separating the refrigerant from the refrigeration oil accompanying the refrigerant discharged from the compression mechanism 2 , and an oil return tube 41 b which is connected to the oil separator 41 a and which returns the refrigeration oil separated from the refrigerant to the intake tube 2 a of the compression mechanism 2 .
  • the oil return tube 41 b is provided with a depressurization mechanism 41 c for depressurizing the refrigeration oil flowing through the oil return tube 41 b .
  • a capillary tube is used as the depressurization mechanism 41 c .
  • the non-return mechanism 42 is a mechanism for allowing the flow of refrigerant from the discharge side of the compression mechanism 2 to the heat source-side heat exchanger 4 and blocking the flow of refrigerant from the heat source-side heat exchanger 4 to the discharge side of the compression mechanism 2 , and a non-return valve is used.
  • the compression mechanism 2 has two compression elements 2 c , 2 d , and the compression mechanism 2 is configured so that refrigerant discharged from the first-stage compression element of these compression elements 2 c , 2 d is sequentially compressed by the second-stage compression element.
  • the control unit 99 drives the low-stage compression element 2 c and the high-stage compression element 2 d while causing their centrifugal forces to cancel each other out to suppress vibrations and/or fluctuations in torque load, and the control unit 99 can perform control so that the operating capacity of the low-stage compression element 2 c and the operating capacity of the high-stage compression element 2 d are balanced, and the compression ratios are equal in the low-stage and high-stage elements.
  • the present invention may be applied to a so-called chiller-type air-conditioning apparatus in which water and/or brine is used as the heating source or cooling source for performing heat exchange with the refrigerant flowing through the usage-side heat exchanger 6 , and a secondary heat exchanger is provided for performing heat exchange between indoor air and the water and/or brine that has undergone heat exchange in the usage-side heat exchanger 6 .
  • the present invention can also be applied even to a refrigeration apparatus of a type different from the aforementioned chiller-type air-conditioning apparatus, such as a cooling-only air-conditioning apparatus or the like.
  • the refrigerant that operates in a supercritical range is not limited to carbon dioxide; ethylene, ethane, nitric oxide, and the like may also be used.
  • the refrigeration apparatus of the present invention since compression efficiency can be more reliably improved in the refrigeration apparatus and the heating of the water for the hot water supply can be made more efficient, the refrigeration apparatus is particularly useful in cases in which the present invention is applied to a refrigeration apparatus which has multi-stage compression-type compression elements and which uses refrigerant that operates including the supercritical state process as the active refrigerant.

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  • Chemical & Material Sciences (AREA)
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CN102016449A (zh) 2011-04-13
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ES2869938T3 (es) 2021-10-26
CN102016449B (zh) 2013-12-25
KR101213257B1 (ko) 2012-12-18
EP2309209A4 (en) 2014-11-19
AU2009240983B2 (en) 2012-08-09
KR20110015582A (ko) 2011-02-16
JP5181813B2 (ja) 2013-04-10
JP2009270747A (ja) 2009-11-19
WO2009133868A1 (ja) 2009-11-05

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