WO2006025427A1 - 冷凍装置 - Google Patents

冷凍装置 Download PDF

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Publication number
WO2006025427A1
WO2006025427A1 PCT/JP2005/015862 JP2005015862W WO2006025427A1 WO 2006025427 A1 WO2006025427 A1 WO 2006025427A1 JP 2005015862 W JP2005015862 W JP 2005015862W WO 2006025427 A1 WO2006025427 A1 WO 2006025427A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
expander
flow path
during
Prior art date
Application number
PCT/JP2005/015862
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
Katsumi Sakitani
Michio Moriwaki
Yume Inokuchi
Yoshinari Sasaki
Original Assignee
Daikin Industries, Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to EP05776819A priority Critical patent/EP1795836A1/en
Priority to US11/661,383 priority patent/US20080060365A1/en
Priority to AU2005278426A priority patent/AU2005278426B2/en
Publication of WO2006025427A1 publication Critical patent/WO2006025427A1/ja

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
    • F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders
    • 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
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • 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
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary 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
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/14—Power generation using energy from the expansion of the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/02—Increasing the heating capacity of a reversible cycle during cold outdoor conditions

Definitions

  • the present invention relates to a refrigeration apparatus including a refrigerant circuit that performs a vapor compression refrigeration cycle, and more particularly to a refrigeration apparatus in which an expander that constitutes an expansion mechanism of the refrigerant circuit is mechanically connected to the compressor. Is.
  • a refrigeration apparatus that performs a refrigeration cycle by circulating a refrigerant in a refrigerant circuit that is a closed circuit is known and widely used as an air conditioner or the like.
  • This type of refrigeration apparatus as disclosed in Patent Document 1, for example, an apparatus in which the high pressure of the refrigeration cycle is set higher than the critical pressure of the refrigerant is known.
  • This refrigeration apparatus includes an expander constituted by a scroll type fluid machine as a refrigerant expansion mechanism. The expander and the compressor are mechanically connected by a shaft, and the power obtained by the expander is used to drive the compressor to improve the COP (coefficient of performance).
  • the mass flow rate of the refrigerant passing through the expander is always equal to the mass flow rate of the refrigerant passing through the compressor. This is because the refrigerant circuit is a closed circuit.
  • the density of the refrigerant at the inlet of the expander or compressor varies depending on the operating conditions of the refrigeration system.
  • the expander and the compressor are connected to each other, and the displacement ratio between the expander and the compressor cannot be changed. For this reason, there is a problem that if the operating conditions change, the operation of the refrigeration apparatus cannot be stably continued.
  • the refrigerant circulation amount changes during cooling operation and heating operation, so that the flow rates of the compressor and the expander do not balance.
  • the refrigeration cycle is designed to balance the flow rate between the expander and the compressor during heating operation, the amount of refrigerant circulation increases during cooling operation when the intake gas of the compressor becomes high temperature.
  • the flow rate (displacement amount) of the expander is insufficient.
  • the mass flow rate Me of the refrigerant passing through the expander is equal to the mass flow rate Mc of the refrigerant passing through the compressor.
  • the relational expression of the volume circulation volume of the refrigerant and dc the suction refrigerant density of the compressor is established.
  • the volume circulation volume (Vc, Ve) is determined by the cylinder volume of each fluid machine X the rotational speed of each fluid machine.
  • Patent Document 1 JP 2001-107881
  • Patent Document 2 JP 2001-116371 A
  • the present invention has been made in view of such problems, and an object of the present invention is to eliminate the unbalance between the flow rates of the compressor and the expander when the operating conditions change (compressor This is to balance the mass flow rate of the refrigerant passing through and the mass flow rate of the refrigerant passing through the expander) and to prevent the COP of the refrigeration system from decreasing.
  • the specific volume of the refrigerant is adjusted by adjusting the temperature of the refrigerant flowing into the expander, whereby the compressor and the expander In addition to eliminating the flow unbalance, the COP of the refrigeration system is prevented from decreasing.
  • a compressor (11), a heat source side heat exchange (21), an expansion mechanism (12), and a use side heat exchanger (22) are connected, and a vapor compression type A refrigerant circuit (10) for performing a refrigeration cycle is provided, and the expansion mechanism (12) includes an expander (12) that generates power by expansion of the refrigerant.
  • the expander (12) and the compressor (11) Presupposes a mechanically linked refrigeration system
  • the refrigeration apparatus is characterized by being provided with temperature adjusting means (23) capable of adjusting the temperature of the refrigerant flowing into the expander (12).
  • the specific volume of the refrigerant can be adjusted by adjusting the temperature of the refrigerant flowing into the expander (12) with the temperature adjusting means. Specifically, the specific volume force increases as the refrigerant is cooled, and the refrigerant flow rate to the expander increases, and the specific volume increases as the refrigerant is heated to increase the refrigerant flow rate to the expander. Less. Therefore, to the expander (12) By adjusting the temperature of the refrigerant flowing in, it becomes possible to balance the flow rates of the compressor (11) and the expander (12) even if the operating conditions change. In the present invention, the refrigerant flowing into the expander (12) does not need to be bypassed, so the power obtained by the expander (12) does not decrease.
  • a second invention is the refrigeration apparatus according to the first invention, wherein the refrigerant circuit (10) includes a heating operation in which the refrigerant flowing through the use side heat exchanger (22) dissipates heat, and the use side heat exchanger (The cooling operation in which the refrigerant flowing through 22) absorbs heat is possible, and the temperature adjusting means (23) is more effective in cooling the refrigerant flowing into the expander (12) during the cooling operation than during the heating operation. It is structured to be high and is characterized by that! /
  • the cooling performance of the temperature adjusting means (23) is higher during the cooling operation than during the heating operation, so the compressor (12) and the compressor are compressed during the heating operation.
  • the refrigeration cycle is designed so that the flow rate of the machine (11) is balanced, the flow rate of the refrigerant flowing into the expander (12) can be increased even if the refrigerant circulation rate is increased during the cooling operation. For this reason, it is possible to prevent the flow rate of the expander (12) from being insufficient during cooling operation. Therefore, the flow rates of the compressor (11) and the expander (12) can be balanced during the cooling operation and the heating operation, and the recovery power of the expander (12) is also reduced because a no-pass is unnecessary. Shina.
  • a third invention is the refrigeration apparatus of the second invention, wherein the temperature adjusting means (23) evaporates the refrigerant after passing through the heat source side heat exchange (21) serving as a radiator during cooling operation. It is characterized in that it is constituted by an internal heat exchanger (23) cooled by exchanging heat with the refrigerant before or after passing through the use side heat exchanger (22) as a heat exchanger.
  • the refrigerant after passing through the heat source side heat exchanger (21) serving as a radiator is before or after passing through the use side heat exchanger (22) serving as an evaporator.
  • the refrigerant is cooled by exchanging heat with the internal refrigerant (23). This adjusts the specific flow rate of the refrigerant flowing into the expander (12), so that the flow rates of the compressor (11) and the expander (12) are balanced during heating and cooling operations. be able to.
  • a fourth invention is the refrigeration apparatus of the third invention, wherein the internal heat exchanger (23) is passed before or after passing through the use side heat exchanger (22) serving as an evaporator during cooling operation.
  • the heat transfer performance of the refrigerant flow path (25) through which the refrigerant flows becomes higher than the heat transfer performance of the refrigerant flow path (24) through which the refrigerant flows after passing through the heat source side heat exchanger (21), which serves as a radiator.
  • a heat source that becomes an evaporator during operation Heat transfer performance of refrigerant flow path (24) through which refrigerant flows before or after passing through side heat exchanger (21) Force Refrigerant flow path through which refrigerant flows after use side heat exchanger (22) as heat radiator The heat transfer performance is lower than the heat transfer performance of (25).
  • the heat transfer coefficient of the refrigerant after passing through the radiator is higher than the heat transfer coefficient of the low-pressure refrigerant before or after passing through the evaporator.
  • the heat transfer performance of the refrigerant flow path (25) through which the refrigerant flows before or after passing through the use-side heat exchanger (22) that serves as an evaporator becomes a radiator. It must be higher than the heat transfer performance of the refrigerant flow path (24) through which the refrigerant flows after passing through the heat source side heat exchanger (21), and passes through the heat source side heat exchanger (21) that serves as an evaporator during heating operation.
  • the heat transfer performance of the refrigerant flow path (24) through which the refrigerant flows before or after passing is the heat transfer performance of the refrigerant flow path (25) through which the refrigerant flows after passing through the user-side heat exchanger (22) serving as a radiator. Therefore, the heat exchange amount during the cooling operation is larger than the heat exchange amount during the heating operation. Accordingly, during the cooling operation, the refrigerant flowing into the expander (12) is cooled more than during the heating operation. Therefore, by increasing the flow rate of the refrigerant flowing into the expander (12) during the cooling operation, the compressor It becomes possible to balance the flow rates of (11) and the expander (12) during cooling operation and heating operation.
  • the fifth invention is the refrigeration apparatus of the fourth invention, wherein the internal heat exchanger (23) is passed through the use side heat exchanger (22), which becomes an evaporator during cooling operation, before or after passing.
  • the heat transfer fins (26) are provided in the refrigerant flow path (25) through which the refrigerant flows after passing through the user-side heat exchanger (22) that serves as a radiator during heating operation. It is a feature.
  • the heat transfer fin (26) is provided in the predetermined refrigerant flow path (25) of the internal heat exchanger (23), so that the internal heat exchanger (23) during the cooling operation can The amount of heat exchange is greater than during heating operation. In this way, the specific volume or flow rate of the refrigerant flowing into the expander (12) can be adjusted, so that the flow rates of the compressor (11) and the expander (12) are balanced during the cooling operation and the heating operation. Becomes pretty.
  • a sixth invention is the refrigeration apparatus of the third invention, wherein the internal heat exchanger (23) is a refrigerant before or after passing through the use side heat exchanger (22) serving as an evaporator during the cooling operation. And the refrigerant after passing through the heat source side heat exchange ⁇ 21 (21) flowing in opposite directions and flowing through the heat source side heat exchange (21) serving as the evaporator before or after passing through Later refrigerant and release The refrigerant after passing through the use side heat exchanger (22) serving as a heater is configured to flow in the same direction.
  • the heat exchange efficiency during the cooling operation is higher than the heat exchange efficiency during the heating operation. Therefore, since the cooling performance of the refrigerant after passing through the expander (12) is higher in the cooling operation than in the heating operation, the internal heat exchanger (23) is connected to the compressor (11) and the expander (12). It is possible to balance the flow rate during cooling operation and heating operation.
  • a seventh invention is the refrigeration apparatus of the third invention, wherein the internal heat exchanger (23) is an inner channel.
  • the double pipe heat exchanger is used, and the refrigerant before and after passing through the use side heat exchanger (22) serving as an evaporator and the radiator.
  • the specific volume V of the refrigerant flowing into the expander (12) is adjusted, and the compressor (11) and the expander The flow rate of (12) can be controlled during cooling operation and heating operation.
  • An eighth invention is the refrigeration apparatus of the third invention, wherein the internal heat exchanger (23) is an inner channel.
  • a three-layer plate heat exchanger having a first outer channel (25A) and a second outer channel (25B) disposed adjacent to the outside of the inner channel (24). It is composed of ⁇ .
  • the refrigerant before and after passing through the use side heat exchanger (22) serving as an evaporator, and the radiator By exchanging heat with the refrigerant after passing through the heat source side heat exchanger (21), the specific volume of refrigerant flowing into the expander (12) is adjusted!
  • the flow rate of the expander (12) can be balanced during the cooling operation and the calorific heat operation.
  • temperature adjusting means (23) for cooling the refrigerant flowing into the expander (12) only during the cooling operation, while stopping the function during the heating operation. Is.
  • the ninth invention relates to a compressor (11), a heat source side heat exchanger (21), an expansion mechanism (12), and
  • the refrigerant circuit (10) is connected to the use side heat exchanger (22) and performs a vapor compression refrigeration cycle, and the refrigerant circuit (10) absorbs heat from the refrigerant flowing through the use side heat exchanger (22).
  • An expander (12) configured to be capable of cooling operation and a heating operation in which the refrigerant flowing through the use side heat exchanger (22) dissipates heat, and the expansion mechanism (12) generates power by expansion of the refrigerant. It is assumed that the expander (12) and the compressor (11) are mechanically coupled to each other.
  • the refrigeration apparatus includes temperature adjusting means (23) capable of adjusting the temperature of the high-pressure refrigerant flowing into the expander (12), and the temperature adjusting means (23) cools the high-pressure refrigerant. It is configured to cool only during operation, and to stop cooling the high-pressure refrigerant during heating operation! /
  • the high-pressure refrigerant flowing into the expander (12) is cooled only during the cooling operation and not cooled during the heating operation. Therefore, the refrigerant flowing into the expander (12) during the cooling operation The density de can be increased. Therefore, during the cooling operation, even when the mass flow rate Mc of the refrigerant passing through the compressor (11) becomes larger than that during the heating operation, the refrigerant sucked into the expander (12) is cooled by following this. By doing so, the mass flow rate Me of the refrigerant passing through the expander (12) can be increased, and the refrigerant mass flow rates Mc and Me of both can be balanced. In the present invention, the refrigerant flowing into the expander (12) does not have to be bypassed, so the power obtained by the expander (12) does not decrease.
  • a tenth aspect of the invention is the internal heat exchanger (23) in which in the refrigeration apparatus of the ninth aspect, the temperature adjusting means (23) is cooled by exchanging heat between the high-pressure refrigerant and the low-pressure refrigerant during cooling operation. It is characterized by being composed of! /
  • the high-pressure refrigerant is cooled by exchanging heat with the low-pressure refrigerant in the internal heat exchanger (23).
  • the suction temperature of the compressor (11) increases and the refrigerant density decreases, and at the same time, the inflow temperature of the expander (12) decreases and the refrigerant density increases. Therefore, during the cooling operation, the mass flow rate Me of the refrigerant passing through the expander (12) can be increased and balanced with the mass flow rate Mc of the refrigerant passing through the compressor (11).
  • An eleventh aspect of the invention is the refrigeration apparatus of the tenth aspect, wherein the internal heat exchanger (23) has a first flow path (27) and a second flow path (28), and the first flow Refrigerant flowing through channel (27) and second channel (28 ) Is configured to be able to exchange heat, and the internal heat exchanger (23) passes through the first flow path (27) and the second flow path (28) during the cooling operation. It is characterized in that the low-pressure refrigerant is circulated and the high-pressure refrigerant is circulated through both flow paths (24, 25) during the heating operation.
  • the high-pressure refrigerant flows through both the flow paths (24, 25) of the internal heat exchanger (23). To 12).
  • the high-pressure refrigerant flowing through the first flow path (27) exchanges heat with the low-pressure refrigerant flowing through the second flow path (28) and is cooled.
  • the mass flow rate Me of the refrigerant passing through the expander (12) can be increased and balanced with the mass flow rate Mc of the refrigerant passing through the compressor (11).
  • the twelfth invention is the refrigeration apparatus of the tenth invention, wherein the internal heat exchanger (23) has a first flow path (27) and a second flow path (28), and the first flow
  • the refrigerant flowing through the channel (27) and the refrigerant flowing through the second channel (28) are configured to be able to exchange heat, and the internal heat exchanger (23) has a high pressure in the first channel (27) during the cooling operation.
  • the refrigerant is circulated while the low-pressure refrigerant is circulated through the second flow path (28), and includes a bypass passage (45) that bypasses the internal heat exchanger (23) during the heating operation.
  • ! / Characterized by! /
  • the high-pressure refrigerant bypasses the internal heat exchanger (23), so the high-pressure refrigerant flows into the expander (12) without changing its temperature.
  • the high-pressure refrigerant flowing through the first flow path (27) is cooled by exchanging heat with the low-pressure refrigerant flowing through the second flow path (28).
  • the mass flow rate Me of the refrigerant passing through the expander (12) can be increased and balanced with the mass flow rate Mc of the refrigerant passing through the compressor (11).
  • a thirteenth invention is the refrigeration apparatus of the tenth invention, wherein the internal heat exchanger (23) has a first flow path (27) and a second flow path (28), and the first flow
  • the refrigerant flowing through the channel (27) and the refrigerant flowing through the second channel (28) are configured to be able to exchange heat, and the internal heat exchanger (23) has a high pressure in the first channel (27) during the cooling operation. While the refrigerant flows, the low-pressure refrigerant is configured to flow through the second flow path (28), and includes a bypass passage (46) that bypasses the internal heat exchanger (23) during the heating operation. ! /, Characterized by!
  • the low-pressure refrigerant bypasses the internal heat exchanger (23), so the high-pressure refrigerant flows into the expander (12) without changing its temperature.
  • the high-pressure refrigerant flowing through the first flow path (27) is cooled by exchanging heat with the low-pressure refrigerant flowing through the second flow path (28).
  • the mass flow rate Me of the refrigerant passing through the expander (12) can be increased and balanced with the mass flow rate Mc of the refrigerant passing through the compressor (11).
  • the fourteenth invention is the refrigeration apparatus of the tenth invention, wherein the internal heat exchanger (23) is configured so that the high-pressure refrigerant after passing through the heat source side heat exchanger (21) is used on the use side during cooling operation. It is configured to be cooled by exchanging heat with the low-pressure refrigerant before passing through the heat exchanger (22).
  • the high-pressure refrigerant power after passing through the heat source side heat exchanger (21) is cooled by exchanging heat with the low-pressure refrigerant before passing through the heat-using side heat exchanger (22), It flows into the expander (12) with the temperature lowered and the density increased.
  • the mass flow rate Me of the refrigerant passing through the expander (12) can be increased and balanced with the mass flow rate Mc of the refrigerant passing through the compressor (11).
  • a fifteenth aspect of the invention is the refrigeration apparatus of the tenth aspect of the invention, wherein the internal heat exchange (23) is performed when the high-pressure refrigerant after passing through the heat source side heat exchanger (21) is the use side during cooling operation. It is configured to be cooled by exchanging heat with the low-pressure refrigerant after passing through the heat exchanger (22).
  • the high-pressure refrigerant force after passing through the heat source side heat exchanger (21) is cooled by exchanging heat with the low-pressure refrigerant after passing through the heat-use side heat exchanger (22), It flows into the expander (12) with the temperature lowered and the density increased.
  • the mass flow rate Me of the refrigerant passing through the expander (12) can be increased and balanced with the mass flow rate Mc of the refrigerant passing through the compressor (11).
  • the sixteenth invention is the refrigeration apparatus of the tenth invention, wherein the internal heat exchanger (23) is configured such that the high-pressure refrigerant and the low-pressure refrigerant flow in opposite directions during cooling operation. It has been characterized by
  • the high pressure refrigerant and the low pressure refrigerant flow through the internal heat exchanger (23) in opposite directions, whereby the high pressure refrigerant is efficiently cooled. Therefore, similarly to the above, during the cooling operation, the mass flow rate Me of the refrigerant passing through the expander (12) is set. It can be increased and balanced with the mass flow rate Mc of the refrigerant passing through the compressor (11).
  • the seventeenth invention is characterized in that, in the refrigeration apparatus of the ninth invention, the refrigerant in the refrigerant circuit (10) is carbon dioxide.
  • the expander (12) Since the high pressure difference of the refrigeration cycle can be increased compared with other refrigerants by using nitric acid carbon as a refrigerant, the expander (12) The expansion power of the obtained refrigerant can be increased.
  • a gas-liquid separator having an internal heat exchange that exchanges heat between the refrigerant expanded in the expander and the refrigerant sucked into the expander is used.
  • the eighteenth aspect of the invention relates to a refrigeration cycle in which a compressor (11), a heat source side heat exchange (21), an expander (12), and a use side heat exchange (22) are connected. It is premised on a refrigeration apparatus that includes a refrigerant circuit (10) for performing the above operation and that mechanically connects the compressor (11) and the expander (12) to recover the expansion power of the expander (12).
  • the refrigeration apparatus includes a gas-liquid separator (51) that separates the refrigerant expanded by the expander (12) into a liquid refrigerant and a gas refrigerant and temporarily stores the refrigerant, and the gas-liquid separator ( 51) includes an internal heat exchange section (50) for exchanging heat between the liquid refrigerant separated by the gas-liquid separator (51) and the refrigerant sucked into the expander (12).
  • a gas-liquid separator that separates the refrigerant expanded by the expander (12) into a liquid refrigerant and a gas refrigerant and temporarily stores the refrigerant
  • the gas-liquid separator ( 51) includes an internal heat exchange section (50) for exchanging heat between the liquid refrigerant separated by the gas-liquid separator (51) and the refrigerant sucked into the expander (12).
  • the refrigerant circuit (10) is provided with the gas-liquid separator (51).
  • the gas-liquid separator (51) separates the gas-liquid two-phase refrigerant after being expanded by the expander (12) into a gas refrigerant and a liquid refrigerant.
  • the gas-liquid separator (51) is provided with an internal heat exchange section (50).
  • the internal heat exchange unit (50) exchanges heat between the refrigerant sucked into the expander (12) and the liquid refrigerant stored in the gas-liquid separator (51).
  • the internal heat exchange unit (50) The refrigerant sucked in 12) is cooled. For this reason, the suction refrigerant density de of the expander (12) can be increased. Therefore, for example, during the cooling operation, even when the mass flow rate Mc of the refrigerant passing through the compressor (11) increases, by cooling the refrigerant sucked into the expander (12) following this, The refrigerant mass flow rate Me passing through the expander (12) can be increased to balance the refrigerant mass flow rates Mc and Me.
  • heat exchange amount adjustment mechanism means that the heat exchange amount can be finely adjusted according to the operating conditions, and in addition, the heat exchange amount is substantially zero or a predetermined value. If adjustment (ONZOFF control) can be performed, it has meaning.
  • the amount of heat exchange between the refrigerant sucked into the expander (12) and the liquid refrigerant separated by the gas-liquid separator (51) depends on the operating conditions. Changed by adjustment mechanism (60). Therefore, when the refrigerant mass flow rate Me of the expander (12) becomes larger than the refrigerant mass flow rate Mc of the compressor (11) due to a change in operating conditions, the amount of heat exchange in the internal heat exchange section (50) By adjusting the refrigerant, the refrigerant mass flow rate Me of the expander (12) and the cold medium amount flow rate Mc of the compressor (11) can be made equal.
  • the twentieth invention is the refrigeration apparatus according to the nineteenth invention, wherein the gas-liquid separator (51) includes a liquid storage section (52) for storing the separated liquid refrigerant, and the liquid storage section (52). And a heat transfer pipe (50) through which the refrigerant sucked into the expander (12) flows, and the heat transfer pipe (50) and the liquid refrigerant in the liquid reservoir (52). This constitutes an internal heat exchange section for exchanging heat with the refrigerant in the heat pipe (50).
  • the gas-liquid separator (51) is provided with the heat transfer tube (50) as an internal heat exchange section.
  • the heat transfer tube (50) is arranged so as to be adjacent to the liquid reservoir (52). Therefore, the refrigerant sucked into the expander (12) is cooled by the liquid refrigerant stored on the outer surface of the heat transfer tube (50) when flowing through the heat transfer tube (50). Therefore, the suction refrigerant density de of the expander (12) can be reliably increased.
  • the twenty-first invention is a refrigerant switching mechanism for switching between a cooling operation and a heating operation by changing the circulation direction of the refrigerant in the refrigerant circuit (10). ), And the heat exchange amount adjusting mechanism (60) allows heat exchange of the cooling medium in the internal heat exchanging section (50) only during the cooling operation.
  • the refrigerant switching mechanism (31, 33) is provided in the refrigerant circuit (10).
  • the refrigerant mechanism (31, 33) switches the refrigerant circulation direction so that the use side heat exchange (22) serves as an evaporator and the use side heat exchanger (21) serves as a radiator. Operation can be switched.
  • the heat exchange amount adjusting mechanism (60) causes heat exchange of the cooling medium in the internal heat exchanging section (50) only during the cooling operation.
  • the intake refrigerant density de of the expander (12) is increased, and the expander The refrigerant mass flow rate Me in (12) and the refrigerant mass flow rate Mc in the compressor (11) can be made equal.
  • the cylinders of the expander (12) and the compressor (11) according to the density ratio between the suction refrigerant density de of the expander (12) and the suction refrigerant density dc of the compressor (11)
  • the refrigerant mass flow rate Me of the expander (12) and the refrigerant mass flow rate Mc of the compressor (11) can be made equal. Therefore, it is not necessary to perform heat exchange of the refrigerant in the internal heat exchange section (50) by the heat exchange amount adjusting mechanism (60).
  • the heat exchange amount adjusting mechanism (60) bypasses the heat transfer pipe (50) and sucks the refrigerant into the expander (12). (57), a first motor-operated valve (36) that adjusts the flow rate of refrigerant flowing through the heat transfer pipe (50), and a second motor-operated valve (37) that adjusts the coolant flow rate of the bypass pipe (57). Constructed!
  • the heat exchange amount of the refrigerant in the heat transfer tube (50) is adjusted by adjusting the opening degree of the first and second motor-operated valves (36, 37). Specifically, for example, when the first motor-operated valve (36) is fully opened and the second motor-operated valve (37) is fully closed, the flow rate of the refrigerant flowing through the heat transfer pipe (50) becomes maximum, and the heat transfer pipe (50) The amount of heat exchange of the refrigerant is also adjusted to the maximum.
  • the refrigerant flow rate flowing through the heat transfer pipe (50) becomes substantially zero, and the heat transfer pipe (50)
  • the heat exchange amount of the refrigerant is also zero.
  • the amount of heat exchange in the heat transfer tube (50) can be adjusted from zero to the maximum value by adjusting the opening of the first and second motor operated valves (36, 37) to a predetermined opening. . Therefore, heat exchange of the refrigerant according to the operating conditions can be performed, and the refrigerant mass flow rate Me of the expander (12) and the refrigerant mass flow rate Mc of the compressor (11) can be made equal.
  • the heat exchange amount adjusting mechanism (60) includes a four-way switching valve (32).
  • the refrigerant flow is changed by switching the four-way switching valve (32) as the heat exchange amount adjusting mechanism (60). For this reason, for example during cooling operation, the heat transfer tube (50) While switching the four-way selector valve (32) so that the refrigerant flows, the four-way selector valve (32) is switched so that the refrigerant does not flow through the heat transfer pipe (50) during the heating operation.
  • the refrigerant mass flow rate Me of the tension machine (12) and the refrigerant mass flow rate Mc of the compressor (11) can be made equal.
  • the heat exchange amount adjusting mechanism (60) bypasses the heat transfer pipe (50) and sucks the refrigerant into the expander (12). (57), a first electromagnetic on-off valve (34) that allows or prohibits refrigerant flow in the heat transfer pipe (50), and a second electromagnetic on-off valve that allows or prohibits refrigerant flow in the bypass pipe (57). (35).
  • the refrigerant flow in the heat transfer tube (50) is changed by opening and closing the first and second electromagnetic on-off valves (34, 35). Specifically, for example, during cooling operation, the first electromagnetic open / close valve (34) is opened and the second electromagnetic open / close valve (35) is closed, so that the refrigerant flows through the heat transfer tube (50). Then, heat exchange of the refrigerant can be performed by the heat transfer tube (50). On the other hand, for example, during heating operation, the first electromagnetic on-off valve (34) is closed and the second electromagnetic on-off valve (35) is opened, thereby allowing the refrigerant to flow through the bypass pipe (57), It is possible to prevent the coolant from flowing through the heat transfer tube (50).
  • the refrigerant mass flow rate Me of the expander (12) and the refrigerant mass flow rate Mc of the compressor (11) can be made equal.
  • the heat exchange amount adjusting mechanism (60) is configured by a combination of a pipe and a check valve (81, 82, 83, 84). It is what.
  • a predetermined piping path as the heat exchange amount adjusting mechanism (60) and a check valve (81, 82, 83, 84) are provided.
  • the refrigerant flows through the heat transfer pipe (50) during the cooling operation, and the check valve (81, 82, 83, 84) and the piping path so that the refrigerant does not flow through the heat transfer pipe (50) during the heating operation.
  • the refrigerant mass flow rate Me of the expander (12) and the refrigerant mass flow rate Mc of the compressor (11) can be made equal.
  • the refrigerant circuit (10) includes a first injection for sending the gas refrigerant of the gas-liquid separator (51) to the suction side of the compressor (11).
  • the gas refrigerant separated by the gas-liquid separator (51) can be sent to the suction side of the compressor (11) via the first indication pipe (55). Therefore, so-called gas injection can be performed as necessary, and the amount of gas injection can be adjusted by changing the opening of the gas control valve (38).
  • a twenty-seventh aspect of the invention is the refrigeration apparatus of the eighteenth aspect of the invention, wherein the refrigerant circuit (10) has a second injection for sending the liquid refrigerant in the gas-liquid separator (51) to the suction side of the compressor (11). It includes a pipe (59) and a liquid control valve (39) for adjusting the refrigerant flow rate of the second injection pipe (59).
  • the liquid refrigerant separated by the gas-liquid separator (51) can be sent to the suction side of the compressor (11) via the second injection pipe (59). Therefore, so-called liquid injection can be performed as required, and the amount of liquid injection can be adjusted by changing the opening of the liquid control valve (39).
  • a plurality of use side heat exchangers (22a, 22b, 22c) are provided in the refrigerant circuit (10).
  • this refrigeration apparatus it is possible to perform a plurality of usage-side heat exchange m ⁇ (22a, 22b, 22 C) at the same time cooling (cooling) or heating (heating).
  • the opening of the multiple flow control valves (61a, 61b, 61c) corresponding to each user-side heat exchanger (22a, 22b, 22c) can be adjusted individually.
  • the refrigerant circuit (10) is filled with carbon dioxide as a refrigerant.
  • This carbon dioxide can increase the differential pressure in the refrigeration cycle as compared with other refrigerants, so that the expansion power of the refrigerant obtained by the expander (12) can be increased.
  • the specific volume or flow rate of the refrigerant can be adjusted by providing the temperature adjusting means (23) capable of adjusting the temperature of the refrigerant flowing into the expander (12). ing. Therefore, it is possible to balance the flow rates of the compressor (11) and the expander (12) even if the operating conditions change. In the present invention, even when the flow rate of the expander (12) is insufficient, it is not necessary to bypass a part of the refrigerant, so that the power obtained by the expander (12) is not reduced. Therefore, the COP can be prevented from decreasing.
  • the temperature adjusting means (23) is configured such that the cooling performance of the refrigerant flowing into the expander (12) is higher during the cooling operation than during the heating operation. is doing. Therefore, when the refrigeration cycle is designed to balance the flow force S between the compressor (11) and the expander (12) during the heating operation, the expansion can be performed without bypassing the expander (12) during the cooling operation. Since the flow rate of the compressor (12) can be prevented from being insufficient, the flow rates of the compressor (11) and the expander (12) can be balanced during cooling operation and heating operation. Therefore, the COP can be prevented from decreasing.
  • the refrigerant circuit (10) is provided with the internal heat exchanger (23), and the refrigerant after passing through the heat source side heat exchanger (21) serving as a radiator is provided during the cooling operation.
  • the specific volume of the refrigerant flowing into the expander (12) is adjusted by heat exchange with the refrigerant before or after passing through the use side heat exchanger (22) that becomes the evaporator, and the flow rate is adjusted.
  • the flow rates of the compressor (11) and the expander (12) can be balanced. Therefore, COP can be prevented from decreasing.
  • the heat transfer performance of (25) should be higher than the heat transfer performance of the refrigerant flow path (24) through which the refrigerant flows after passing through the heat source side heat exchanger (21) serving as a radiator.
  • the heat transfer performance of the refrigerant flow path (24) through which the refrigerant before or after passing through the heat source side heat exchanger (21) becomes the refrigerant after passing through the use side heat exchanger (22) as a radiator By making the temperature lower than the heat transfer performance of the refrigerant flow path (25) through which the refrigerant flows, the specific volume or flow rate of the refrigerant flowing into the expander (12) is adjusted as in the third aspect of the invention.
  • the flow rates of the compressor (11) and the expander (12) can be balanced. Therefore, COP can be prevented from decreasing.
  • the heat transfer fin (26) is provided in the predetermined refrigerant flow path (25) of the internal heat exchanger (23), and the internal heat exchanger (23) during the cooling operation is provided. Therefore, the specific volume of the refrigerant flowing into the expander (12) can be adjusted and the flow rate can be adjusted. Therefore, it is possible to balance the flow rates of the compressor (11) and the expander (12) during the cooling operation and the heating operation, thereby preventing the COP from decreasing.
  • the cooling performance during the cooling operation is greater than that during the heating operation. Therefore, the specific volume of the refrigerant flowing into the expander (12) can be adjusted and the flow rate can be adjusted. Therefore, the flow rate of the compressor (11) and the expander (12) can be balanced during the cooling operation and the heating operation, and the COP can be prevented from decreasing.
  • the double pipe heat exchanger is used to dissipate the refrigerant before and after passing through the use side heat exchanger (22) serving as an evaporator.
  • the specific volume or flow rate of the refrigerant flowing into the expander (12) can be adjusted by exchanging heat with the refrigerant after passing through the heat source side heat exchanger (21) serving as a vessel. Therefore, the flow rates of the compressor (11) and the expander (12) can be balanced during the cooling operation and the heating operation.
  • the three-layer plate heat exchanger is used to pass the refrigerant before or after passing through the use side heat exchanger (22) serving as an evaporator.
  • the specific volume or flow rate of the refrigerant flowing into the expander (12) can be adjusted by exchanging heat with the refrigerant after passing through the heat source side heat exchanger (21) serving as a radiator. Therefore, the flow rates of the compressor (11) and the expander (12) can be balanced during the cooling operation and the heating operation.
  • the high-pressure refrigerant flowing into the expander (12) is cooled only during the cooling operation by the temperature adjusting means (23), while the high-pressure refrigerant is cooled during the heating operation. Therefore, the refrigerant density de flowing into the expander (12) can be increased during the cooling operation. Therefore, during the cooling operation, even when the mass flow rate Mc of the refrigerant passing through the compressor (11) becomes larger than that during the heating operation, the refrigerant sucked into the expander (12) is cooled by following this.
  • the mass flow rate Me of the refrigerant passing through the expander (12) can be increased and the mass flow rate Mc, Me of both refrigerants can be balanced, so that both the cooling operation and the heating operation are highly efficient.
  • Expander (12) and pressure so that the obtained operating state
  • the compressor (11) can be designed. In the present invention, the refrigerant flowing into the expander (12) does not have to be bypassed, so the power obtained by the expander (12) does not decrease!
  • the internal heat exchange (23) is used to cool the high pressure refrigerant by exchanging heat with the low pressure refrigerant during the cooling operation. For this reason, by cooling the high-pressure refrigerant flowing into the expander (12) only during the cooling operation, the mass flow rate Me of the refrigerant passing through the expander (12) is increased, and the refrigerant passes through the compressor (11). Since the mass flow rate Mc of the refrigerant can be balanced, it is possible to operate with high efficiency in both the cooling operation and the heating operation.
  • the internal heat exchanger (23) does not perform heat exchange by flowing a high-pressure refrigerant through both flow paths (24, 25) during the heating operation, and does not perform high-pressure during the cooling operation. Heat is exchanged by flowing both refrigerant and low-pressure refrigerant.
  • the high-pressure refrigerant flowing into the expander (12) is cooled only during the cooling operation, thereby increasing the mass flow rate Me of the refrigerant passing through the expander (12) and passing through the compressor (11). Since it can be balanced with the mass flow rate Mc of the refrigerant, it is possible to operate with high efficiency in both the cooling operation and the heating operation.
  • the high-pressure refrigerant bypasses the internal heat exchange (23) during the heating operation, and both the high-pressure refrigerant and the low-pressure refrigerant enter the internal heat exchanger (23) during the cooling operation. It is configured to allow heat exchange to flow.
  • the high-pressure refrigerant flowing into the expander (12) is cooled only during the cooling operation, thereby increasing the mass flow rate Me of the refrigerant passing through the expander (12) and the refrigerant passing through the compressor (11). Therefore, it is possible to operate with high efficiency in both the cooling operation and the heating operation.
  • the low-pressure refrigerant bypasses the internal heat exchange (23) during the heating operation, and both the high-pressure refrigerant and the low-pressure refrigerant enter the internal heat exchanger (23) during the cooling operation. It is configured to allow heat exchange to flow.
  • the high-pressure refrigerant flowing into the expander (12) is cooled only during the cooling operation, thereby increasing the mass flow rate Me of the refrigerant passing through the expander (12) and the refrigerant passing through the compressor (11). Therefore, it is possible to operate with high efficiency in both cooling operation and heating operation. Become.
  • the high-pressure refrigerant that has passed through the heat source side heat exchanger (21) is used as the use side heat exchanger (22). It is cooled by exchanging heat with the low-pressure refrigerant before passing.
  • the high-pressure refrigerant flowing into the expander (12) is cooled only during the cooling operation, thereby increasing the mass flow rate Me of the refrigerant passing through the expander (12) and passing through the compressor (11). Since the mass flow rate Mc of the refrigerant can be balanced, it is possible to operate at high efficiency during both the cooling operation and the heating operation.
  • the high-pressure refrigerant that has passed through the heat source side heat exchanger (21) is used as the use side heat exchanger (22). It is cooled by exchanging heat with the low-pressure refrigerant after passing.
  • the high-pressure refrigerant flowing into the expander (12) is cooled only during the cooling operation, thereby increasing the mass flow rate Me of the refrigerant passing through the expander (12) and passing through the compressor (11). Since the mass flow rate Mc of the refrigerant can be balanced, it is possible to operate at high efficiency during both the cooling operation and the heating operation.
  • the high-pressure refrigerant and the low-pressure refrigerant are caused to flow through the internal heat exchanger (23) in opposite directions during the cooling operation. Can be cooled. Accordingly, during the cooling operation, the mass flow rate Me of the refrigerant passing through the expander (12) can be increased and balanced with the mass flow rate Mc of the refrigerant passing through the compressor (11).
  • the differential pressure in the refrigeration cycle can be increased compared to other refrigerants. . Therefore, the recovery power of the compressor (11) can be improved, and the COP of the refrigeration apparatus can be further improved.
  • the suction refrigerant density de that is, the mass flow rate Me of the expander (12) can be increased. Therefore, in the internal heat exchange section (50), the refrigerant is heat-exchanged with a predetermined heat exchange amount, thereby compressing the refrigerant.
  • the refrigerant mass flow rates (Me and Mc) of the compressor (11) and the expander (12) can be balanced, and a desired refrigeration cycle can be performed with this refrigeration system.
  • the present invention can balance the refrigerant mass flow rate Me and Mc without bypassing a part of the refrigerant and the expander force. That is, in the refrigeration apparatus of Patent Document 2, the expansion power of the expander decreases and the COP also decreases. However, in the present invention, all the refrigerant can be introduced into the expander (12). A decrease can be avoided.
  • the liquid state refrigerant has a higher heat transfer rate than the two-phase state refrigerant or the gas state refrigerant, so the heat exchange rate in the internal heat exchanger (50) is increased. Can be improved. Therefore, the refrigerant sucked into the expander (12) can be effectively cooled, and as a result, the internal heat exchange section (50) and the gas-liquid separator (51) can be designed compactly.
  • the gas-liquid separator (51) also serves as the internal heat exchange section (50)
  • the gas-liquid separator (51) and the internal heat exchange section (50) are individually provided. Compared with the case where it is provided, the refrigeration apparatus can be made more compact.
  • the liquid refrigerant separated by the gas-liquid separator (51) can be transported to a predetermined pipe or heat exchanger. For this reason, pressure loss in the piping can be reduced compared to, for example, a case where a two-phase refrigerant flows through the piping or heat exchange. In addition, when the two-phase refrigerant flows through the pipes and the heat exchanger, the refrigerant passing sound tends to be noise, but in the present invention, this can be prevented.
  • the heat exchange amount adjusting mechanism (60) is provided so that the heat exchange amount of the internal heat exchange section (50) can be adjusted according to the operating conditions. Therefore, in this refrigeration apparatus, the refrigerant mass flow rates (Me and Mc) of the compressor (11) and the expander (12) can be balanced following the change in operating conditions.
  • the expander that circulates in the heat transfer tube (50) ( Heat exchange between the suction refrigerant of 12) and the liquid refrigerant separated by the gas-liquid separator (51) is reliably performed.
  • the expander (12) The refrigerant mass flow rate (Me and Mc) of the compressor (11) and the expander (12) can be balanced by reliably increasing the intake refrigerant density.
  • the refrigerant mass flow rate Me of the expander (12) is likely to be smaller than the refrigerant mass flow rate Mc of the compressor (11). ) To exchange heat with the cooling medium. Therefore, the refrigerant mass flow rates (Me and Mc) of the compressor (11) and the expander (12) can be reliably balanced during the cooling operation.
  • the first and second motor-operated valves (36, 37) and the bypass pipe (57) are provided as the heat exchange amount adjusting mechanism (60). Then, the heat exchange amount of the refrigerant in the heat transfer pipe (50) can be adjusted by adjusting the opening degree of the first and second motor operated valves (36, 37) to a predetermined opening degree. Therefore, the refrigerant mass flow rates (Me and Mc) of the compressor (11) and the expander (12) can be balanced with high accuracy according to the operating conditions.
  • the first motor-operated valve (36) is fully opened and the second motor-operated valve (37) is fully closed, so that the refrigerant flows through the heat transfer tube (50) only during the cooling operation. Heat exchange can be performed. Therefore, the effect of the 21st invention can be obtained.
  • the four-way switching valve (32) is provided as the heat exchange amount adjusting mechanism (60).
  • the refrigerant flow can be changed between a state in which the refrigerant flows through the heat transfer tube (50) and a state in which the refrigerant does not flow.
  • the four-way selector valve (32) By switching the four-way selector valve (32), the refrigerant can flow through the heat transfer tube (50) only during the cooling operation, and the refrigerant can be heat-exchanged. Therefore, the operational effects of the twenty-first invention can be easily obtained.
  • the first and second electromagnetic on-off valves (34, 35) and the bypass pipe (57) are provided as the heat exchange amount adjusting mechanism (60). Then, by opening the first electromagnetic on-off valve (34) and at the same time closing the second electromagnetic on-off valve (35), the refrigerant flows through the heat transfer pipe (50) only during the cooling operation, and the refrigerant Heat exchange can be performed. Therefore, the second The effect of the invention of 1 can be obtained.
  • the predetermined piping path and the check valves (81, 82, 83, 84) are provided. Therefore, the combination of these piping paths and check valves (81, 82, 83, 84) allows the refrigerant to flow through the heat transfer pipe (50) only during the cooling operation, while the refrigerant flows into the heat transfer pipe (50) during the heating operation. Can be avoided. Therefore, the twenty-first invention can be realized only by switching control of the refrigerant circulation direction by the refrigerant switching means (31).
  • the gas refrigerant separated by the gas-liquid separator (51) can be sent to the suction side of the compressor (11) to perform gas injection. Therefore, the degree of superheat of the suction refrigerant of the compressor (11) can be adjusted, and optimal refrigeration cycle control can be performed with this refrigeration apparatus.
  • the liquid refrigerant separated by the gas-liquid separator (51) can be sent to the suction side of the compressor (11) to perform liquid injection. Therefore, the same effect as in the twenty-sixth invention can be obtained. Further, by combining the gas injection of the twenty-sixth aspect of the invention and the liquid injection of the present invention, refrigeration cycle control can be performed more finely.
  • the refrigerating machine oil contained in the refrigerant that has flowed out of the expander (12) is supplied to the suction side of the compressor (11) together with the liquid refrigerant separated by the gas-liquid separator (51). Can be returned.
  • this refrigeration apparatus can be used for a so-called multi-type air conditioner or the like.
  • the flow rate of the refrigerant flowing into each user-side heat exchanger (22a, 22b, 22c) can be adjusted by each flow control valve (61a, 61b, 61c), each user-side heat exchanger (22a, 22b, 22c)
  • the cooling (cooling) capacity of each can be adjusted individually.
  • liquid refrigerant separated by the gas-liquid separator (51) can be sent to each of the use side heat exchangers (22a, 22b, 22c), for example, compared with a refrigerant in a two-phase state.
  • the flow rate can be easily adjusted in the flow rate adjusting valves (61a, 61b, 61c).
  • the pressure loss of the refrigerant in the relatively long piping can reduce the noise caused by the refrigerant passing sound.
  • the use of carbon dioxide and carbon dioxide as the refrigerant of the refrigerant circuit (10) makes it possible to increase the differential pressure of the refrigeration cycle compared to other refrigerants. . Gatsutsu
  • the recovery power of the expander (12) can be improved, and the COP of this refrigeration apparatus can be further improved.
  • FIG. 1 is a refrigerant circuit diagram of an air conditioner according to Embodiment 1 of the present invention.
  • FIG. 2 is a schematic configuration diagram of internal heat exchange.
  • FIG. 3 is a refrigerant circuit diagram of an air conditioner according to Embodiment 2.
  • FIG. 4 is a refrigerant circuit diagram of an air conditioner according to Embodiment 3.
  • FIG. 5 is a refrigerant circuit diagram of an air conditioner according to Embodiment 4.
  • FIG. 6 is a refrigerant circuit diagram of an air conditioner according to Embodiment 5.
  • FIG. 7 is a refrigerant circuit diagram of an air conditioner according to Embodiment 6.
  • FIG. 8 is a refrigerant circuit diagram of an air conditioner according to Embodiment 7.
  • FIG. 9 is a refrigerant circuit diagram of an air conditioner according to Embodiment 8.
  • FIG. 10 is a refrigerant circuit diagram of an air conditioner according to Embodiment 9.
  • FIG. 11 is a refrigerant circuit diagram of an air conditioner according to a first modification of Embodiment 9.
  • FIG. 12 is a refrigerant circuit diagram of an air conditioner according to a second modification of Embodiment 9.
  • FIG. 13 is a refrigerant circuit diagram of an air conditioner according to Embodiment 10.
  • FIG. 14 is a refrigerant circuit diagram of an air conditioner according to a first modification of Embodiment 10.
  • FIG. 15 is a refrigerant circuit diagram of an air conditioner according to a second modification of the tenth embodiment.
  • FIG. 16 is a refrigerant circuit diagram of an air conditioner according to a third modification of Embodiment 10.
  • FIG. 17 is a refrigerant circuit diagram of an air conditioner according to a fourth modification of the tenth embodiment.
  • FIG. 18 is a refrigerant circuit diagram of an air conditioner according to Embodiment 11.
  • FIG. 19 is a refrigerant circuit diagram of an air conditioner according to Embodiment 12.
  • FIG. 20 is a refrigerant circuit diagram illustrating a refrigerant flow during a cooling operation of the twelfth embodiment.
  • FIG. 21 is a refrigerant circuit diagram showing a refrigerant flow during heating operation of the twelfth embodiment.
  • FIG. 22 is a refrigerant circuit diagram of an air conditioner according to a modification of the twelfth embodiment.
  • FIG. 23 is a refrigerant circuit diagram of an air conditioner according to Embodiment 13.
  • FIG. 24 is a refrigerant circuit diagram showing a refrigerant flow during a cooling operation of the thirteenth embodiment.
  • FIG. 25 is a refrigerant circuit diagram showing a refrigerant flow during heating operation of the thirteenth embodiment.
  • FIG. 26 is a refrigerant circuit diagram of an air conditioner according to a modification of the thirteenth embodiment.
  • FIG. 27 is a refrigerant circuit diagram of an air conditioner according to Embodiment 14.
  • FIG. 28 is a refrigerant circuit diagram showing the refrigerant flow during the cooling operation of the fourteenth embodiment.
  • FIG. 29 is a refrigerant circuit diagram showing a refrigerant flow during heating operation of Embodiment 14.
  • FIG. 30 is a refrigerant circuit diagram of an air conditioner according to a modification of Embodiment 14.
  • Air conditioner (refrigeration equipment)
  • Embodiment 1 relates to an air conditioner (1) constituted by a refrigeration apparatus according to the present invention.
  • the air conditioner (1) includes a refrigerant circuit (10).
  • the air conditioner (1) of Embodiment 1 is configured to circulate the refrigerant in the refrigerant circuit (10) and switch between the cooling operation (cooling operation) and the heating operation (heating operation).
  • the refrigerant circuit (10) is filled with carbon dioxide (CO 2) as a refrigerant.
  • the medium circuit (10) includes a compressor (11), an expander (12), an outdoor heat exchanger (heat source side heat exchanger) (21) An indoor heat exchanger (use side heat exchanger) (22), an internal heat exchanger (23), a first four-way switching valve (31), and a second four-way switching valve (32) are provided.
  • the compressor (11) is constituted by, for example, a rolling piston type fluid machine.
  • the compressor (11) is configured by a positive displacement fluid machine having a constant displacement volume.
  • the expander (12) is constituted by, for example, a rolling piston type fluid machine.
  • the expander (12) is constituted by a positive displacement fluid machine having a constant displacement volume.
  • the fluid machine constituting them is not limited to the rolling piston type.
  • a scroll-type positive displacement fluid machine is used as the compressor (11 ) Or expander (12).
  • the compressor (11) is mechanically coupled to the expander (12) via a motor (13).
  • the compressor (11) is rotationally driven by both power obtained by expansion of the refrigerant in the expander (12) and power obtained by energizing the motor (13).
  • the compressor (11) and the expander (12) are connected by a single drive shaft, and their rotational speeds are always equal. Therefore, the ratio of the displacement of the compressor (11) and the displacement of the expander (12) is constant.
  • the outdoor heat exchanger (21) is configured by so-called cross fin type fin 'and' tube heat exchange. Outdoor air is supplied to the outdoor heat exchanger (21) by a fan (not shown). In the outdoor heat exchanger (21), heat exchange between the supplied outdoor air and the refrigerant in the refrigerant circuit (10) is performed.
  • the indoor heat exchange (22) is constituted by a so-called cross fin type fin “and” tube heat exchange ⁇ . Room air is supplied to the indoor heat exchanger (22) by a fan (not shown). In this indoor heat exchange (22), heat is exchanged between the supplied indoor air and the refrigerant in the refrigerant circuit (10).
  • the internal heat exchange (23) has an inner flow path (24) and an outer flow path (25). Is composed of double-pipe heat exchange arranged adjacent to each other.
  • the internal heat exchanger (23) is an outdoor heat exchanger that serves as a radiator during cooling operation.
  • the refrigerant after passing through the exchanger (21) is cooled by exchanging heat with the refrigerant after passing through the indoor heat exchanger (22) serving as an evaporator.
  • the inner flow path (24) of the internal heat exchanger (23) is a flow path through which the refrigerant passes through the outdoor heat exchanger (21) serving as a radiator during cooling operation, and during heating operation, It becomes a flow path through which the refrigerant flows after passing through the outdoor heat exchanger (21) serving as an evaporator.
  • the outer channel (25) is a channel through which the refrigerant passes through the indoor heat exchanger (22) serving as an evaporator during cooling operation, and the indoor heat exchanger (22) serving as a radiator during heating operation. It becomes the flow path through which the refrigerant passes.
  • the outer flow path (25) is provided with heat transfer fins (26).
  • the internal heat exchanger (23) is provided with a refrigerant flow path (outside flow) through which the refrigerant flows after passing through the indoor heat exchanger (22) serving as an evaporator during cooling operation.
  • the heat transfer performance of the passage (25)) is higher than the heat transfer performance of the refrigerant flow path (inner flow path (24)) through which the refrigerant flows after passing through the outdoor heat exchanger (21) serving as a radiator.
  • the heat transfer performance of the refrigerant flow path (inner flow path (24)) through which the refrigerant flows after passing through the outdoor heat exchanger (21) serving as an evaporator is greater than the indoor heat exchanger (22) serving as a heat sink. It is configured to be lower than the heat transfer performance of the refrigerant channel (outer channel (25)) through which the refrigerant passes. Therefore, the internal heat exchanger (23) is configured so that the amount of heat exchange during the cooling operation is larger than that during the heating operation, and the cooling performance of the refrigerant flowing into the expander (12) is improved. ing.
  • the discharge side of the compressor (11) is connected to the first port (P1) of the first four-way switching valve (31), and the first four-way switching valve (31)
  • the second port (P2) is connected to the first end of the outdoor heat exchanger (21).
  • the second end of the outdoor heat exchanger (21) is connected to the first port (P1) of the second four-way selector valve (32) via the inner flow path (24) of the internal heat exchanger (23),
  • the second port (P2) of the second four-way switching valve (32) is connected to the inflow side of the expander (12).
  • the outflow side of the expander (12) is connected to the third port (P3) of the first four-way selector valve (31), and the fourth port (P4) of the first four-way selector valve (31) is the indoor heat exchanger. It is connected to the first end of (22).
  • the second end of the indoor heat exchanger (2 2) is connected to the third port (P3) of the second four-way selector valve (32) via the outer flow path (25) of the internal heat exchanger (23),
  • the fourth port (P4) of the second four-way selector valve (32) is connected to the suction side of the compressor (11).
  • the first port (P1) communicates with the second port (P2) and the third port (P3) communicates with the fourth port (P4).
  • State shown by the solid line in Fig. 1), state where the first port (P1) communicates with the fourth port (P4) and the second port (P2) communicates with the third port (P3) (Fig. 1) (indicated by a broken line).
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state shown by the solid line in FIG.
  • the motor (13) is energized in this state, the refrigerant is circulated in the refrigerant circuit (10) to perform a refrigeration cycle.
  • the outdoor heat exchanger (21) serves as a radiator and the indoor heat exchanger (22) serves as an evaporator.
  • the high pressure of the refrigeration cycle is set higher than the critical pressure of carbon dioxide as a refrigerant.
  • the high pressure refrigerant in the supercritical state is discharged from the compressor (11).
  • This high-pressure refrigerant flows into the outdoor heat exchanger (21) through the first four-way selector valve (31).
  • the outdoor heat exchanger (21) the high-pressure refrigerant radiates heat to the outdoor air, and the temperature decreases.
  • the high-pressure refrigerant discharged from the outdoor heat exchanger (21) passes through the inner flow path (24) of the internal heat exchanger (23), and at that time, the evaporator flows through the outer flow path (25). Heat is exchanged with the refrigerant after passing through and cooled.
  • This refrigerant flows into the expander (12) through the second four-way selector valve (32).
  • the introduced high-pressure refrigerant expands, and the internal energy of the high-pressure refrigerant is converted into rotational power. Due to the expansion in the expander (12), the pressure of the high-pressure refrigerant decreases and changes from a supercritical state to a gas-liquid two-layer state.
  • the indoor heat exchanger (22) the low-pressure refrigerant absorbs heat from the indoor air and evaporates.
  • the indoor air is cooled by the low-pressure refrigerant. Cooled room air is sent back into the room.
  • the low-pressure refrigerant that has flowed out of the indoor heat exchanger (22) passes through the outer flow path (25) of the internal heat exchanger (23), and at that time, outdoor heat flows through the inner flow path (24). Heat is exchanged with the refrigerant after passing through the exchanger (21).
  • This refrigerant is sucked into the compressor (11) through the second four-way selector valve (32).
  • the refrigerant sucked into the compressor (11) is compressed to a predetermined pressure and discharged by the compressor (11).
  • the heat transfer fin (26) is provided in the outer flow path (25) through which the refrigerant passes through the indoor heat exchanger (22) serving as an evaporator.
  • the heat transfer fin (26) is not provided in the inner flow path (24) through which the refrigerant passes through the outdoor heat exchanger (21) serving as a radiator.
  • the heat transfer coefficient of the low-pressure gas refrigerant after passing through the indoor heat exchanger (22) is relatively low.
  • the heat transfer coefficient of the supercritical refrigerant after passing through the outdoor heat exchanger (21) is relatively low. high.
  • the heat transfer performance of the outer flow path (25) through which the heat transfer coefficient is relatively low and the low-pressure gas refrigerant flows is improved! Therefore, the low-pressure gas refrigerant flowing in the outer flow path (25) and the supercritical refrigerant flowing in the inner flow path (24) exchange heat relatively efficiently, and internal heat exchange (23 ), The amount of refrigerant flowing into the expander (12) increases as the specific volume decreases.
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state indicated by the broken line in FIG.
  • the motor (13) is energized in this state
  • the refrigerant is circulated in the refrigerant circuit (10) to perform a refrigeration cycle.
  • the indoor heat exchanger (22) serves as a radiator and the outdoor heat exchanger (21) serves as an evaporator.
  • the high pressure of the refrigeration cycle is set higher than the critical pressure of carbon dioxide as a refrigerant, as in the cooling operation.
  • the high pressure refrigerant in the supercritical state is discharged from the compressor (11).
  • This high-pressure refrigerant flows into the indoor heat exchanger (22) through the first four-way selector valve (31).
  • the indoor heat exchanger (22) the high-pressure refrigerant radiates heat to the indoor air, and the temperature decreases.
  • the indoor heat exchanger (22) the room air is heated by the high-pressure refrigerant, and the heated room air is sent back into the room.
  • the high-pressure refrigerant from the indoor heat exchanger (22) passes through the outer flow path (25) of the internal heat exchanger (23). After passing, it flows into the expander (12) through the second four-way selector valve (32).
  • the introduced high-pressure refrigerant expands, and the internal energy of the high-pressure refrigerant is converted into rotational power. Due to the expansion in the expander (12), the pressure of the high-pressure refrigerant decreases and changes from a supercritical state to a gas-liquid two-layer state.
  • the low-pressure refrigerant discharged from the expander (12) flows into the outdoor heat exchanger (21) through the first four-way switching valve (31). In the outdoor heat exchanger (21), the low-pressure refrigerant absorbs heat from the outdoor air and evaporates.
  • the low-pressure refrigerant discharged from the outdoor heat exchanger (21) passes through the inner flow path (24) of the internal heat exchanger (23) and is then compressed through the second four-way switching valve (32). Inhaled into the machine (11). The refrigerant sucked into the compressor (11) is compressed to a predetermined pressure and discharged by the compressor (11).
  • the heat transfer fin (26) is provided in the outer flow path (25) through which the refrigerant passes through the indoor heat exchanger (22) serving as a radiator.
  • the heat transfer fin (26) is not provided in the inner flow path (24) through which the refrigerant passes through the outdoor heat exchanger (21) serving as an evaporator.
  • the heat transfer coefficient of the low-pressure gas refrigerant after passing through the outdoor heat exchanger (21) is relatively low.
  • the heat transfer coefficient of the supercritical refrigerant after passing through the indoor heat exchanger (22) is relatively low. high.
  • the heat transfer coefficient is relatively low and the heat transfer performance of the inner flow path (24) through which the low-pressure gas refrigerant flows is low.
  • the supercritical refrigerant flowing through the channel (25) and the low-pressure gas refrigerant flowing through the inner channel (24) hardly exchange heat.
  • Embodiment 1 in the internal heat exchanger (23), during the cooling operation, the refrigerant after passing through the indoor heat exchanger (22) serving as an evaporator flows through the outer flow path (25) and serves as a radiator.
  • the refrigerant after passing through the outdoor heat exchanger (21) flows through the inner flow path (24).
  • the refrigerant after passing through the indoor heat exchanger (22) serving as a heat radiator flows through the outer flow path (25) and passes through the outdoor heat exchanger (21) serving as an evaporator. Flows through the inner channel (24). Then, heat transfer fins (26) are provided in the outer flow path (25).
  • the gas refrigerant after passing through the evaporator flows through the outer flow path (25), so the refrigerant in the outer flow path (25) and the refrigerant in the inner flow path (24) are relatively Efficient heat exchange
  • the temperature of the supercritical refrigerant decreases and flows into the expander (12).
  • the gas refrigerant after passing through the evaporator flows through the inner flow path (24), so the refrigerant in the outer flow path (25) and the refrigerant in the inner flow path (24) hardly exchange heat, The supercritical refrigerant flows into the expander (12) with almost no change in temperature.
  • the refrigerant flowing into the expander (12) is cooled in the internal heat exchanger (23) more than in the heating operation.
  • the flow rate of (12) increases. Therefore, in this embodiment, the flow rates of the compressor (11) and the expander (12) can be balanced by adjusting the specific volume or flow rate of the refrigerant flowing into the expander (12) during the cooling operation.
  • the refrigerant is expanded during the cooling operation in which the circulation amount of the refrigerant is larger than that during the heating operation.
  • a receiver (41) is provided between the expander (12) and the first four-way switching valve (31) in the refrigerant circuit (10) of the first embodiment. That is, in the second embodiment, the receiver (41) is provided on the outlet side of the expander (12).
  • the outflow side of the expander (12) is connected to the inlet of the receiver (41), and the outlet of the receiver (41) is connected to the first four-way selector valve (31). Connected to port 3 (P3)!
  • a liquid injection pipe (42) connected to the lower end of the receiver (41) and a gas vent pipe (43) connected to the upper end of the receiver (41) are connected to the suction side of the compressor (11).
  • the liquid junction pipe (42) is equipped with a first motor-operated valve (EV1)
  • the gas vent pipe (43) is equipped with a second motor-operated valve (EV2) so that the refrigerant flow rate can be adjusted. It is summer.
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state shown by the solid line in FIG.
  • the refrigerant from which the compressor (11) force is also discharged is the first four-way switching valve (31), the outdoor heat exchanger (21), the inner flow path (24) of the internal heat exchanger (23), the second 2 Four-way switching valve (32), expander (12), receiver (41), first four-way switching valve (31), indoor heat exchange (22), It flows through the outer flow path (25) of the internal heat exchanger (23) and the second four-way selector valve (32) in this order, and is sucked into the compressor (11) again.
  • the supercritical refrigerant after passing through the outdoor heat exchanger (21) flows through the inner flow path (24) and passes through the indoor heat exchanger (22).
  • the low-pressure gas refrigerant flows through the outer flow path (25), so that the refrigerant flowing through the inner flow path (24) and the refrigerant flowing through the outer flow path (25) exchange heat.
  • the supercritical refrigerant is cooled by the internal heat exchange (23) and flows into the expander (12) in a state where the specific volume is reduced.
  • the suction superheat degree control and the oil return operation of the compressor (11) can be performed by adjusting the opening of the motor-operated valve of the liquid injection pipe (42). Further, the receiver (41) can be vented by adjusting the opening of the motor-operated valve of the gas vent pipe (43). Also, adjusting the opening of the first motor operated valve (EV1) of the liquid injection pipe (42) and the second motor operated valve (EV2) of the gas vent pipe (43) will cause the compressor (11) to run out of capacity during operation. When it occurs, the shortage of capacity can be compensated.
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state indicated by the broken line in FIG.
  • the refrigerant from which the compressor (11) force is also discharged is the first four-way switching valve (31), the indoor heat exchanger (22), the outer flow path (25) of the internal heat exchanger (23), the second 2 Four-way switching valve (32), expander (12), receiver (41), first four-way switching valve (31), outdoor heat exchange (21), inner flow path of internal heat exchanger (23) ( 24), flows through the second four-way selector valve (32) in order, and is sucked into the compressor (11) again.
  • the supercritical refrigerant after passing through the indoor heat exchanger (22) flows through the outer flow path (25) and passes through the outdoor heat exchanger (21).
  • the low-pressure gas refrigerant flows through the inner flow path (24), so that the refrigerant flowing through the inner flow path (24) and the refrigerant flowing through the outer flow path (25) hardly exchange heat.
  • the refrigerant in the supercritical state has internal heat exchange (
  • the specific volume or flow rate can be adjusted by adjusting the temperature of the refrigerant flowing into the expander (12) during the cooling operation, so that the compressor (11) and the expander ( It is possible to balance the flow rate of 12) and prevent the COP from decreasing.
  • the receiver (41) is provided at a position different from that of the second embodiment.
  • the supercritical refrigerant that has exited the radiator flows into the internal heat exchanger (23), while the low-pressure refrigerant that exits the evaporator passes through the receiver (41) before the internal heat exchange ( It is configured to flow into 23).
  • the pipe connecting the second end of the indoor heat exchanger (22) and the outer flow path (25) of the internal heat exchanger (23) is connected to the indoor heat exchanger (22).
  • the first solenoid valve (SVI) is installed between the heat exchanger and the internal heat exchanger (23), branches before the first solenoid valve (SV1), and passes through the third solenoid valve (SV3). )It is connected to the.
  • the pipe connecting the second end of the outdoor heat exchanger (21) and the inner flow path (24) of the internal heat exchanger (23) is connected between the outdoor heat exchanger (21) and the internal heat exchanger (23).
  • 2 Solenoid valve (SV2) is provided, branched before this 2nd solenoid valve (SV2), and connected to receiver (41) via 4th solenoid valve (SV4)!
  • a liquid injection pipe (42) provided with an electric valve (EV) is connected to the suction side of the compressor (11).
  • the vent pipe (43) of the receiver (41) is branched into two, and the first branch pipe (43a) is a first check valve (CV) that prohibits the flow of refrigerant toward the receiver (41).
  • the second branch pipe (43b) is connected to the outer flow path (25) of the internal heat exchanger (23) through 1), and the second check valve (43b) prohibits the refrigerant flow toward the receiver (41). It is connected to the inner channel (24) of the internal heat exchanger (23) via CV2).
  • the first four-way selector valve (31) and the second four-way selector valve (32) are shown by solid lines in FIG. Switch to state.
  • the first solenoid valve (SV1), fourth solenoid valve (SV4) and force S are closed, and the second solenoid valve (SV2) and third solenoid valve (SV3) are opened.
  • the refrigerant from which the compressor (11) force is also discharged flows through the first four-way switching valve (31), the outdoor heat exchanger (21), and the inner flow path of the internal heat exchanger (23) ( 24), the second four-way selector valve (32), the expander (12), the first four-way selector valve (31), the indoor heat exchange (22), the receiver (41), the internal heat exchange (23) It flows through the outer channel (25) and the second four-way selector valve (32) in this order, and is sucked into the compressor (11) again.
  • the supercritical refrigerant after passing through the outdoor heat exchanger (21) flows through the inner flow path (24) and passes through the indoor heat exchanger (22).
  • the low-pressure gas refrigerant flows through the outer flow path (25), so that the refrigerant flowing through the inner flow path (24) and the refrigerant flowing through the outer flow path (25) exchange heat.
  • the supercritical refrigerant is cooled by the internal heat exchange (23) and flows into the expander (12) in a state where the specific volume is reduced.
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to a state indicated by a broken line in FIG.
  • the first solenoid valve (SV1) and the fourth solenoid valve (SV4) are ⁇ open ''
  • the second solenoid valve (SV2) and the third solenoid valve (SV3) are ⁇ closed ''. It becomes.
  • the refrigerant from which the compressor (11) force is also discharged flows through the first four-way switching valve (31), the indoor heat exchanger (22), and the external flow path of the internal heat exchanger (23) ( 25), second four-way selector valve (32), expander (12), first four-way selector valve (31), outdoor heat exchange (21), receiver (41), internal heat exchange (23) It flows through the inner channel (24) and the second four-way selector valve (32) in this order, and is sucked into the compressor (11) again.
  • the supercritical refrigerant after passing through the indoor heat exchanger (22) flows through the outer flow path (25) and passes through the outdoor heat exchanger (21).
  • the low-pressure gas refrigerant flows through the inner flow path (24), so that the refrigerant flowing through the inner flow path (24) and the refrigerant flowing through the outer flow path (25) hardly exchange heat.
  • the supercritical refrigerant flows into the expander (12) with almost no change in temperature even after passing through the internal heat exchanger (23).
  • the gas refrigerant after passing through the indoor heat exchanger (22) serving as an evaporator flows through the outer flow path (25).
  • Road ( The refrigerant in 24) exchanges heat relatively efficiently!
  • the refrigerant in the supercritical state flows into the expander (12) with the temperature decreased and the specific volume decreased.
  • the gas refrigerant after passing through the outdoor heat exchanger (21) serving as an evaporator flows through the inner flow path (24), so the refrigerant in the outer flow path (25) and the refrigerant in the inner flow path (24)
  • the refrigerant hardly exchanges heat and the supercritical refrigerant flows into the expander (12) with almost no change in temperature.
  • the specific volume or flow rate can be adjusted by adjusting the temperature of the refrigerant flowing into the expander (12) during the cooling operation, so that the compressor (11) and the expander ( It is possible to balance the flow rate of 12) and prevent the COP from decreasing.
  • the flow directions of the refrigerant in the inner flow path (24) and the outer flow path (25) of the internal heat exchanger (23) are opposite to each other during cooling operation (counterflow), and during the heating operation, This is an example in which the same direction is the same (parallel flow).
  • a third four-way selector valve (33) is provided between the outdoor heat exchanger (21) and the internal heat exchanger (23), and an internal heat exchanger ( The flow direction of the inner flow path (24) of 23) is reversed between the cooling operation and the heating operation.
  • the second end of the outdoor heat exchanger (21) is connected to the first port (P1) of the third four-way selector valve (33) and the second port of the third four-way selector valve (33).
  • the first port (P1) communicates with the second port (P2) and the third port (P3) communicates with the fourth port (P4).
  • the state shown by the solid line in Fig. 1), the state where the first port (P1) communicates with the third port (P3) and the second port (P2) communicates with the fourth port (P4) (see Fig. 1). (The state indicated by the broken line).
  • the first four-way selector valve (31), the second four-way selector valve (32), and the third four-way selector valve (33) are switched to the state shown by the solid line in FIG.
  • the refrigerant discharged from the compressor (11) passes through the first four-way switching valve (31), the outdoor heat exchange (21), the third four-way switching valve (33), the internal Inner flow path (24) of heat exchange (23), third four-way selector valve (33), second four-way selector valve (32), expander (12), first four-way selector valve (31),
  • the air flows through the indoor heat exchanger (22), the outer heat passage (25) of the internal heat exchanger (23), and the second four-way selector valve (32) in this order, and is sucked into the compressor (11) again.
  • the refrigerant flowing through the channel (24) and the refrigerant flowing through the outer channel (25) exchange heat efficiently. As a result, the refrigerant in the supercritical state is cooled by the internal heat exchanger (23) and flows into the expander (12) with the specific volume being reduced.
  • the first four-way selector valve (31), the second four-way selector valve (32), and the third four-way selector valve (33) are switched to the state indicated by the broken line in FIG.
  • the refrigerant discharged from the compressor (11) passes through the first four-way switching valve (31), the indoor heat exchange (22), the outer flow path (25) of the internal heat exchange (23), Second four-way selector valve (32), expander (12), first four-way selector valve (31), outdoor heat exchanger (21), third four-way selector valve (33), internal heat exchanger (23 )
  • the inner flow path (24), the third four-way selector valve (33), and the second four-way selector valve (32) in this order, and again sucked into the compressor (11).
  • the heat exchange efficiency of the counter flow is 0.8
  • the heat exchange efficiency of the parallel flow is 0.3
  • the heat transfer rate during cooling operation is between the outer channel (25) and the inner channel. If it is 2.3 times that of heating operation due to the difference in heat transfer area, the heat transfer performance during cooling is
  • Embodiment 4 Effect of Embodiment 4
  • the gas refrigerant after passing through the indoor heat exchanger (22) serving as an evaporator flows in the outer flow path (25), and in addition to the refrigerant in the outer flow path (25). Since the refrigerant in the inner channel (24) flows in opposite directions, the refrigerant in the outer channel (25) and the refrigerant in the inner channel (24) exchange heat relatively efficiently. As a result, the refrigerant in the supercritical state flows into the expander (12) in a state where the temperature drops and the specific volume force is reduced.
  • the gas refrigerant after passing through the outdoor heat exchanger (21) serving as an evaporator flows through the inner flow path (24), and at that time, the refrigerant in the outer flow path (25) and the inner flow path (24 ) Flows in the same direction as each other, the refrigerant in the outer flow path (25) and the refrigerant in the inner flow path (24) hardly exchange heat, and the temperature of the refrigerant in the supercritical state changes little. Without any further flow into the expander (12).
  • the specific volume or flow rate can be adjusted by adjusting the temperature of the refrigerant flowing into the expander (12) during the cooling operation, so that the compressor (11) and the expander ( It is possible to balance the flow rate of 12) and prevent the COP from decreasing.
  • a three-layer plate heat exchanger is used instead of the double-tube heat exchanger as the internal heat exchanger (23) in the first embodiment.
  • the internal heat exchange (23) includes an inner flow path (24) located in the center, a first outer flow path (25A) disposed adjacent to the outer side of the inner flow path (24), and a second outer flow path. With a road (25B).
  • the inner flow path (24) of the internal heat exchanger (23) is a flow path through which the refrigerant flows after passing through the outdoor heat exchanger (21) serving as a radiator during cooling operation.
  • the second outer channel (25B) is a channel through which the refrigerant after passing through the indoor heat exchanger (22) serving as an evaporator flows during cooling operation, and the indoor heat exchanger serving as a radiator during heating operation. It becomes a flow path through which the refrigerant passes through (22).
  • the first outer channel (25A) is a channel through which low-pressure refrigerant flows after passing through the second outer channel (25B) during cooling operation and through the inner channel (24) during heating operation.
  • the first outer flow path (25A) of the internal heat exchanger (23) is provided with heat transfer fins (26) on the side surface on the inner flow path (24) side.
  • the exchanger (23) has a heat transfer performance of the refrigerant flow path (first outer flow path (25A)) through which the refrigerant passes through the indoor heat exchanger (22) serving as an evaporator. It becomes higher than the heat transfer performance of the refrigerant flow path (inner flow path (24)) through which the refrigerant flows after passing through the outdoor heat exchanger (21).
  • the outdoor heat exchanger (21 ) Refrigerant flow path (inner flow path (24)) through which the refrigerant flows after passing through the indoor heat exchanger (22) serving as a heat sink (refrigerant flow path through which the refrigerant flows (first outer side) It is configured to be lower than the heat transfer performance of the flow path (25A)). Therefore, the internal heat exchanger (23) is configured such that the cooling performance of the refrigerant flowing into the expander (12) is higher during the cooling operation than during the heating operation.
  • the second end of the outdoor heat exchanger (21) is connected to the second four-way switching valve via the inner flow path (24) of the internal heat exchanger (23). It is connected to the first port (P1) of (32), and the second port (P2) of the second four-way selector valve (32) is connected to the inflow side of the expander (12).
  • the second end of the indoor heat exchanger (22) is connected to the third port (P3 of the second four-way selector valve (32) via the second outer flow path (25B) of the internal heat exchanger (23).
  • the fourth port (P4) of the second four-way selector valve (32) is connected to the compressor (11) via the first outer flow path (25A) of the internal heat exchanger (23). Connected to the suction side.
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state shown by the solid line in FIG.
  • the refrigerant from which the compressor (11) force is also discharged is the first four-way switching valve (31), the outdoor heat exchanger (21), the inner flow path (24) of the internal heat exchanger (23), the second 2 Four-way switching valve (32), expander (12), first four-way switching valve (31), indoor heat exchanger (22), second outer flow path (25B) of internal heat exchanger (23), It flows in order through the second four-way selector valve (32) and the first outer flow path (25A) of the internal heat exchange (23), and is sucked into the compressor (11) again.
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state indicated by the broken line in FIG. In this state, the refrigerant from which the compressor (11) force is also discharged is the first four-way switching valve (31), the indoor heat exchanger (22), the second outer flow path (25B) of the internal heat exchanger (23).
  • the supercritical refrigerant that passes through the first outer flow path (25 B) after passing through the indoor heat exchanger (22), and the outdoor heat exchanger (21) The low-pressure gas refrigerant that passes through the inner flow path (24) after passing through has a large temperature difference but is a parallel flow, so that the amount of heat exchange is relatively small. Further, since there is no temperature difference between the gas refrigerant passing through the inner flow path and the gas refrigerant passing through the first outer flow path (25 A) thereafter, the heat exchange amount is almost zero. This allows the supercritical refrigerant to flow into the expander (12) with almost no change in temperature even after passing through the internal heat exchanger (23).
  • the gas refrigerant after passing through the indoor heat exchanger (22) serving as an evaporator flows in the outer flow path (25) (first outer flow path (25A)). Therefore, the refrigerant in the first outer flow path (25A) and the refrigerant in the inner flow path (24) flow in opposite directions to each other!
  • the refrigerant in the channel (24) exchanges heat relatively efficiently, and the supercritical refrigerant flows into the expander (12) in a state where the temperature decreases and the specific volume decreases.
  • the gas refrigerant after passing through the outdoor heat exchanger (21) serving as an evaporator flows through the inner channel (24) and the first outer channel (25A), and at that time, the second outer channel Since the refrigerant in the supercritical state (25B) hardly exchanges heat, the refrigerant in the supercritical state flows into the expander (12) with almost no change in temperature.
  • the specific volume or flow rate can be adjusted by adjusting the temperature of the refrigerant flowing into the expander (12) during the cooling operation, so that the compressor (11) and the expander ( 12) Current It is possible to balance the amount and prevent the COP from dropping.
  • the refrigerant after passing through the radiator and the refrigerant before flowing into the evaporator exchange heat with the internal heat exchanger (23) (double tube heat exchanger). This is an example.
  • the discharge side of the compressor (11) is connected to the first port (P1) of the first four-way selector valve (31), and the first four-way selector valve (31) has the second Two ports (P2) are connected to the first end of the outdoor heat exchanger (21)!
  • the second end of the outdoor heat exchanger (21) is connected to the first port (P1) of the second four-way selector valve (32) via the inner flow path (24) of the internal heat exchanger (23).
  • the second port (P2) of the four-way selector valve (32) is connected to the inflow side of the expander (12).
  • the outflow side of the expander (12) is connected to the third port (P3) of the second four-way selector valve (32), and the fourth port (P4) of the second four-way selector valve (32) is connected to the internal heat exchanger. It is connected to the first end of the indoor heat exchanger (22) via the outer flow path (25) of (23). The second end of the indoor heat exchanger (22) is connected to the third port (P3) of the first four-way selector valve (31), and the fourth port (P4) of the first four-way selector valve (31) is the compressor. It is connected to the suction side of (11).
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state indicated by the solid line in FIG.
  • the refrigerant from which the compressor (11) force is also discharged is the first four-way switching valve (31), the outdoor heat exchanger (21), the inner flow path (24) of the internal heat exchanger (23), the second 2 Four-way switching valve (32), expander (12), second four-way switching valve (32), outer flow path (25) of internal heat exchanger (23), indoor heat exchanger (22), first It flows through the four-way selector valve (31) in order, and is sucked into the compressor (11) again.
  • the supercritical refrigerant after passing through the outdoor heat exchanger (21) flows through the inner flow path (24) and passes through the indoor heat exchanger (22). Since the low-pressure refrigerant before the flow flows in the outer flow path (25), the refrigerant flowing in the inner flow path (24) and the refrigerant flowing in the outer flow path (25) exchange heat. Thus, the supercritical refrigerant is cooled by the internal heat exchange (23) and flows into the expander (12) in a state where the specific volume is reduced.
  • the first four-way selector valve (31) and the second four-way selector valve (32) are indicated by broken lines in FIG. Switch to state.
  • the refrigerant from which the compressor (11) force is also discharged is the first four-way switching valve (31), the indoor heat exchanger (22), the outer flow path (25) of the internal heat exchanger (23), the second 2 Four-way switching valve (32), expander (12), second four-way switching valve (32), internal heat exchanger (23) inner flow path (24), outdoor heat exchanger (21), first It flows through the four-way selector valve (31) in order, and is sucked into the compressor (11) again.
  • the supercritical refrigerant after passing through the indoor heat exchanger (22) flows through the outer flow path (25) and passes through the outdoor heat exchanger (21). Since the low-pressure refrigerant before the flow flows through the inner flow path (24), the refrigerant flowing through the inner flow path (24) and the refrigerant flowing through the outer flow path (25) hardly exchange heat. As a result, the refrigerant in the supercritical state flows into the expander (12) with almost no change in temperature even after passing through the internal heat exchanger (23).
  • the refrigerant before passing through the indoor heat exchanger (22) serving as an evaporator flows through the outer flow path (25), so the refrigerant in the outer flow path (25) and the inner flow path
  • the refrigerant of (24) exchanges heat relatively efficiently, and the supercritical refrigerant flows into the expander (12) in a state where the temperature decreases and the specific volume decreases.
  • the refrigerant before passing through the outdoor heat exchanger (21) serving as an evaporator flows through the inner flow path (24), so the refrigerant in the outer flow path (25) and the refrigerant in the inner flow path (24).
  • the refrigerant in the supercritical state flows into the expander (12) with almost no change in temperature.
  • the specific volume or flow rate can be adjusted by adjusting the temperature of the refrigerant flowing into the expander (12) during the cooling operation, so that the compressor (11) and the expander ( It is possible to balance the flow rate of 12) and prevent the COP from decreasing.
  • Embodiment 7 uses a bridge circuit (32a) in the refrigerant circuit (10) of Embodiment 6 instead of the second four-way selector valve (32).
  • the bridge circuit (32a) is configured by connecting four pipes in a bridge shape and has four ports (P1, P2, P3, P4). .
  • Each of the four pipes is provided with a check valve (CV).
  • the check valve (CV) includes a refrigerant flow from the first port (P1) to the second port (P2), a directional refrigerant flow from the third port (P3) to the fourth port (P4), Three It is installed in each pipe line to allow the refrigerant flow from port (P3) to the first port (PI) and the directional refrigerant flow from the fourth port (P4) to the second port (P2). Yes.
  • the inner flow path (24) of the internal heat exchanger (23) is connected to the first port (P1) of the bridge circuit (32a).
  • the second port (P2) of the bridge circuit (32a) is connected to the inflow side of the expander (12).
  • the outflow side of the expander (12) is connected to the third port (P3) of the bridge circuit (32a).
  • the fourth port (P4) of the bridge circuit (32a) is connected to the outer flow path (25) of the internal heat exchanger (23).
  • the first four-way selector valve (31) switches to the state shown by the solid line in FIG. In this state, the refrigerant from which the compressor (11) is also discharged is the first four-way switching valve (31), the outdoor heat exchanger (21), the inner flow path (24) of the internal heat exchanger (23), Bridge circuit (32a), expander (12), pledge circuit (32, outer flow path (25) of internal heat exchanger (23), indoor heat exchanger (22), first four-way switching valve (31 ) In order and again sucked into the compressor (11).
  • the supercritical refrigerant after passing through the outdoor heat exchanger (21) flows through the inner flow path (24) and passes through the indoor heat exchanger (22). Since the low-pressure refrigerant before the flow flows in the outer flow path (25), the refrigerant flowing in the inner flow path (24) and the refrigerant flowing in the outer flow path (25) exchange heat. Thus, the supercritical refrigerant is cooled by the internal heat exchange (23) and flows into the expander (12) in a state where the specific volume is reduced.
  • the first four-way selector valve (31) switches to the state indicated by the broken line in FIG.
  • the refrigerant from which the compressor (11) force is also discharged includes the first four-way switching valve (31), the indoor heat exchanger (22), the outer flow path (25) of the internal heat exchanger (23), Bridge circuit (32a), expander (12), pledge circuit (32, inner heat exchanger (23) inner flow path (24), outdoor heat exchanger (21), first four-way switching valve (31 ) In order and again sucked into the compressor (11).
  • the supercritical refrigerant after passing through the indoor heat exchanger (22) flows through the outer flow path (25) and passes through the outdoor heat exchanger (21). Since the low-pressure refrigerant before the flow flows through the inner flow path (24), the refrigerant flowing through the inner flow path (24) and the refrigerant flowing through the outer flow path (25) hardly exchange heat. This allows the supercritical refrigerant to exchange internal heat (23). Even if it passes, the temperature hardly changes and flows into the expander (12).
  • the specific volume or flow rate can be adjusted by adjusting the temperature of the refrigerant flowing into the expander (12) during the cooling operation, so that the compressor (11) and the expander ( It is possible to balance the flow rate of 12) and prevent the COP from decreasing.
  • Embodiment 8 differs from Embodiment 6 in that the refrigerant flow directions in the inner flow path (24) and the outer flow path (25) of the internal heat exchanger (23) are opposite to each other during the cooling operation and to each other during the heating operation. In this example, the directions are the same.
  • a third four-way switching valve (23) is provided between the outdoor heat exchange (21) and the internal heat exchange (23). 33) so that the flow direction of the inner flow path (24) does not reverse even if the flow direction of the outer flow path (25) of the internal heat exchanger (23) is reversed during cooling operation and heating operation.
  • the second end of the outdoor heat exchange ⁇ (21) is connected to the first port (P1) of the third four-way selector valve (33) and the second port of the third four-way selector valve (33).
  • the first port (P1) communicates with the second port (P2) and the third port (P3) communicates with the fourth port (P4).
  • the state shown by the solid line in Fig. 1), the state where the first port (P1) communicates with the third port (P3) and the second port (P2) communicates with the fourth port (P4) (see Fig. 1). (The state indicated by the broken line).
  • Other configurations are the same as those in the sixth embodiment.
  • the first four-way selector valve (31), the second four-way selector valve (32), and the third four-way selector valve (33) are switched to the state shown by the solid line in FIG.
  • the refrigerant discharged from the compressor (11) passes through the first four-way switching valve (31), the outdoor heat exchange (21), the third four-way switching valve (33), the internal heat exchange ( 23) inner flow path (24), third four-way selector valve (33), second four-way selector valve (32), expander (12), second four-way selector valve (32), internal heat exchanger
  • the first four-way selector valve (31), the second four-way selector valve (32), and the third four-way selector valve (33) are switched to the state indicated by the broken line in FIG.
  • the refrigerant discharged from the compressor (11) passes through the first four-way switching valve (31), the indoor heat exchange (22), the outer flow path (25) of the internal heat exchange (23), 2nd 4-way selector valve (32), expander (12), 2nd 4-way selector valve (32), 3rd 4-way selector valve (33), inner flow path of internal heat exchanger (23) (24)
  • the air flows through the third four-way switching valve (33), the outdoor heat exchanger (21), and the first four-way switching valve (31) in this order, and is sucked into the compressor (11) again.
  • the low-pressure refrigerant before passing through the indoor heat exchanger (22) serving as an evaporator flows through the outer flow path (25), and in addition, the refrigerant in the outer flow path (25).
  • the refrigerant in the inner flow path (24) flow in opposite directions, so that the refrigerant in the outer flow path (25) and the refrigerant in the inner flow path (24) exchange heat relatively efficiently.
  • the refrigerant in the supercritical state flows into the expander (12) in a state in which the temperature drops and the specific volume force is reduced.
  • the low-pressure refrigerant before passing through the outdoor heat exchanger (21) serving as an evaporator flows through the inner flow path (24), and at that time, the refrigerant in the outer flow path (25) and the inner flow path ( Since the refrigerant in (24) flows in the same direction in the same direction, the refrigerant in the outer channel (25) and the refrigerant in the inner channel (24) hardly exchange heat, and the refrigerant in the supercritical state has a temperature of Flows into the expander (12) with almost no change.
  • Embodiment 9 relates to an air conditioner (1) constituted by a refrigeration apparatus according to the present invention.
  • the air conditioner (1) includes a refrigerant circuit (10).
  • the refrigerant circuit (10) performs a vapor compression refrigeration cycle by compressing the refrigerant to a supercritical state.
  • the air conditioner (1) of the ninth embodiment is configured to circulate the refrigerant in the refrigerant circuit (10) and switch between the cooling operation (cooling operation) and the heating operation (heating operation).
  • the refrigerant circuit (10) is filled with carbon dioxide (CO 2) as a refrigerant.
  • the medium circuit (10) includes a compressor (11), an expander (12), an outdoor heat exchanger (heat source side heat exchanger) (21), indoor heat exchange (use side heat exchange) (22), An internal heat exchanger (23), a first four-way selector valve (31), and a second four-way selector valve (32) are provided.
  • the compressor (11) and the expander (12) are each composed of a rotary piston type fluid machine having a unique cylinder volume.
  • the compressor (11) and the expander (12) are connected to each other by the rotating shaft of the motor (13).
  • the compressor (11) includes power (expansion power) obtained by expansion of the refrigerant in the expander (12) and power obtained by energizing the motor (13). And driven by both.
  • the ratio (VeZVc) between the volume circulation amount Ve of the refrigerant passing through the expander (12) and the volume circulation amount Vc of the refrigerant passing through the compressor (11) is determined by each fluid machine ( 11,12) It is a fixed value determined by the cylinder volume ratio.
  • the cylinder volume ratio is the ratio of the above VeZVc and the density ratio d eZdc between the inflow refrigerant density de of the expander (12) and the intake refrigerant density dc of the compressor (11) when the air conditioner (1) is heated. Is designed so that the mass flow rate Me of refrigerant passing through the expander (12) is equal to the mass flow rate Mc of refrigerant passing through the compressor (11) !,
  • the fluid machine constituting them is not limited to the rolling piston type.
  • a scroll-type positive displacement fluid machine is used as the compressor (11 ) Or expander (12).
  • the outdoor heat exchanger (21) is configured by so-called cross fin type fin 'and' tube heat exchange. Outdoor air is supplied to the outdoor heat exchanger (21) by a fan (not shown). In the outdoor heat exchanger (21), heat exchange between the supplied outdoor air and the refrigerant in the refrigerant circuit (10) is performed.
  • the indoor heat exchange (22) is constituted by a so-called cross fin type fin 'and' tube heat exchange ⁇ . Room air is supplied to the indoor heat exchanger (22) by a fan (not shown). In the indoor heat exchanger (22), heat is exchanged between the supplied indoor air and the refrigerant in the refrigerant circuit (10).
  • the internal heat exchanger (23) includes a first channel (27) and a second channel arranged adjacent to each other.
  • the refrigerant flowing through the first flow path (27) and the refrigerant flowing through the second flow path (28) are configured to be able to exchange heat.
  • the internal heat exchanger (23) may be configured such that the high-pressure refrigerant is cooled by exchanging heat with the low-pressure refrigerant during the cooling operation.
  • the internal heat exchanger (23) allows the high-pressure refrigerant to flow through the first flow path (27), while the low-pressure refrigerant flows through the second flow path (28) in the direction opposite to that of the high-pressure refrigerant.
  • both flow paths (24, 25) are configured to be parallel flows in which high-pressure refrigerant flows in the same direction.
  • the outdoor heat exchange functioning as a radiator
  • the high-pressure refrigerant after passing through the converter (21) is cooled by exchanging heat with the low-pressure refrigerant before passing through the indoor heat exchanger (22) serving as an evaporator.
  • the high-pressure refrigerant that has passed through the indoor heat exchanger (22) that serves as a radiator flows in order through the second flow path (28) and the first flow path (27), and the high-pressure refrigerant is cooled. I will not.
  • the discharge side of the compressor (11) is connected to the first port (P1) of the first four-way switching valve (31), and the first four-way switching valve (31)
  • the second port (P2) is connected to the first end of the outdoor heat exchanger (21).
  • the second end of the outdoor heat exchanger (21) is connected to the first port (P1) of the second four-way selector valve (32), and the second port (P2) of the second four-way selector valve (32) is internal. It is connected to the inflow side of the expander (12) via the first flow path (27) of the heat exchanger (23).
  • the expansion side of the expander (12) is connected to the third port (P3) of the second four-way selector valve (32), and the fourth port (P4) of the second four-way selector valve (32) is internally heat exchanged. It is connected to the first end of the indoor heat exchanger (22) via the second flow path (28) of the heat exchanger (23). The second end of the indoor heat exchanger (22) is connected to the third port (P3) of the first four-way selector valve (31), and the fourth port (P4) of the first four-way selector valve (31) Connected to the suction side of the compressor (11).
  • the first port (P1) communicates with the second port (P2) and the third port (P3) communicates with the fourth port (P4).
  • the state shown by the solid line in Fig. 10
  • the state where the first port (P1) communicates with the third port (P3) and the second port (P2) communicates with the fourth port (P4) see Fig. 10). (The state indicated by the broken line).
  • the first port (P1) communicates with the second port (P2) and the third port (P3) communicates with the fourth port (P4).
  • State shown by the solid line in Fig. 10
  • state where the first port (P1) communicates with the third port (P3) and the second port (P2) communicates with the fourth port (P4) Fig. (The state indicated by the broken line in FIG. 10).
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state shown by the solid line in FIG.
  • the motor (13) is energized in this state, the refrigerant circulates in the refrigerant circuit (10) to perform a refrigeration cycle.
  • the outdoor heat exchanger (21) becomes a radiator,
  • the heat exchanger (22) becomes the evaporator.
  • the high pressure of the refrigeration cycle is set higher than the critical pressure of carbon dioxide as a refrigerant.
  • the high pressure refrigerant in the supercritical state is discharged from the compressor (11).
  • This high-pressure refrigerant flows into the outdoor heat exchanger (21) through the first four-way switching valve (31) as indicated by the solid arrow.
  • the outdoor heat exchanger (21) the high-pressure refrigerant radiates heat to the outdoor air, and the temperature decreases.
  • the high-pressure refrigerant discharged from the outdoor heat exchanger (21) passes through the first flow path (27) of the internal heat exchanger (23) via the second four-way switching valve (32).
  • This high-pressure refrigerant is cooled by exchanging heat with the low-pressure refrigerant flowing in the second flow path (28) in the internal heat exchanger (23).
  • the high-pressure refrigerant flows into the expander (12).
  • the introduced high-pressure refrigerant expands, and the internal energy of the high-pressure refrigerant is converted into rotational power. Due to the expansion in the expander (12), the pressure of the high-pressure refrigerant drops and changes from a supercritical state to a gas-liquid two-phase state.
  • the low-pressure refrigerant exiting the expander (12) passes through the second flow path (28) of the internal heat exchange (23) through the second four-way switching valve (32), and at that time, Heat is exchanged with the high-pressure refrigerant flowing through one channel (27).
  • This low-pressure refrigerant flows into the indoor heat exchanger (22), and in the indoor heat exchanger (22) absorbs heat from the indoor air and evaporates.
  • the indoor heat exchanger (22) the room air is cooled by the low-pressure refrigerant, and the cooled room air is sent back into the room.
  • the low-pressure refrigerant discharged from the indoor heat exchanger (22) is sucked into the compressor (11) through the first four-way switching valve (31).
  • the refrigerant sucked into the compressor (11) is compressed to a predetermined pressure and discharged from the compressor (11).
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state shown by the broken line in FIG.
  • the motor (13) is energized in this state, the refrigerant circulates in the refrigerant circuit (10) to perform a refrigeration cycle.
  • the indoor heat exchanger (22) serves as a radiator and the outdoor heat exchanger (21) serves as an evaporator.
  • the high pressure of the refrigeration cycle is set higher than the critical pressure of the carbon dioxide as a refrigerant, as in the cooling operation.
  • the supercritical high-pressure refrigerant is also discharged from the compressor (11) force.
  • This high-pressure refrigerant flows into the indoor heat exchanger (22) through the first four-way switching valve (31) as indicated by the dashed arrow.
  • the indoor heat exchanger (22) the high-pressure refrigerant radiates heat to the indoor air, and the temperature decreases. Ma
  • the indoor air is heated by the high-pressure refrigerant, and the heated indoor air is sent back into the room.
  • the high-pressure refrigerant discharged from the indoor heat exchanger (22) passes through the second flow path (28) of the internal heat exchanger (23) and then passes through the second four-way switching valve (32). Passes through the first flow path (27) of the internal heat exchanger (23). At that time, in the internal heat exchanger (23), the high-pressure refrigerant that has exited the indoor heat exchanger (22) flows in order through the second flow path (28) and the first flow path (27), so that a temperature change occurs. What! /
  • the introduced high-pressure refrigerant expands, and the internal energy of the high-pressure refrigerant is converted into rotational power. Due to the expansion in the expander (12), the pressure of the high-pressure refrigerant decreases and changes from a supercritical state to a gas-liquid two-phase state.
  • the low-pressure refrigerant absorbs heat from the outdoor air and evaporates.
  • the low-pressure refrigerant that has also generated power in the outdoor heat exchanger (21) is sucked into the compressor (11) through the first four-way switching valve (31).
  • the refrigerant sucked into the compressor (11) is compressed to a predetermined pressure, and the compressor (11) force is also discharged.
  • Embodiment 9 in the internal heat exchanger (23), during the cooling operation, the high-pressure refrigerant after passing through the outdoor heat exchanger (21) serving as a radiator flows through the first flow path (27), and the evaporator Since the low-pressure refrigerant before passing through the indoor heat exchanger (22) that flows through the second flow path (28), the high-pressure refrigerant is cooled.
  • the high-pressure refrigerant after passing through the indoor heat exchanger (22), which serves as a radiator flows in order through the second flow path (28) and the first flow path (27), so the temperature of the high-pressure refrigerant changes. Absent.
  • the internal heat exchanger (23) functions only during the cooling operation, the high-pressure refrigerant sucked into the expander (12) can be cooled during the cooling operation, and the expander (12) The inflow refrigerant density de can be increased.
  • the refrigerant mass flow rate Mc of the compressor (11) becomes larger than the refrigerant mass flow rate Me of the expander (12) for the reasons described above.
  • the refrigerant mass flow rates Mc and Me of both can be balanced.
  • the cooling medium amount flows Me and Mc are balanced without bypassing part of the refrigerant with the expander (12) force. For this reason, if a part of the refrigerant is bypassed from the expander (12), the expansion power of the expander (12) decreases and the COP also decreases. In this embodiment, all the refrigerant is expanded. Since it can be introduced in (12), it is possible to avoid a drop in COP.
  • the high pressure refrigerant and the low pressure refrigerant flow through the internal heat exchanger (23) in the reverse direction during the cooling operation, thereby improving the heat exchange efficiency.
  • the medium is a liquid refrigerant before the evaporator and has a high heat transfer coefficient
  • the high pressure refrigerant and the low pressure refrigerant may flow in the same direction through the internal heat exchanger (23). Even in this case, it is possible to cool the high-pressure refrigerant.
  • a receiver (41) is provided between the expander (12) and the second four-way selector valve (32) in the refrigerant circuit (10) of the ninth embodiment. . That is, in the first modification, the receiver (41) is provided on the outlet side of the expander (12).
  • the outflow side of the expander (12) is connected to the inlet of the receiver (41), and the outlet of the receiver (41) is connected to the second four-way selector valve (32).
  • port 3 (P3)! Also, on the suction side of the compressor (11), there are a liquid induction pipe (42) connected to the lower end of the receiver (41) and a gas vent pipe (43) connected to the upper part of the receiver (41). And are connected.
  • the liquid index pipe (42) is provided with a first motor-operated valve (EV1) and the gas vent pipe (43) is provided with a second motor-operated valve (EV2). ing.
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state shown by the solid line in FIG.
  • the refrigerant from which the compressor (11) force is also discharged is the first four-way switching valve (31), the outdoor heat exchange (21), the second four-way switching valve (32), the internal heat exchange (23 ) First flow path (27), expander (12), receiver (41), second four-way selector valve (32), internal heat exchange (23) second flow path (28), indoor heat exchange Flows through the compressor (22) and the first four-way selector valve (31) in this order, and is sucked into the compressor (11) again.
  • the high-pressure refrigerant after passing through the outdoor heat exchanger (21) flows through the first flow path (27) and before passing through the indoor heat exchanger (22). Since the low-pressure refrigerant flows through the second flow path (28), the high-pressure refrigerant and the low-pressure refrigerant exchange heat. As a result, the high-pressure refrigerant is cooled by the internal heat exchange (23) and flows into the power expander (12).
  • the suction superheat degree control and the oil return operation of the compressor (11) are controlled by adjusting the opening degree of the first motor operated valve (EV1) of the liquid injection pipe (42). Is possible. Further, the receiver (41) can be vented by adjusting the opening degree of the second motor operated valve (EV2) of the vent pipe (43). In addition, if the opening of the first motor operated valve (EV1) of the liquid induction pipe (42) and the second motor operated valve (EV2) of the gas vent pipe (43) are adjusted, there will be insufficient capacity in the compressor (11) during operation. When it occurs, the shortage of capacity can be compensated.
  • the refrigerant from which the compressor (11) force is also discharged includes the first four-way switching valve (31), the indoor heat exchanger (22), the second flow path (28) of the internal heat exchanger (23), 2nd 4-way selector valve (32), 1st flow path (27) of internal heat exchanger (23), expander (12), receiver (41), 2nd 4-way selector valve (32), outdoor heat exchange Flows through the compressor (21) and the first four-way selector valve (31) in this order, and is sucked into the compressor (11) again.
  • the high-pressure refrigerant after passing through the indoor heat exchanger (22) serving as a radiator passes through the second flow path (28) and the first flow path (27) in order. Because it flows, the temperature of the high-pressure refrigerant does not change. As a result, the high-pressure refrigerant flows into the expander (12) without being cooled.
  • the second modification of the ninth embodiment uses a bridge circuit (32a) instead of the second four-way switching valve (32) in the refrigerant circuit (10) of the ninth embodiment.
  • the bridge circuit (32a) is configured by connecting four pipes in a bridge shape and has four ports (P1, P2, P3, P4).
  • Each of the four pipes is provided with a check valve (CV).
  • the check valve (CV) has a directional refrigerant flow from the first port (P1) to the second port (P2) and a directional refrigerant flow from the third port (P3) to the fourth port (P4).
  • the check valve (CV) has a directional refrigerant flow from the first port (P1) to the second port (P2) and a directional refrigerant flow from the third port (P3) to the fourth port (P4).
  • the second end of the outdoor heat exchanger (21) is connected to the first port (P1) of the bridge circuit (32a).
  • the second port (P2) of the bridge circuit (32a) is connected to the inflow side of the expander (12) via the first flow path (27) of the internal heat exchange (23).
  • the outflow side of the expander (12) is connected to the third port (P3) of the bridge circuit (32a)!
  • the fourth port (P4) of the bridge circuit (32a) is connected to the first end of the indoor heat exchanger (22) via the second flow path (28) of the internal heat exchanger (23).
  • the first four-way selector valve (31) switches to the state shown by the solid line in FIG. In this state, the refrigerant from which the compressor (11) force is also discharged passes through the first four-way switching valve (31), the outdoor heat exchanger (21), the bridge circuit (32a), and the internal heat exchanger (23). 1 flow path (27), expander (12), bridge circuit (32, 2nd flow path (28) of internal heat exchanger (23), indoor heat exchanger (22), 1st four-way selector valve ( 31) in order and again sucked into the compressor (11).
  • the high-pressure refrigerant after passing through the outdoor heat exchanger (21) flows through the first flow path (27) and before passing through the indoor heat exchanger (22). Since the low-pressure refrigerant flows through the second flow path (28), the high-pressure refrigerant and the low-pressure refrigerant exchange heat. As a result, the high-pressure refrigerant is cooled by the internal heat exchange (23) and flows into the power expander (12).
  • the first four-way selector valve (31) switches to the state indicated by the broken line in FIG. In this state, the refrigerant from which the compressor (11) force is also discharged passes through the first four-way selector valve (31), the indoor heat exchanger. Exchanger (22), second flow path (28) of internal heat exchanger (23), bridge circuit (32, first flow path (27) of internal heat exchanger (23), expander (12), bridge It flows through the circuit (32a), the outdoor heat exchanger (21), and the first four-way selector valve (31) in this order, and is sucked into the compressor (11) again.
  • the high-pressure refrigerant after passing through the indoor heat exchanger (22) serving as a radiator passes through the second flow path (28) and the first flow path (27) in order. Because it flows, the temperature of the high-pressure refrigerant does not change. As a result, the high-pressure refrigerant flows into the expander (12) without being cooled.
  • the internal heat exchanger (23) functions only during the cooling operation, the high-pressure refrigerant sucked into the expander (12) can be cooled during the cooling operation, and the expander (12) The refrigerant density de can be increased.
  • the refrigerant mass flow rate Mc of the compressor (11) becomes larger than the refrigerant mass flow rate Me of the expander (12) for the reasons described above.
  • the refrigerant mass flow rate Me of the expander (12) can be increased, so that the refrigerant mass flow rates Mc and Me of both can be balanced.
  • the refrigerant mass flow rate Me, Mc is balanced without bypassing a part of the refrigerant from the expander (12). By introducing it, it is possible to avoid a drop in COP.
  • the tenth embodiment is different from the ninth embodiment in the configuration of the refrigerant circuit (10).
  • the position of the internal heat exchanger (23) is different from that of the ninth embodiment, and a bypass passage (45) is provided for the high-pressure refrigerant to bypass the internal heat exchanger (23) during heating operation.
  • the discharge side of the compressor (11) is connected to the first port (P1) of the first four-way switching valve (31), and the first four-way switching valve (31 )
  • Second port (P2) is connected to the first end of the outdoor heat exchanger (21).
  • the second end of the outdoor heat exchanger (21) is connected to the first port (P1) of the second four-way selector valve (32), and the second port (P2) of the second four-way selector valve (32) is internal. It is connected to the inflow side of the expander (12) via the first flow path (27) of the heat exchanger (23).
  • a first on-off valve (SV1) is provided between the second port (P2) of the second four-way selector valve (32) and the first flow path (27) of the internal heat exchanger (23).
  • One end of a bypass passage (45) having a second on-off valve (SV2) is connected to the pipe between the on-off valve (SV1).
  • the other end of the bypass passage (45) joins a pipe connecting the first flow path (27) of the internal heat exchanger (23) and the inflow side of the expander (12).
  • the outflow side of the expander (12) is connected to the third port (P3) of the second four-way selector valve (32), and the fourth port (P4) of the second four-way selector valve (32) Connected to the first end of the heat exchanger (22)!
  • the second end of the indoor heat exchanger (22) is connected to the third port (P3) of the first four-way selector valve (31), and the fourth port (P4) of the first four-way selector valve (31) is It is connected to the suction side of the compressor (11) via the second flow path (28) of the internal heat exchanger (23).
  • an electromagnetic on-off valve or an electric valve can be used as the first on-off valve (SV1) and the second on-off valve (SV2).
  • the first on-off valve (SV1) may be provided either before or after the internal heat exchange (23).
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state shown by the solid line in FIG.
  • the first on-off valve (SV1) is opened and the second on-off valve (SV2) is closed.
  • the refrigerant from which the compressor (11) force is also discharged includes the first four-way switching valve (31), the outdoor heat exchanger (21), the second four-way switching valve (32), the internal heat exchanger (23 ) First flow path (27), expander (12), second four-way selector valve (32), indoor heat exchange (22), first four-way selector valve (31), internal heat exchanger (23 ) Through the second flow path (28) in order, and again sucked into the compressor (11).
  • the high-pressure refrigerant after passing through the outdoor heat exchanger (21) flows through the first flow path (27) and passes through the indoor heat exchanger (22). Since the low-pressure refrigerant flows through the second flow path (28), the high-pressure refrigerant and the low-pressure refrigerant exchange heat. As a result, the high-pressure refrigerant is cooled by the internal heat exchange (23) and flows into the power expander (12).
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state shown by the broken line in FIG.
  • the first on-off valve (SV1) is closed and the second on-off valve (SV2) is open. Is done.
  • the refrigerant from which the compressor (11) force is also discharged includes the first four-way switching valve (31), the indoor heat exchanger (22), the second four-way switching valve (32), the bypass passage (45),
  • the high-pressure refrigerant after passing through the indoor heat exchanger (22) does not flow, and only the low-pressure refrigerant after passing through the outdoor heat exchanger (21) is the second flow. Since it flows through the passage (28), the temperature of the high-pressure refrigerant does not change. As a result, the high-pressure refrigerant flows into the expander (12) without being cooled.
  • Embodiment 10 since the internal heat exchanger (23) functions only during the cooling operation, the high-pressure refrigerant sucked into the expander (12) can be cooled during the cooling operation, and the inflow of the expander (12) The refrigerant density de can be increased. As a result, during the cooling operation of the conventional refrigeration system, the refrigerant mass flow rate Mc of the compressor (11) becomes larger than the refrigerant mass flow rate Me of the expander (12), whereas the expander (12) Since the refrigerant mass flow rate Me can be increased, the refrigerant mass flow rates Mc and Me of both can be balanced.
  • a receiver (41) is provided between the outlet side of the evaporator and the low pressure side of the internal heat exchanger (23). It is a thing.
  • the fourth port (P4) of the first four-way selector valve (31) is connected to the inlet of the receiver (41), and the outlet of the receiver (41) is the internal heat exchanger. It is connected to the suction side of the compressor (11) via the second flow path (28) of (23).
  • a liquid injection pipe (42) connected to the lower end of the receiver (41) is connected to the suction side of the compressor (11).
  • the liquid injection pipe (42) is equipped with a first motor-operated valve (EV1) to adjust the refrigerant flow rate. It is like that.
  • the internal heat exchange ⁇ (23) is configured so that the high-pressure refrigerant and the low-pressure refrigerant flow in opposite directions during cooling operation.
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state shown by the solid line in FIG.
  • the first on-off valve (SV1) is opened and the second on-off valve (SV2) is closed.
  • the refrigerant from which the compressor (11) force is also discharged includes the first four-way switching valve (31), the outdoor heat exchanger (21), the second four-way switching valve (32), the internal heat exchanger (23 ) First flow path (27), expander (12), second four-way selector valve (32), indoor heat exchange (22), first four-way selector valve (31), receiver (41) Then, it flows through the second flow path (28) of the internal heat exchanger (23) in order, and is sucked into the compressor (11) again.
  • the high-pressure refrigerant after passing through the outdoor heat exchanger (21) flows through the first flow path (27), and the indoor heat exchanger (22) and the receiver (41) Since the low-pressure refrigerant after passing through the second flow path (28) flows, the high-pressure refrigerant and the low-pressure refrigerant exchange heat. As a result, the high-pressure refrigerant is cooled by the internal heat exchange (23) and flows into the power expander (12).
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state shown by the broken line in FIG.
  • the first on-off valve (SV1) is closed and the second on-off valve (SV2) is opened.
  • the refrigerant from which the compressor (11) force is also discharged includes the first four-way switching valve (31), the indoor heat exchanger (22), the second four-way switching valve (32), the bypass passage (45), Second flow of expander (12), second four-way selector valve (32), outdoor heat exchanger (21), first four-way selector valve (31), receiver (41), internal heat exchanger (23) It flows through the passage (28) in order, and is sucked into the compressor (11) again.
  • the high-pressure refrigerant after passing through the indoor heat exchanger (22) does not flow, and the low-pressure refrigerant after passing through the outdoor heat exchanger (21) and the receiver (21). Since only flows through the second flow path (28), the temperature of the high-pressure refrigerant does not change. As a result, the high-pressure refrigerant flows into the expander (12) without being cooled.
  • the internal heat exchanger (23) functions only during the cooling operation, so During the cell operation, the high-pressure refrigerant sucked into the expander (12) can be cooled, and the inflow refrigerant density de of the expander (12) can be increased.
  • the refrigerant mass flow rate Mc of the compressor (11) becomes larger than the refrigerant mass flow rate Me of the expander (12), whereas the expander (12) Since the refrigerant mass flow rate Me can be increased, the refrigerant mass flow rates Mc and Me of both can be balanced.
  • the refrigerant mass flow rate Me, Mc is balanced without bypassing a part of the refrigerant from the expander (12). By introducing it, it is possible to avoid a drop in COP.
  • the second modification of the tenth embodiment is an example in which the refrigerant bypasses the internal heat exchange (23) in the refrigerant circuit (10) of the tenth embodiment shown in FIG.
  • the first on-off valve (SV1) is not provided between the first flow paths (27) of (23), and the refrigerant shown in FIG. 13 is used for bypassing the first flow path (27) by the refrigerant during heating operation. There is no bypass passage (high-pressure side no-pass passage) (45).
  • the first on-off valve (SV1) is provided between the fourth port (P4) of the first four-way selector valve (31) and the second flow path (28) of the internal heat exchanger (23). ing.
  • the pipe between the 4th port (P4) of the first four-way selector valve (31) and the first on-off valve (SV1) has a bypass passage (low-pressure side bypass passage) having a second on-off valve (SV2).
  • One end of (46) is connected.
  • the other end of the bypass passage (46) joins a pipe connecting the second flow path (28) of the internal heat exchanger (23) and the suction side of the compressor (11).
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state shown by the solid line in FIG.
  • the first on-off valve (SV1) is opened and the second on-off valve (SV2) is closed.
  • the refrigerant from which the compressor (11) force is also discharged includes the first four-way switching valve (31), the outdoor heat exchanger (21), the second four-way switching valve (32), the internal heat exchanger (23 ) First flow path (27), expander (12), second four-way selector valve (32), indoor heat exchange (22), first four-way selector valve (31), internal heat exchanger (23 ) Through the second flow path (28) in order, and again sucked into the compressor (11).
  • the high-pressure refrigerant after passing through the outdoor heat exchanger (21) flows through the first flow path (27) and passes through the indoor heat exchanger (22). Since the low-pressure refrigerant flows through the second flow path (28), the high-pressure refrigerant and the low-pressure refrigerant exchange heat. As a result, the high-pressure refrigerant is cooled by the internal heat exchange (23) and flows into the power expander (12).
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state shown by the broken line in FIG.
  • the first on-off valve (SV1) is closed and the second on-off valve (SV2) is opened.
  • the refrigerant from which the compressor (11) force is also discharged includes the first four-way switching valve (31), the indoor heat exchanger (22), the second four-way switching valve (32), the internal heat exchanger (23 ) First flow path (27), expander (12), second four-way selector valve (32), outdoor heat exchanger (21), first four-way selector valve (31), bypass passage (46) In order and again sucked into the compressor (11).
  • the high-pressure refrigerant after passing through the indoor heat exchanger (22) flows through the first flow path (27), but after passing through the outdoor heat exchange (21). Because the low-pressure refrigerant does not flow! / ⁇ , the temperature of the high-pressure refrigerant does not change. As a result, the high-pressure refrigerant flows into the expander (12) without being cooled.
  • the internal heat exchanger (23) functions only during the cooling operation, so that during the cooling operation, the high-pressure refrigerant sucked into the expander (12) can be cooled, and the expander (12 ) Inflow refrigerant density de can be increased.
  • the refrigerant mass flow rate Mc of the compressor (11) becomes larger than the refrigerant mass flow rate Me of the expander (12), whereas the expander (12) Since the refrigerant mass flow rate Me can be increased, the refrigerant mass flow rates Mc and Me of both can be balanced.
  • the refrigerant mass flow rate Me, Mc is balanced without bypassing a part of the refrigerant from the expander (12). By introducing it, it is possible to avoid a drop in COP.
  • a third modification of the tenth embodiment is an example in which the second four-way selector valve (32) is not used in the refrigerant circuit of the tenth embodiment shown in FIG.
  • the second end of the outdoor heat exchanger (21) is the first flow of the third check valve (CV3) and the internal heat exchanger (23).
  • the outflow side of the expander (12) branches into two pipes, one of which is connected between the outdoor heat exchanger (21) and the third check valve (CV3) via the first check valve (C VI)
  • the other end is connected to the first end of the indoor heat exchanger (22) via the second check valve (CV2).
  • One end of a bypass passage (45) having a fourth check valve (CV4) is connected to the pipe between the second check valve (CV2) and the indoor heat exchanger (22).
  • the first check valve (CV1) and the second check valve (CV2) allow the refrigerant to flow out of the expander (12).
  • the open / close state may be switched during cooling operation and heating operation.
  • the third check valve (CV3) and the fourth check valve (CV4) are valves that allow the refrigerant to flow into the expander (12).
  • the first check valve (CV1) and the second check valve As with (CV 2), a solenoid valve can be substituted!
  • the first four-way selector valve (31) switches to the state shown by the solid line in FIG. In this state, the refrigerant from which the compressor (11) force is also discharged is the first four-way switching valve (31), the outdoor heat exchanger (21), the third check valve (CV3), the internal heat exchanger (23 ) First flow path (27), expander (12), second check valve (CV2), indoor heat exchanger (22), first four-way selector valve (31), internal heat exchanger (23)
  • the second flow path (28) flows in order and is sucked into the compressor (11) again.
  • the high-pressure refrigerant after passing through the outdoor heat exchanger (21) flows through the first flow path (27) and passes through the indoor heat exchanger (22). Since the low-pressure refrigerant flows through the second flow path (28), the high-pressure refrigerant and the low-pressure refrigerant exchange heat. As a result, the high-pressure refrigerant is cooled by the internal heat exchange (23) and flows into the power expander (12).
  • the first four-way selector valve (31) switches to the state indicated by the broken line in FIG. In this state, the refrigerant that has also discharged the compressor (11) force is the first four-way switching valve (31), the indoor heat exchange (22), the bypass passage (45) (fourth check valve (CV4)), The expander (12), the first check valve (CV1), the outdoor heat exchanger (21), the first four-way selector valve (31), and the second flow path (28) of the internal heat exchanger (23) in this order It flows and is sucked into the compressor (11) again.
  • the refrigerant that has also discharged the compressor (11) force is the first four-way switching valve (31), the indoor heat exchange (22), the bypass passage (45) (fourth check valve (CV4)), The expander (12), the first check valve (CV1), the outdoor heat exchanger (21), the first four-way selector valve (31), and the second flow path (28) of the internal heat exchanger (23) in this order It flows and is sucked into the compressor (11) again.
  • the high-pressure refrigerant after passing through the indoor heat exchanger (22) flows. Since the low-pressure refrigerant after passing through the outdoor heat exchanger (21) flows through the second flow path (28), the temperature of the high-pressure refrigerant does not change. As a result, the high-pressure refrigerant flows into the expander (12) without being cooled.
  • the refrigerant mass flow rate Me, Mc is balanced without bypassing a part of the refrigerant from the expander (12). By introducing it, it is possible to avoid a drop in COP.
  • the high-pressure refrigerant flows through the internal heat exchanger (23) in the opposite direction to the low-pressure refrigerant during the cooling operation.
  • the second port (P2) of the second four-way selector valve (32) is opposite to the example of FIG. ) Is connected to the right end of the figure.
  • the left end of the first flow path (27) of the internal heat exchanger (23) in the drawing is connected to the inflow side of the expander (12) via the first on-off valve (SV1).
  • the bypass passage (45) having the second on-off valve (SV2) is connected to the pipe between the second port (P2) of the second four-way selector valve (32) and the internal heat exchanger (23), and 1 Connected to the pipe between the open / close valve (SV1) and the expander (12).
  • Embodiment 11 differs from Embodiments 9 and 10 in the configuration of the refrigerant circuit (10). It will be.
  • the discharge side of the compressor (11) is connected to the first port (P1) of the first four-way switching valve (31), and the first four-way switching valve (31 )
  • Second port (P2) is connected to the first end of the outdoor heat exchanger (21).
  • the second end of the outdoor heat exchanger (21) is connected to the first port (P1) of the second four-way selector valve (32), and the second port (P2) of the second four-way selector valve (32) is internal. It is connected to the inflow side of the expander (12) via the first flow path (27) of the heat exchanger (23).
  • the outflow side of the expander (12) is connected to the third port (P3) of the first four-way selector valve (31), and the fourth port (P4) of the first four-way selector valve (31) Connected to the first end of the heat exchanger (22)!
  • the second end of the indoor heat exchanger (22) is connected to the third port (P3) of the second four-way selector valve (32), and the fourth port (P4) of the second four-way selector valve (32) is It is connected to the suction side of the compressor (11) via the second flow path (28) of the internal heat exchanger (23).
  • a first on-off valve (S1) is provided between the second flow path (28) of the internal heat exchanger (23) and the suction side of the compressor (11).
  • the piping between the fourth port (P4) of the second four-way selector valve (32) and the second flow path (28) of the internal heat exchange (23), the first on-off valve (SV1) and the compressor A bypass passage (46) having a second on-off valve (SV2) is connected to the pipe between the suction sides of (11).
  • the first port (P1) communicates with the second port (P2) and the third port (P3) Is in communication with the fourth port (P4) (shown by the solid line in FIG. 18), the first port (P1) is in communication with the fourth port (P4), and the second port (P2) is in the third port. Switch to the state of communication with (P3) (the state indicated by the broken line in FIG. 18).
  • a receiver may be provided between the outlet side of the expander (12) and the low pressure side of the evaporator and the internal heat exchanger (23)!
  • a high-pressure side bypass passage (45) may be provided !, and the flow of high-pressure refrigerant and low-pressure refrigerant during cooling operation in the internal heat exchange (23) You can make it.
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state shown by the solid line in FIG.
  • the first on-off valve (SV1) is opened and the second on-off valve (SV2) is closed.
  • the refrigerant from which the compressor (11) force is also discharged includes the first four-way switching valve (31), the outdoor heat exchanger (21), the second four-way switching valve (32), the internal heat exchanger (23 ) First flow path (27), expander (12), first four-way selector valve (31), indoor heat exchange (22), second four-way selector valve (32), internal heat exchanger (23 ) Through the second flow path (28) in order, and again sucked into the compressor (11).
  • the high-pressure refrigerant after passing through the outdoor heat exchanger (21) flows through the first flow path (27) and passes through the indoor heat exchanger (22). Since the low-pressure refrigerant flows through the second flow path (28), the high-pressure refrigerant and the low-pressure refrigerant exchange heat. As a result, the high-pressure refrigerant is cooled by the internal heat exchange (23) and flows into the power expander (12).
  • the first four-way selector valve (31) and the second four-way selector valve (32) are switched to the state shown by the broken line in FIG.
  • the first on-off valve (SV1) is closed and the second on-off valve (SV2) is opened.
  • the refrigerant from which the compressor (11) force is also discharged includes the first four-way switching valve (31), the indoor heat exchanger (22), the second four-way switching valve (32), the internal heat exchanger (23 ) First flow path (27), expander (12), first four-way selector valve (31), outdoor heat exchanger (21), second four-way selector valve (32), bypass passage (46) In order and again sucked into the compressor (11).
  • the high-pressure refrigerant after passing through the indoor heat exchanger (22) flows through the first flow path (27), but after passing through the outdoor heat exchanger (21). Since the low-pressure refrigerant does not flow through the second flow path (28), the temperature of the high-pressure refrigerant does not change. As a result, the high-pressure refrigerant flows into the expander (12) without being cooled.
  • the internal heat exchanger (23) functions only during the cooling operation, the high-pressure refrigerant sucked into the expander (12) can be cooled during the cooling operation, and the inflow of the expander (12) The refrigerant density de can be increased.
  • the refrigerant mass flow rate Mc of the compressor (11) becomes larger than the refrigerant mass flow rate Me of the expander (12), whereas the expander (12) Since the refrigerant mass flow rate Me can be increased, the refrigerant mass flow rates Mc and Me of both can be balanced.
  • Embodiment 12 The refrigeration apparatus of Embodiment 12 is applied to the air conditioner (1).
  • This air conditioner (1) This air conditioner (1)
  • the indoor cooling operation and the heating operation can be switched.
  • the air conditioner (1) includes a refrigerant circuit (10).
  • a vapor compression refrigeration cycle is performed by circulating the refrigerant.
  • CO 2 carbon dioxide
  • the refrigerant circuit (10) includes a compressor (11), an expander (12), outdoor heat exchange (21), indoor heat exchange (22), a gas-liquid separator (51), 1 Four-way selector valve (31) and second four-way selector valve (32) are connected.
  • the compressor (11) and the expander (12) are each composed of a rotary piston type fluid machine having a unique cylinder volume.
  • the compressor (11) and the expander (12) are connected to each other by the rotating shaft of the motor (13).
  • the compressor (11) is rotationally driven by both power (expansion power) obtained by expansion of the refrigerant in the expander (12) and power obtained by energizing the motor (13).
  • the compressor (11) and the expander (12) are connected to the rotating shaft, their rotational speeds are always equal. Therefore, in the refrigerant circuit (10), the volume circulation amount Ve of refrigerant passing through the expander (12) and the compressor (1
  • the ratio (VeZVc) of the volume circulation volume Vc of the refrigerant passing through I) is a fixed value determined by the cylinder volume ratio of each fluid machine (11, 12).
  • the cylinder volume ratio is the ratio of the above VeZV c, the refrigerant density de of the suction of the expander (12) when the air conditioner (1) is heated, and the compressor (
  • the density ratio deZdc with the suction refrigerant density dc of II) is equal, that is, the mass flow rate Me of refrigerant passing through the expander (12) and the mass flow rate Mc of refrigerant passing through the compressor (11) are Designed to be equal.
  • the outdoor heat exchange (21) and the indoor heat exchange (22) are composed of so-called cross fin type fin 'and' tube heat exchanges. Outdoor air is blown to the outdoor heat exchanger (21) by a fan outside the figure. In this outdoor heat exchange (21), heat is exchanged between the outdoor air and the refrigerant. On the other hand, the indoor heat exchanger (22) is connected to the room by a fan (not shown). Inside air is blown. In the indoor heat exchanger (22), heat is exchanged between the indoor air and the refrigerant.
  • a gas-liquid separator (51) is connected to the discharge side of the expander (12)!
  • the gas-liquid separator (51) is a sealed container that separates the two-phase refrigerant expanded by the expander (12) into liquid refrigerant and gas refrigerant.
  • a liquid storage part (52) for storing the separated liquid refrigerant is formed in the lower space
  • a gas storage part (53) for storing the separated gas refrigerant is formed in the upper space. Is formed.
  • the liquid storage part (52) of the gas-liquid separator (51) is connected to the separation liquid pipe (54), while the gas-liquid gas storage part (53) has a separation gas pipe ( 55) is connected!
  • the separation liquid pipe (54) is a pipe that sends the liquid refrigerant separated by the gas-liquid separator (51) to the second four-way switching valve (32).
  • the separation gas pipe (55) is a so-called gas injection pipe (first injection pipe) that sends the gas refrigerant separated by the gas-liquid separator (51) to the suction side of the compressor (11).
  • the separation gas pipe (55) is provided with a gas control valve (38) for adjusting the flow rate of the gas refrigerant sent to the suction side of the compressor (11).
  • the gas-liquid separator (51) is provided with a heat transfer tube (50) penetrating the inside of the gas-liquid separator (51) so as to be adjacent to the liquid reservoir (52). .
  • One end of the heat transfer tube (50) is connected to one end of the outdoor heat exchange (21), and the other end is connected to the second four-way switching valve (32).
  • the heat transfer tube (50) constitutes an internal heat exchange unit that exchanges heat between the liquid refrigerant in the liquid storage unit (52) and the refrigerant in the heat transfer tube.
  • the first four-way selector valve (31) and the second four-way selector valve (32) each have first to fourth ports.
  • the first four-way selector valve (31) has a first port (P1) connected to the discharge side of the compressor (11), a second port (P2) connected to the other end of the outdoor heat exchanger (21), The third port (P3) is connected to the suction side of the compressor (11), and the fourth port (P4) is connected to one end of the indoor heat exchanger (22).
  • the first port (P1) is connected to the liquid storage part (52) of the gas-liquid separator (51) via the separation liquid pipe (54).
  • the port (P2) is connected to the heat transfer tube (50) of the gas-liquid separator (51), the third port (P3) is connected to the suction side of the expander (12), and the fourth port (P4) is indoor heat Connect to the other end of the exchanger (22)!
  • the first and second four-way selector valves (31, 32) communicate the first port (P1) and the second port (P2).
  • the first port (P3) and the fourth port (P4) are connected to the first port (P3) and the fourth port (P4).
  • the second port (P2) and the third port (P3) can be switched to the second state (shown by the broken line in FIG. 19).
  • the first four-way switching valve (31) constitutes a refrigerant mechanism that switches the circulation direction of the cooling medium in order to switch between the cooling operation and the heating operation.
  • the second four-way selector valve (32) constitutes a heat exchange amount adjustment mechanism (60) that changes the heat exchange amount of the refrigerant in the internal heat exchange section (50), and is used during the cooling operation of the air conditioner (1). Only the heat exchange of the refrigerant in the heat transfer tube (50) is allowed.
  • the first four-way selector valve (31) is set to the first state
  • the second four-way selector valve (32) is set to the second state.
  • the motor (13) is energized in this state
  • the refrigerant circulates in the refrigerant circuit (10) and a refrigeration cycle is performed.
  • the outdoor heat exchanger (21) serves as a heat radiator
  • the indoor heat exchanger (22) serves as an evaporator.
  • the high pressure of the refrigeration cycle is set higher than the critical pressure of carbon dioxide, which is a refrigerant.
  • the high-pressure refrigerant radiated by the outdoor heat exchanger (21) flows through the heat transfer tube (50) of the gas-liquid separator (51). At this time, the high-pressure refrigerant is cooled by exchanging heat with the liquid refrigerant stored in the liquid storage section (52) of the gas-liquid separator (51).
  • the high-pressure refrigerant that has flowed out of the heat transfer tube (50) flows into the expander (12) through the second four-way switching valve (32).
  • the expander (12) the high-pressure refrigerant expands, and the internal energy of the high-pressure refrigerant is converted into the rotational power of the compressor D. Due to the expansion in the expander (12), the pressure of the high-pressure refrigerant decreases and changes from a supercritical state to a gas-liquid two-layer state.
  • the low-pressure refrigerant decompressed by the expander (12) flows into the container of the gas-liquid separator (51). spirit In the liquid separator (51), the low-pressure refrigerant in a gas-liquid two-phase state is separated into a liquid refrigerant and a gas refrigerant.
  • the low-pressure liquid refrigerant stored in the liquid storage part (52) is heated by heat exchange with the high-pressure refrigerant flowing through the heat transfer pipe (50).
  • the low-pressure gas refrigerant stored in the gas storage part (53) passes through the separation gas pipe (55), and the compressor (11) when the gas control valve (38) is appropriately opened at a predetermined opening. It is returned to the suction side.
  • the low-pressure liquid refrigerant in the liquid storage section (52) flows into the indoor heat exchanger (22) after passing through the separation liquid pipe (54) and the second four-way selector valve (32).
  • indoor heat exchange (22) the low-pressure refrigerant absorbs heat from the indoor air and evaporates.
  • room air cooled by the low-pressure refrigerant is supplied into the room.
  • the low-pressure refrigerant evaporated in the indoor heat exchanger (22) passes through the first four-way switching valve (31) and is sucked into the compressor (11).
  • the first four-way selector valve (31) is set to the second state, and the second four-way selector valve (32) is set to the first state.
  • the motor (13) is energized in this state, the refrigerant circulates in the refrigerant circuit (10) and a refrigeration cycle is performed.
  • the indoor heat exchanger (22) serves as a heat radiator, and the outdoor heat exchanger (21) serves as an evaporator.
  • the high pressure of the refrigeration cycle is set higher than the critical pressure of carbon dioxide, which is a refrigerant, as in the cooling operation.
  • the high pressure refrigerant in the supercritical state is discharged from the compressor (11).
  • This high-pressure refrigerant flows into the indoor heat exchanger (22) through the first four-way selector valve (31).
  • the indoor heat exchanger (22) the high-pressure refrigerant radiates heat to the indoor air. At this time, indoor air heated by the high-pressure refrigerant is supplied indoors.
  • the high-pressure refrigerant expands, and the internal energy of the high-pressure refrigerant is converted into the rotational power of the compressor (11). Due to the expansion in the expander (12), the pressure of the high-pressure refrigerant drops and changes to a supercritical state gas-liquid two-layer state.
  • the low-pressure refrigerant decompressed by the expander (12) flows into the container of the gas-liquid separator (51).
  • the gas-liquid separator (51) the low-pressure refrigerant in the gas-liquid two-phase state is separated into liquid refrigerant and gas refrigerant.
  • the low-pressure liquid refrigerant stored in the liquid storage section (52) flows through the heat transfer pipe (50) after passing through the separation liquid pipe (54) and the second four-way switching valve (32). At this time, the liquid refrigerant and heat transfer tube (50) in the liquid storage section (52)
  • the liquid refrigerant in the inside is substantially isothermal and therefore hardly undergoes heat exchange.
  • the gas-liquid separator (51) is provided with the heat transfer tube (50) as an internal heat exchange part. Then, by switching the second four-way selector valve (32), the refrigerant that flows through the heat transfer tube (50) and is sucked into the expander (12), and the liquid refrigerant separated by the gas-liquid separator (51) Heat exchange only during cooling operation. For this reason, during the cooling operation, the refrigerant sucked into the expander (12) can be cooled, and the sucked refrigerant density de of the expander (12) can be increased.
  • the gas-liquid separator (51) also serves as the internal heat exchanger (50)
  • the gas-liquid separator (51) and the internal heat exchanger (50) are individually provided. Compared to the case of refrigeration
  • the device can be compact.
  • the gas refrigerant separated by the gas-liquid separator (51) is sent to the suction side of the compressor (11) so as to perform so-called gas injection. Therefore, the degree of superheat of the refrigerant sucked in the compressor (11) can be adjusted, and the optimum refrigeration cycle can be controlled in this refrigeration apparatus.
  • Embodiment 12 a refrigeration apparatus according to a modification of Embodiment 12 will be described.
  • the refrigeration apparatus of this modified example is provided with a plurality of indoor heat exchangers that are the use side heat exchangers of the air conditioner (1). That is, the refrigeration apparatus of this modification is applied to a multi-type air conditioner.
  • the differences from Embodiment 12 will be described below.
  • First to third indoor heat exchangers (22a, 22b, 22c) are connected in parallel to the refrigerant circuit (10) of this modification.
  • Each indoor heat exchanger (22a, 22b, 22c) is provided with a fan (not shown), and the indoor air is sent to each indoor heat exchanger (22a, 22b, 22c) by the corresponding fan. It is being blown.
  • the refrigerant circuit (10) is provided with first to third flow rate adjustment valves (61a, 61b, 61c) corresponding to the indoor heat exchangers (22a, 22b, 22c).
  • Each flow rate adjusting valve (61a, 61b, 61c) is configured to be able to adjust the flow rate of the refrigerant flowing into each indoor heat exchanger (22a, 22b, 22c).
  • the refrigerant flows branched into ⁇ a plurality of indoor heat exchange m (22a, 22b, 22 C ), except that again if flow, the same as in Embodiment 12 It has become.
  • the refrigerant sucked into the expander (12) is cooled by exchanging heat of the refrigerant in the heat transfer tube (50) during the cooling operation, and the sucked refrigerant density of the expander (12) is reduced. de can be increased. Therefore, the refrigerant mass flow rates (Mc and Me) of the compressor (11) and the expander (12) can be balanced, and a desired refrigeration cycle can be performed in the refrigerant circuit (10).
  • this refrigeration apparatus can be applied to a so-called multi-type air conditioner (1). Furthermore, since the flow rate of refrigerant flowing into each indoor heat exchanger (22a, 22b, 22c) can be adjusted by each flow control valve (61a, 61b, 61c), the cooling of each indoor heat exchanger (22a, 22b, 22c) Individually adjusting capacity and heating capacity Can do.
  • the liquid refrigerant separated in the gas-liquid separator (51) can be sent to each indoor heat exchanger m ⁇ (22a, 22b, 22 C ), so it can be compared with, for example, a refrigerant in a two-phase state or a gas state.
  • the flow rate adjustment in the flow rate adjustment valves (61a, 61b, 61c) can be easily performed.
  • the connecting pipe between the indoor heat exchanger ⁇ (22a, 22b, 22c) and the outdoor heat exchanger ⁇ (21) tends to be long.
  • the pressure loss of the refrigerant increases and the refrigerant passing sound that occurs at this time tends to become noise.
  • the liquid refrigerant separated by the gas-liquid separator (51) can be circulated through the communication pipe, the pressure loss and noise as described above can be effectively reduced.
  • Embodiment 13 The refrigeration apparatus of Embodiment 13 is different from the refrigeration apparatus of Embodiment 12 in the configuration of the refrigerant circuit (10). Hereinafter, differences from Embodiment 12 will be described.
  • the refrigerant circuit (10) includes a compressor (11), an expander as in the twelfth embodiment.
  • one end of the heat transfer tube (50) is connected to the suction side of the expander (12) and the other end is a liquid inflow tube (56 ) Is connected to the second four-way selector valve (33).
  • the liquid inflow pipe (56) is provided with a first electromagnetic on-off valve (34) that allows or prohibits the refrigerant flowing through the heat transfer pipe (50).
  • one end of a bypass pipe (57) is connected between the first electromagnetic on-off valve (34) and the second four-way switching valve (33). The other end of the bypass pipe (57) is connected to the suction side of the expander (12).
  • the bypass pipe (57) causes the refrigerant to be sucked into the expander (12) by bypassing the heat transfer pipe (50). Further, the bypass pipe (57) is provided with a second electromagnetic on-off valve (35) that allows or prohibits the refrigerant flow in the bypass pipe (57).
  • the bypass pipe (57) and the first and second electromagnetic on-off valves (34, 35) have a heat exchange amount adjusting mechanism (60) that changes the heat exchange amount of the refrigerant in the heat transfer pipe (50). ) And heat exchange of the refrigerant in the heat transfer tube (50) is performed only during the cooling operation of the air conditioner (1).
  • the first port (P1) is connected to the discharge side of the compressor (11), and the second port (P2) is the outdoor heat.
  • the third port (P3) connected to the suction side of the compressor (11), and the fourth port (P4) connected to one end of the indoor heat exchanger (22) Yes.
  • the first port (P1) is connected to the liquid reservoir (52) of the gas-liquid separator (51) via the separation liquid pipe (54), and the second port (P2) is connected to the other end of the outdoor heat exchanger (21), and the third port (P3) is connected to the heat transfer pipe (50) of the gas-liquid separator (51) via the liquid inflow pipe (56).
  • the 4th port (P4) is connected to the other end of the indoor heat exchanger (22).
  • the first and second four-way selector valves (31, 33) are configured to be switchable between the first and second states, as in the twelfth embodiment.
  • the first and second four-way switching valves (31, 33) constitute a refrigerant switching mechanism for switching the refrigerant circulation direction in order to switch between the cooling operation and the heating operation.
  • the first four-way selector valve (31) is set to the first state, and the second four-way selector valve (33) is set to the second state. Further, the first electromagnetic on-off valve (34) is opened, and the second electromagnetic on-off valve (35) is closed.
  • the motor (13) is energized in this state, the refrigerant circulates in the refrigerant circuit (10) to perform a refrigeration cycle.
  • the outdoor heat exchanger (21) serves as a radiator and the indoor heat exchanger (22) serves as an evaporator.
  • the high pressure of the refrigeration cycle is set higher than the critical pressure of carbon dioxide, which is a refrigerant.
  • the high-pressure refrigerant radiated by the outdoor heat exchanger (21) passes through the second four-way switching valve (33) and the liquid inflow pipe (56) and then flows through the heat transfer pipe (50). At this time, the high-pressure refrigerant is cooled by exchanging heat with the liquid refrigerant stored in the liquid storage section (52) of the gas-liquid separator (51). The high-pressure refrigerant that has flowed out of the heat transfer tube (50) flows into the expander (12). In the expander (12), the high-pressure refrigerant expands, The internal energy of the refrigerant is converted into the rotational power of the compressor (11). Due to the expansion in the expander (12), the pressure of the high-pressure refrigerant decreases and changes from a supercritical state to a gas-liquid two-layer state.
  • the low-pressure refrigerant decompressed by the expander (12) flows into the container of the gas-liquid separator (51).
  • the gas-liquid separator (51) the low-pressure refrigerant in the gas-liquid two-phase state is separated into liquid refrigerant and gas refrigerant.
  • the low-pressure liquid refrigerant stored in the liquid storage part (52) is heated by heat exchange with the high-pressure refrigerant flowing through the heat transfer pipe (50).
  • the low-pressure gas refrigerant stored in the gas storage part (53) passes through the separation gas pipe (55), and the compressor (11) when the gas control valve (38) is appropriately opened at a predetermined opening. It is returned to the suction side.
  • the low-pressure liquid refrigerant in the liquid storage section (52) flows into the indoor heat exchanger (22) after passing through the separation liquid pipe (54) and the second four-way selector valve (33).
  • indoor heat exchange (22) the low-pressure refrigerant absorbs heat from the indoor air and evaporates.
  • room air cooled by the low-pressure refrigerant is supplied into the room.
  • the low-pressure refrigerant evaporated in the indoor heat exchanger (22) passes through the first four-way switching valve (31) and is sucked into the compressor (11).
  • the first four-way selector valve (31) is set to the second state, and the second four-way selector valve (33) is set to the first state. Further, the first electromagnetic on-off valve (34) is closed, and the second electromagnetic on-off valve (35) is opened.
  • the motor (13) is energized in this state, the refrigerant circulates in the refrigerant circuit (10) to perform a refrigeration cycle.
  • the indoor heat exchanger (22) serves as a radiator and the outdoor heat exchanger (21) serves as an evaporator.
  • the high pressure of the refrigeration cycle is set higher than the critical pressure of carbon dioxide, which is a refrigerant, as in the cooling operation.
  • the high pressure refrigerant in the supercritical state is discharged from the compressor (11).
  • This high-pressure refrigerant flows into the indoor heat exchanger (22) through the first four-way selector valve (31).
  • the indoor heat exchanger (22) the high-pressure refrigerant radiates heat to the indoor air. At this time, indoor air heated by the high-pressure refrigerant is supplied indoors.
  • the high-pressure refrigerant radiated by the indoor heat exchanger (22) flows into the expander (12) through the second four-way switching valve (33) and the bypass pipe (57).
  • the high-pressure refrigerant expands, and the internal energy of the high-pressure refrigerant is converted into the rotational power of the compressor D. Due to the expansion in the expander (12), the pressure of the high-pressure refrigerant decreases and changes from a supercritical state to a gas-liquid two-layer state.
  • the low-pressure refrigerant decompressed by the expander (12) flows into the container of the gas-liquid separator (51).
  • the low-pressure refrigerant in the gas-liquid two-phase state is separated into liquid refrigerant and gas refrigerant.
  • the liquid refrigerant in the liquid reservoir (52) is not subjected to heat exchange.
  • the low-pressure liquid refrigerant in the liquid storage section (52) flows into the outdoor heat exchanger (21) after passing through the separation liquid pipe (54) and the second four-way switching valve (33).
  • the low-pressure refrigerant absorbs heat from the outdoor air and evaporates.
  • the low-pressure refrigerant evaporated in the outdoor heat exchanger (21) passes through the first four-way switching valve (31) and is sucked into the compressor (11).
  • Embodiment 13 the state of the first and second electromagnetic on-off valves (34, 35) is switched so that the heat exchange of the refrigerant is performed by the heat transfer tube (50) only during the cooling operation.
  • the suction refrigerant density de of the expander (12) is increased. Therefore, the refrigerant mass flow rates (Mc and Me) of the compressor (11) and the expander (12) can be balanced, and a desired refrigeration cycle can be performed in the refrigerant circuit (10).
  • the refrigeration apparatus of Modification 1 is provided with first and second motor-operated valves (36, 37) instead of the first and second electromagnetic on-off valves (34, 35) of Embodiment 13. It is. Hereinafter, differences from the embodiment 13 will be described.
  • the liquid inflow pipe (56) is provided with a first motor-operated valve (36) whose opening is variable.
  • the first motor-operated valve (36) is configured to be able to adjust the flow rate of the refrigerant flowing through the heat transfer tube (50).
  • the bypass pipe (57) is provided with a second motor-operated valve (37) having a variable opening.
  • the second motor operated valve (37) is configured to be able to adjust the refrigerant flow rate of the bypass pipe (57).
  • the bypass pipe (57) and the first and second motor-operated valves (36, 37) constitute a heat exchange amount adjusting mechanism (60) that changes the heat exchange amount of the refrigerant in the heat transfer pipe (50).
  • the flow rate of the refrigerant flowing through the heat transfer tube (50) is adjusted by adjusting the opening degree of the first and second motor operated valves (36,37), and the heat transfer tube (50) It is possible to adjust the heat exchange amount of the refrigerant it can. Therefore, the refrigerant mass flow rates (Me and Mc) of the compressor (11) and the expander (12) can be balanced with high accuracy according to the operating conditions.
  • Embodiment 14 Next, the refrigeration apparatus of Embodiment 14 will be described.
  • the refrigeration apparatus of Embodiment 14 is different from the refrigeration apparatus of Embodiment 12 in the configuration of the refrigerant circuit (10). The differences from Embodiment 12 will be described below.
  • the refrigerant circuit (10) of the fourteenth embodiment is provided with a four-way switching valve (31) in the same manner as the first four-way switching valve of the twelfth embodiment.
  • the second four-way switching valve (32) of Embodiment 12 is not provided.
  • the four-way selector valve (31) forms a refrigerant mechanism that switches the refrigerant circulation direction in order to switch between the cooling operation and the heating operation.
  • the outdoor heat exchanger (21) and the indoor heat exchanger (22) are connected by the first pipe (71).
  • the first pipe (71) is provided with a first check valve (81) near the outdoor heat exchanger (21) and a second check valve (82) near the indoor heat exchanger (22). Yes.
  • one end of the liquid inflow pipe (56) is connected between the outdoor heat exchanger (21) and the first check valve (81).
  • the other end of the liquid inflow pipe (56) is connected to one end of the heat transfer pipe (50).
  • the other end of the heat transfer tube (50) is connected to the suction side of the expander (12).
  • the liquid inflow pipe (56) is provided with a third check valve (83).
  • One end of the separation liquid pipe (54) of the present embodiment is connected to the liquid storage section (52) of the gas-liquid separator (51), and the other end is a first check in the first pipe (71). Connected between the valve (81) and the second check valve (82). In the first pipe (71), one end of the second pipe (72) is connected between the second check valve (82) and the indoor heat exchanger (22). The other end of the second pipe (72) is connected to a pipe between the suction side of the expander (12) and the gas-liquid separator (51). The second pipe (72) is provided with a fourth check valve (84).
  • the first check valve (81) only allows the refrigerant to flow from the connection portion of the separation liquid pipe (54) to the connection portion of the liquid inflow pipe (56) in the first pipe (71).
  • the second check valve (82) Only the flow of the propellant refrigerant from the connection of the separation liquid pipe (54) to the connection of the second pipe (72) in the pipe (71) is allowed.
  • the third check valve (83) allows only the flow of the refrigerant toward the first pipe (71) and the heat transfer pipe (50).
  • the fourth check valve (84) allows only the flow of the directional refrigerant to the suction side of the first pipe (71) force expander (12).
  • the refrigerant circuit (10) of the present embodiment forms a circuit similar to a so-called bridge circuit.
  • This circuit constitutes a heat exchange amount adjusting mechanism (60) that changes the heat exchange amount of the refrigerant in the heat transfer tube (50), and the refrigerant flow in the heat transfer tube (50) is only during the cooling operation of the air conditioner (1). Let the heat exchange.
  • the four-way selector valve (31) is set to the first state.
  • the motor (13) is energized in this state, the refrigerant circulates in the refrigerant circuit (10) to perform a refrigeration cycle.
  • the outdoor heat exchanger (21) serves as a radiator, and the indoor heat exchanger (22) serves as an evaporator.
  • the high pressure of the refrigeration cycle is set higher than the critical pressure of carbon dioxide as a refrigerant.
  • the high-pressure refrigerant radiated by the outdoor heat exchanger (21) passes through the third check valve (83) of the liquid inflow pipe (56) and flows through the heat transfer pipe (50). At this time, the high-pressure refrigerant is cooled by exchanging heat with the liquid refrigerant stored in the liquid storage section (52) of the gas-liquid separator (51). The high-pressure refrigerant that has flowed out of the heat transfer tube (50) flows into the expander (12). In the expander (12), the high-pressure refrigerant expands, and the internal energy of the high-pressure refrigerant is converted into the rotational power of the compressor (11). Due to the expansion in the expander (12), the pressure of the high-pressure refrigerant decreases and changes to a supercritical state gas-liquid two-layer state.
  • the low-pressure refrigerant decompressed by the expander (12) flows into the container of the gas-liquid separator (51). this At this time, the gas-liquid two-phase low-pressure refrigerant is separated into a liquid refrigerant and a gas refrigerant.
  • the low-pressure liquid refrigerant stored in the liquid storage section (52) is heated by exchanging heat with the high-pressure refrigerant flowing through the heat transfer pipe (50).
  • the low-pressure gas refrigerant stored in the gas storage section (53) is released from the compressor (11) via the separation gas pipe (55) by appropriately opening the gas control valve (38) at a predetermined opening. It is returned to the suction side.
  • the low-pressure liquid refrigerant in the liquid storage section (52) passes through the second check valve (82) of the first pipe (71) via the separation liquid pipe (54) and passes through the indoor heat exchanger (22). Flow into.
  • indoor heat exchange (22) the low-pressure refrigerant absorbs heat from room air and evaporates. At this time, room air cooled by the low-pressure refrigerant is supplied to the room.
  • the low-pressure refrigerant evaporated in the indoor heat exchanger (22) passes through the four-way switching valve (31) and is sucked into the compressor (11).
  • the four-way selector valve (31) is set to the second state.
  • the motor (13) is energized in this state, the refrigerant circulates in the refrigerant circuit (10) to perform a refrigeration cycle.
  • the indoor heat exchanger (22) serves as a radiator and the outdoor heat exchanger (21) serves as an evaporator.
  • the high pressure of the refrigeration cycle is set higher than the critical pressure of carbon dioxide as a refrigerant, as in the cooling operation.
  • the high pressure refrigerant in the supercritical state is discharged from the compressor (11).
  • This high-pressure refrigerant flows into the indoor heat exchanger (22) through the four-way switching valve (31).
  • indoor heat exchange (22) the high-pressure refrigerant dissipates heat into the room air. At this time, indoor air heated by the high-pressure refrigerant is supplied to the room.
  • the high-pressure refrigerant that has radiated heat in the indoor heat exchanger (22) passes through the first check valve (84) of the second pipe (72) via the first pipe (71) and passes through the expander (12 ).
  • the high-pressure refrigerant expands, and the internal energy of the high-pressure refrigerant is converted into the rotational power of the compressor (11). Due to the expansion in the expander (12), the pressure of the high-pressure refrigerant drops and changes from a supercritical state to a gas-liquid two-layer state.
  • the low-pressure refrigerant decompressed by the expander (12) flows into the container of the gas-liquid separator (51).
  • the gas-liquid separator (51) the low-pressure refrigerant in the gas-liquid two-phase state is separated into liquid refrigerant and gas refrigerant.
  • the liquid refrigerant in the liquid storage section (52) No heat exchange.
  • the low-pressure liquid refrigerant in the liquid storage section (52) passes through the first check valve (81) of the first pipe (72) via the separation liquid pipe (54), and the outdoor heat exchange (21). Flow into.
  • the outdoor heat exchange (21) the low-pressure refrigerant absorbs heat from the outdoor air and evaporates.
  • the low-pressure refrigerant evaporated in the outdoor heat exchanger (21) passes through the four-way switching valve (31) and is sucked into the compressor (11).
  • the heat exchange of the refrigerant is performed by the heat transfer pipe (50) only during the cooling operation by combining the predetermined piping path and the check valve (81, 82, 83, 84).
  • the suction refrigerant density de of the expander (12) is increased. Therefore, the refrigerant mass flow rates (Mc and Me) of the compressor (11) and the expander (12) can be balanced, and a desired refrigeration cycle can be performed in the refrigerant circuit (10).
  • the presence or absence of heat exchange of the refrigerant in the heat transfer pipe (50) is switched according to the switching between the cooling operation and the heating operation only by the switching control of the four-way switching valve (31). Can do. For this reason, the control operation in the refrigerant circuit (10) can be easily performed.
  • the present invention may be configured as follows with respect to the above embodiment.
  • the temperature adjusting means is not limited to the one in which the cooling performance of the refrigerant flowing into the expander (12) changes during the cooling operation and the heating operation, but also when the operation condition of the refrigerant circuit (10) changes. If you want to adjust the temperature of the.
  • Embodiments 12 to 14 the gas refrigerant separated by the gas-liquid separator (51) is separated into the separation gas pipe.
  • a liquid injection pipe for sending the liquid refrigerant separated by the gas-liquid separator (51) to the suction side of the compressor (11) may be provided. Oh ,.
  • FIG. 30 shows the liquid injection pipe (second injection pipe) in the refrigeration apparatus of Embodiment 13.
  • a Yon pipe (59) is provided.
  • One end of this liquid injection pipe (59) is connected to the pipe between the liquid reservoir (52) and the second four-way selector valve (33), and the other end is connected to the suction pipe of the compressor (11). is doing.
  • the liquid injection pipe (59) is provided with a liquid control valve (39) for adjusting the refrigerant flow rate of the liquid injection pipe (59).
  • the liquid refrigerant separated by the gas-liquid separator (51) is supplied to the liquid injection pipe.
  • the force in which the compressor (11) and the expander (12) are constituted by a rotary piston type fluid machine not limited to this, for example, a scroll type, a swing type, a multi-vene It may be configured with a positive displacement fluid machine such as a mold! /, Or a combination of these positive displacement fluid machines (including the rotary piston type).
  • carbon dioxide is used as the refrigerant, but the present invention is not limited to this, and natural refrigerants such as HFC refrigerant, HC refrigerant, water, air, ammonia, and the like may be used. good. Industrial applicability
  • the present invention is useful for a refrigeration apparatus that includes a refrigerant circuit that performs a vapor compression refrigeration cycle and in which an expander that constitutes an expansion mechanism of the refrigerant circuit is mechanically coupled to the compressor. is there.

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  • Engineering & Computer Science (AREA)
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  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
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  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
PCT/JP2005/015862 2004-09-01 2005-08-31 冷凍装置 WO2006025427A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP05776819A EP1795836A1 (en) 2004-09-01 2005-08-31 Refrigerating device
US11/661,383 US20080060365A1 (en) 2004-09-01 2005-08-31 Refrigeration System
AU2005278426A AU2005278426B2 (en) 2004-09-01 2005-08-31 Refrigeration system

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JP2004-254834 2004-09-01

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JP (1) JP2006071174A (ko)
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Publication number Priority date Publication date Assignee Title
EP2034255A1 (en) * 2006-06-21 2009-03-11 Daikin Industries, Ltd. Refrigeration device

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JP4887929B2 (ja) * 2006-06-21 2012-02-29 ダイキン工業株式会社 冷凍装置
JP5120056B2 (ja) * 2008-05-02 2013-01-16 ダイキン工業株式会社 冷凍装置
KR100860819B1 (ko) * 2008-05-08 2008-09-30 충주대학교 산학협력단 냉매 조기 회수를 위한 분기관을 구비한 냉난방장치
JP5180680B2 (ja) * 2008-05-20 2013-04-10 サンデン株式会社 冷凍サイクル
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CN102725599B (zh) * 2010-01-29 2014-11-26 大金工业株式会社 热泵系统
CN102822609B (zh) * 2010-03-25 2014-12-31 三菱电机株式会社 冷冻循环装置及其运转方法
JPWO2011161953A1 (ja) * 2010-06-23 2013-08-19 パナソニック株式会社 冷凍サイクル装置
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US20080060365A1 (en) 2008-03-13
AU2005278426B2 (en) 2008-09-04
KR20070046974A (ko) 2007-05-03
CN100465550C (zh) 2009-03-04
CN101002059A (zh) 2007-07-18
AU2005278426A1 (en) 2006-03-09

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