EP1992887A1 - Dispositif de réfrigération - Google Patents

Dispositif de réfrigération Download PDF

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Publication number
EP1992887A1
EP1992887A1 EP07737771A EP07737771A EP1992887A1 EP 1992887 A1 EP1992887 A1 EP 1992887A1 EP 07737771 A EP07737771 A EP 07737771A EP 07737771 A EP07737771 A EP 07737771A EP 1992887 A1 EP1992887 A1 EP 1992887A1
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EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
intermediate pressure
gas
circuit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP07737771A
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German (de)
English (en)
Other versions
EP1992887A4 (fr
Inventor
Masahiro Yamada
Takahiro Yamaguchi
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Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP1992887A1 publication Critical patent/EP1992887A1/fr
Publication of EP1992887A4 publication Critical patent/EP1992887A4/fr
Withdrawn legal-status Critical Current

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    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/053—Compression system with heat exchange between particular parts of the system between the storage receiver and another part of the system
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • 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
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the present invention relates to a refrigeration system adapted to perform a gas injection operation by supplying gas refrigerant of intermediate pressure to a compressor.
  • Refrigeration systems have been known in the past which perform a so-called gas injection operation (i.e., the operation of supplying gas refrigerant of intermediate pressure to a compressor) for the purpose of reducing the input to the compressor.
  • a so-called gas injection operation i.e., the operation of supplying gas refrigerant of intermediate pressure to a compressor
  • Figure 1 of a patent document JP-A-2001-033117
  • Figure 13 of the patent document another refrigeration system which performs a two-stage compression refrigerating cycle and, in this refrigeration system, gas refrigerant of intermediate pressure is supplied to between a lower stage compressor and a higher stage compressor.
  • gas refrigerant of intermediate pressure In order to perform such a gas injection operation, gas refrigerant of intermediate pressure must be generated.
  • the refrigeration system illustrated in Figure 1 of the patent document is provided in its refrigerant circuit with a gas/liquid separator configured to separate intermediate pressure refrigerant into liquid refrigerant and gas refrigerant, and the gas refrigerant of intermediate pressure is supplied to the compressor from the gas/liquid separator.
  • intermediate pressure refrigerant is made to exchange heat with high pressure liquid refrigerant in an intermediate pressure heat exchanger, whereby the intermediate pressure refrigerant evaporates and changes to gas refrigerant of intermediate pressure.
  • This intermediate pressure gas refrigerant is supplied to the compressor from the intermediate pressure heat exchanger.
  • an air-conditioning system which is a type of refrigeration system is often configured by establishing connection between an outdoor unit and an indoor unit by interconnecting piping.
  • the length of interconnecting piping may reach in some cases a length of about 100 meters.
  • the difference in height between the outdoor unit and the indoor unit may be somewhere between about 20 and about 30 meters.
  • gas refrigerant of intermediate pressure may be in some cases supplied to the compressor from the gas/liquid separator.
  • Liquid refrigerant and gas refrigerant coexist within the gas/liquid separator. That is, liquid refrigerant to be fed out of the gas/liquid separator is in the saturated state.
  • this type of refrigeration system performs an operation of cooling a target object, liquid refrigerant in the saturated state flowing out of the gas/liquid separator is delivered to a utilization side heat exchanger.
  • the utilization side heat exchanger is installed at a far distance from the gas/liquid separator or if the utilization side heat exchanger is installed at a higher position relative to the gas/liquid separator, this causes a pressure drop in the refrigerant during its flow through piping from the gas/liquid separator towards the utilization side heat exchanger, and as a result, a part of the refrigerant may evaporate. This produces the possibility that the amount of liquid refrigerant flowing into the utilization side heat exchanger may decrease, thereby to reduce the cooling capacity to be obtained in the utilization side heat exchanger.
  • intermediate pressure refrigerant may be in some cases made to exchange heat with high pressure liquid refrigerant in the intermediate pressure heat exchanger for supplying of the evaporated intermediate pressure refrigerant from the intermediate pressure heat exchanger to the compressor.
  • this type of refrigeration system performs an operation of heating a target object, a part of the refrigerant condensed in the utilization side heat exchanger is pressure reduced down to an intermediate pressure and is introduced into the intermediate pressure heat exchanger.
  • the intermediate pressure heat exchanger is installed at a far distance from the utilization side heat exchanger or if the intermediate pressure heat exchanger is installed at a higher position relative to the utilization side heat exchanger, this causes a pressure drop in the refrigerant during its flow through piping from the utilization side heat exchanger towards the intermediate pressure heat exchanger, and as a result, a part of the refrigerant may evaporate thereby causing a temperature drop in the refrigerant.
  • an object of the present invention is to enable a refrigeration system adapted to perform a so-called gas injection operation to operate smoothly irrespective of the installation situation or the operation state of the refrigeration system.
  • the present invention provides, as a first aspect, a refrigeration system comprising a refrigerant circuit (20) wherein the refrigerant circuit (20) includes a compressor (31, 34), a heat source side heat exchanger (36) , and a utilization side heat exchanger (71) which are connected to perform a refrigerating cycle, and wherein the refrigerant circuit (20) is selectively operable either in a cooling mode in which the heat source side heat exchanger (36) becomes a condenser and the utilization side heat exchanger (71) becomes an evaporator or a heating mode in which the utilization side heat exchanger (71) becomes a condenser and the heat source side heat exchanger (36) becomes an evaporator.
  • the refrigerant circuit (20) further includes an injection passageway (43) through which to supply to the compressor (31, 34) intermediate pressure refrigerant resulting from pressure reducing a part of high pressure liquid refrigerant, an intermediate pressure heat exchanger (40) in which intermediate pressure refrigerant flowing through the injection passageway (43) towards the compressor (31, 34) exchanges heat with high pressure liquid refrigerant and evaporates, and a gas/liquid separator (51) in which intermediate pressure refrigerant resulting from pressure reducing high pressure liquid refrigerant is separated into liquid refrigerant and gas refrigerant, and the refrigerant circuit (20) is configured such that its refrigerant circulation path is selectively changeable between the cooling mode during which gas refrigerant of intermediate pressure flowing through the injection passageway (43) is supplied to the compressor (31, 34) and the heating mode during which gas refrigerant of intermediate pressure flowing out of the gas/liquid separator (51) is supplied to the compressor (31, 34).
  • the source of intermediate pressure refrigerant to the compressor (31, 34) differs between the cooling mode and the heating mode.
  • intermediate pressure refrigerant evaporated in the intermediate pressure heat exchanger (40) is supplied to the compressor (31, 34) .
  • high pressure liquid refrigerant is cooled by heat exchange with the intermediate pressure refrigerant, thereby increasing the degree of supercooling of the high pressure liquid refrigerant.
  • the present invention provides, as a second aspect according to the aforesaid first aspect, a refrigeration system wherein the refrigerant circuit (20) is formed by connecting, by interconnecting piping (21, 22) , a heat source side circuit (30) in which the compressor (31, 34) and the heat source side heat exchanger (36) are disposed and a utilization side circuit (70) in which the utilization side heat exchanger (71) is disposed, and wherein the injection passageway (43), the intermediate pressure heat exchanger (40) , and the gas/liquid separator (51) are disposed in the heat source side circuit (30).
  • the refrigerant circuit (20) is composed of the heat source side circuit (30) , the utilization side circuit (70), and the interconnecting piping (21, 22).
  • high pressure liquid refrigerant cooled during its passage through the intermediate pressure heat exchanger (40) flows into the utilization side heat exchanger (71) by way of the interconnecting piping (21).
  • the present invention provides, as a third aspect according to the aforesaid first aspect, a refrigeration system wherein the gas/liquid separator (51) is formed by a container-shaped member (65) which is arranged at a position in the refrigerant circuit (20) , which position is located, during the cooling mode, downstream of the heat source side heat exchanger (36) and is located, during the heating mode, downstream of the utilization side heat exchanger (71), and wherein the intermediate pressure heat exchanger (40) is formed by a heat exchange member (66) which is housed in the inside of the container-shaped member (65) and in which intermediate pressure refrigerant flowing through the injection passageway (43) exchanges heat with liquid refrigerant within the container-shaped member (65).
  • the gas/liquid separator (51) is formed by a container-shaped member (65) which is arranged at a position in the refrigerant circuit (20) , which position is located, during the cooling mode, downstream of the heat source side heat exchanger (36) and is located, during the heating mode, downstream of the utilization
  • the gas/liquid separator (51) is formed by the container-shaped member (65) and the intermediate pressure heat exchanger (40) is formed by the heat exchange member (66).
  • refrigerant high pressure liquid refrigerant
  • the heat source side heat exchanger (36) flows into the container-shaped member (65).
  • a part of the high pressure liquid refrigerant flows into the injection passageway (43), is pressure reduced down to an intermediate pressure, and then flows into the heat exchange member (66).
  • the intermediate pressure refrigerant admitted into the heat exchange member (66) exchanges heat with the high pressure liquid refrigerant within the container-shaped member (65), evaporates, and is then supplied to the compressor (31, 34).
  • the high pressure liquid refrigerant within the container-shaped member (65) cooled by heat exchange with the intermediate pressure refrigerant is delivered towards the utilization side heat exchanger (71) from the container-shaped member (65).
  • refrigerant condensed in the utilization side heat exchanger (71) and then pressure reduced down to an intermediate pressure, flows into the container-shaped member (65).
  • the intermediate pressure refrigerant admitted thereinto is separated into liquid refrigerant and gas refrigerant.
  • the liquid refrigerant is delivered towards the heat source side heat exchanger (36) whereas the gas refrigerant is supplied through the injection passageway (43) to the compressor (31, 34).
  • the present invention provides, as a fourth aspect according to the aforesaid first aspect, a refrigeration system wherein a supercooling heat exchanger (60) , configured to cool high pressure liquid refrigerant by heat exchange with low pressure refrigerant resulting from pressure reducing a part of the high pressure liquid refrigerant, is arranged at a position in the refrigerant circuit (20), which position is located, during the cooling mode, downstream of the intermediate pressure heat exchanger (40).
  • a supercooling heat exchanger (60) configured to cool high pressure liquid refrigerant by heat exchange with low pressure refrigerant resulting from pressure reducing a part of the high pressure liquid refrigerant
  • the refrigerant circuit (20) is provided with the supercooling heat exchanger (60) .
  • the supercooling heat exchanger (60) high pressure liquid refrigerant passing through the intermediate pressure heat exchanger (40) is cooled by heat exchange with low pressure refrigerant resulting from pressure reduction of a part of the high pressure liquid refrigerant. That is, the degree of supercooling of the high pressure liquid refrigerant increases.
  • the high pressure liquid refrigerant cooled in the supercooling heat exchanger (60) is delivered to the utilization side heat exchanger (71).
  • the present invention provides, as a fifth aspect according to the aforesaid first aspect, a refrigeration system wherein a single-stage compression refrigerating cycle is performed in the refrigerant circuit (20) , and wherein the compressor (31) is configured such that gas refrigerant of intermediate pressure flows into a compression chamber being in the process of compression.
  • gas refrigerant of intermediate pressure is introduced into the compression chamber being in the process of compression in the compressor (31).
  • the compressor (31) draws in low pressure refrigerant evaporated in either the utilization side heat exchanger (71) or the heat source side heat exchanger (36) , whichever functions as an evaporator, and intermediate pressure refrigerant supplied from either the intermediate pressure heat exchanger (40) or the gas/liquid separator (51), and then compresses them.
  • the present invention provides, as a sixth aspect according to the aforesaid first aspect, a refrigeration system wherein in the refrigerant circuit (20) , a lower stage compressor (33) and a higher stage compressor (34) are connected together in series to perform a two-stage compression refrigerating cycle, and wherein the refrigerant circuit (20) is configured such that gas refrigerant of intermediate pressure is supplied to a suction side of the higher stage compressor (34).
  • gas refrigerant of intermediate pressure is introduced to the suction side of the higher stage compressor (34).
  • the higher stage compressor (34) draws in refrigerant compressed in the lower stage compressor (33) and gas refrigerant supplied from the intermediate pressure heat exchanger (40) and the gas/liquid separator (51) and compresses them.
  • the present invention is arranged such that during the cooling mode, intermediate pressure refrigerant evaporated in the intermediate pressure heat exchanger (40) is supplied to the compressor (31, 34) and high pressure liquid refrigerant cooled in the intermediate pressure heat exchanger (40) is supplied to the utilization side heat exchanger (71).
  • the refrigerant circuit (20) is made up of the heat source side circuit (30), the utilization side circuit (70), and the interconnecting piping (21, 22).
  • the heat source side circuit (30) provided with the intermediate pressure heat exchanger (40) and the gas/liquid separator (51) is arranged at a far distance from the utilization side circuit ( 70 ) provided with the utilization side heat exchanger (71) or these two circuits are positioned at different levels of height.
  • the source of intermediate pressure refrigerant to the compressor (31, 34) is made to differ between the cooling mode and the heating mode, this makes it possible to relax the constraints on the installation situation of the refrigeration system (10).
  • the heat exchange member (66) constituting the intermediate pressure heat exchanger (40) is housed in the inside of the container-shaped member (65) constituting the gas/liquid separator (51) .
  • the container-shaped member (65) with the heat exchange member (66) housed therein is connected to the refrigerant circuit (20) , this is the same as arranging both the gas/liquid separator (51) and the intermediate pressure heat exchanger (40) in the refrigerant circuit (20). Therefore, in accordance with the third aspect of the present invention, the refrigerant circuit (20) can be simplified in configuration in comparison with the case where the gas/liquid separator (51) and the intermediate pressure heat exchanger (40) are formed separately from each other.
  • the supercooling heat exchanger (60) is disposed in the refrigerant circuit (20) thereby increasing the degree of supercooling of high pressure liquid refrigerant to be supplied to the utilization side heat exchanger (71) during the cooling mode.
  • the present embodiment is an air conditioning system (10) formed by a refrigeration system according to the present invention.
  • the air conditioning system (10) of the present embodiment is provided with a single outdoor unit (11) and two indoor units (12) .
  • the outdoor unit (11) accommodates an outdoor circuit (30) which is a heat source side circuit (30) .
  • Each of the indoor units (12) accommodates a respective indoor circuit (70) which is a utilization side circuit.
  • the outdoor circuit (30) and the indoor circuit (70) are connected together by liquid side interconnecting piping (21) and gas side interconnecting piping (22) to form a refrigerant circuit (20) .
  • the two indoor circuits (70) are connected in parallel with each other to the single outdoor circuit (30).
  • Each of the indoor circuits (70) is provided with a respective indoor heat exchanger (71) which is a utilization side heat exchanger and a respective indoor expansion valve (72) .
  • the indoor heat exchanger (71) is an air heat exchanger for heat exchange between indoor air and refrigerant.
  • the indoor heat exchanger (71) and the indoor expansion valve (72) are connected together in series.
  • one end thereof on the side of the indoor expansion valve (72) is connected to the liquid side interconnecting piping (21) and the other end thereof on the side of the indoor heat exchanger (71) is connected to the gas side interconnecting piping (22).
  • the outdoor circuit (30) is provided with a compressor (31) , a four-way selector valve (35), an outdoor heat exchanger (36) which is a heat source side heat exchanger, an outdoor expansion valve (37), and an accumulator (38).
  • the outdoor circuit (30) is provided with an intermediate pressure heat exchanger (40) , a gas/liquid separator ( 51 ), bypass piping (50) , injection piping (43), and intermediate pressure gas piping (52).
  • the compressor (31) is a positive compressor (31) and is configured such that it compresses refrigerant drawn into its compression chamber.
  • the compressor (31) has an intermediate pressure port (32) through which to introduce refrigerant of intermediate pressure into the compression chamber being in the process of compression.
  • the discharge side of the compressor (31) is connected to a first port of the four-way selector valve (35) and the suction side thereof is connected via the accumulator (38) to a second port of the four-way selector valve (35) .
  • a plurality of compressors may be arranged in parallel.
  • the outdoor heat exchanger (36) is an air heat exchanger for heat exchange between outdoor air and refrigerant.
  • the intermediate pressure heat exchanger (40) is a heat exchanger intended for refrigerant to refrigerant heat exchange, such as a double-pipe heat exchanger, a plate type heat exchanger et cetera.
  • Formed in the intermediate pressure heat exchanger (40) are a first flowpath (41) and a second flowpath (42) .
  • One end of the outdoor heat exchanger ( 36 ) is connected to a third port of the four-way selector valve (35) and the other end thereof is connected via the outdoor expansion valve (37) to one end of the first flowpath (41) of the intermediate pressure heat exchanger (40) .
  • the other end of the first flowpath (41) of the intermediate pressure heat exchanger (40) is connected via a first check valve (45) to the liquid side interconnecting piping (21).
  • the first check valve (45) is arranged so that it permits only the flow and passage of refrigerant towards the liquid side interconnecting piping (21) from the intermediate pressure heat exchanger (40).
  • the injection piping (43) forms an injection passageway.
  • the start end of the injection piping (43) is connected to between the intermediate pressure heat exchanger (40) and the first check valve (45) and the termination end thereof is connected to the intermediate pressure port (32) of the compressor (31) .
  • the second flowpath (42) of the intermediate pressure heat exchanger (40) is arranged along the injection piping (43) .
  • the injection piping (43) is provided, between its start end and the second flowpath (42) of the intermediate pressure heat exchanger (40), with an injection expansion valve (44).
  • the gas/liquid separator (51) is a hermetically closed container shaped like a vertically elongated cylinder.
  • the gas/liquid separator (51) has a lower end part arranged along the bypass piping (50).
  • the start end of the bypass piping (50) is connected to between the first check valve (45) and the liquid side interconnecting piping (21), and the terminal end thereof is connected to between the first flowpath (41) of the intermediate pressure heat exchanger (40) and the outdoor expansion valve (37).
  • the bypass piping (50) is provided, between its termination end and the gas/liquid separator (51), with a second check valve (55).
  • the second check valve (55) is arranged such that it permits only the flow and passage of refrigerant in the outflow direction from the gas/liquid separator (51).
  • One end of the intermediate pressure gas piping (52) is connected to the top of the gas/liquid separator (51).
  • the other end of the intermediate pressure gas piping (52) is connected to between the second flowpath (42) of the intermediate pressure heat exchanger (40) and the compressor (31) in the injection piping (43) .
  • a solenoid valve (53) is disposed along the intermediate pressure gas piping (52) .
  • the first port of the four-way selector valve (35) is connected to the discharge side of the compressor (31), the second port is connected to the accumulator (38), and the third port is connected to the outdoor heat exchanger (36) .
  • the fourth port of the four-way selector valve (35) is connected to the gas side interconnecting piping (22).
  • the four-way selector valve (35) is selectively switchable between a first state (shown in Figure 1 ( A )) and a second state (shown in Figure 1 ( B )). That is, when the four-way selector valve (35) is placed in the first state, this establishes fluid communication between the first port and the third port and fluid communication between the second port and the fourth port. On the other hand, when the four-way selector valve (35) is placed in the second state, this establishes fluid communication between the first port and the fourth port and fluid communication between the second port and the third port.
  • the air conditioning system (10) is selectively operable either in a cooling or a heating mode.
  • the four-way selector valve (35) is set in the first state.
  • the outdoor expansion valve (37) is set in the fully opened state, the degree of opening of the injection expansion valve (44) and that of the indoor expansion valve (72) are properly regulated, and the solenoid valve (53) is closed.
  • High pressure gas refrigerant discharged from the compressor (31) dissipates heat to the outdoor air in the outdoor heat exchanger (36) and condenses.
  • This high pressure liquid refrigerant exiting the outdoor heat exchanger (36) passes through the first flowpath (41) of the intermediate pressure heat exchanger (40) during which passage it dissipates heat to the refrigerant in the second flowpath (42).
  • a part of the high pressure liquid refrigerant flowing out of the first flowpath (41) of the intermediate pressure heat exchanger (40) flows into the injection piping (43) whereas the rest of the high pressure liquid refrigerant is distributed to each indoor circuit (70) by way of the liquid side interconnecting piping (21).
  • each indoor circuit (70) the high pressure liquid refrigerant admitted thereinto passes through the indoor expansion valve (72) during which passage it is pressure reduced, absorbs heat from the indoor air in the indoor heat exchanger (71), and evaporates.
  • the refrigerant evaporated in the indoor heat exchanger (71) returns to the outdoor circuit (30) by way of the gas side interconnecting piping (22) and is drawn into the compressor (31) by way of the accumulator (38).
  • the high pressure liquid refrigerant admitted into the injection piping (43) passes through the injection expansion valve (44) during which passage it is pressure reduced down to an intermediate pressure and changes to intermediate pressure refrigerant in the gas/liquid two-phase state.
  • This intermediate pressure refrigerant flows through the second flowpath (42) of the intermediate pressure heat exchanger (40) during which flow it absorbs heat from the refrigerant in the first flowpath (41) and evaporates.
  • the intermediate pressure gas refrigerant exiting the second flowpath (42) of the intermediate pressure heat exchanger (40) is delivered to the intermediate pressure port (32) of the compressor (31).
  • the compressor (31) draws low pressure refrigerant into its compression chamber through the accumulator (38) and compresses it.
  • the intermediate pressure gas refrigerant admitted in through the intermediate pressure port (32) is introduced to the compression chamber being in the process of compression.
  • the compressor (31) compresses the refrigerant in the compression chamber up to a high pressure and discharges it.
  • high pressure liquid refrigerant is cooled during its passage through the intermediate pressure heat exchanger (40) and, as a result, its degree of supercooling increases. Then, the high pressure refrigerant is delivered by way of the liquid side interconnecting piping (21) to the indoor circuit (70) .
  • the high pressure refrigerant flowing into the indoor circuit (70) is maintained in the liquid single-phase state, even in the case where, due to the fact that the liquid side interconnecting piping (21) is more than a certain length or due to the fact that the indoor circuit (70) is positioned higher by a certain height than the outdoor circuit ( 30 ), the liquid refrigerant to be fed into the liquid side interconnecting piping (21) from the outdoor circuit (30) is placed in the saturated state or a part of the high pressure liquid refrigerant evaporates by the time it reaches the indoor circuit (70).
  • the amount of evaporation of the high pressure liquid refrigerant is reduced as compared to the case where the liquid refrigerant to be fed into the liquid side interconnecting piping (21) from the outdoor circuit (30) is in the saturated state.
  • the four-way selector valve (35) is set in the second state.
  • the degree of opening of the outdoor expansion valve (37) and that of the indoor expansion valve (72) are properly controlled.
  • the injection expansion valve (44) is set in the fully closed state and the solenoid valve (53) is opened.
  • High pressure gas refrigerant discharged from the compressor (31) is distributed by way of the gas side interconnecting piping (22) to each indoor circuit (70) .
  • the high pressure gas refrigerant dissipates heat to the indoor air and condenses.
  • the high pressure liquid refrigerant flowing out of the indoor heat exchanger (71) passes through the indoor expansion valve (72) during which passage it is pressure reduced and changes to intermediate pressure refrigerant in the gas/liquid two-phase state.
  • the intermediate pressure refrigerant flowing out of each indoor circuit (70) returns to the outdoor circuit (30) by way of the liquid side interconnecting piping (21) and flows into the gas/liquid separator (51) by way of the bypass piping (50).
  • liquid refrigerant is collected in a lower part of the gas/liquid separator (51) whereas gas refrigerant is collected in an upper part of the gas/liquid separator (51).
  • the liquid refrigerant of intermediate pressure in the gas/liquid separator (51) again flows through the bypass piping (50), passes through the outdoor expansion valve (37) during which passage it is pressure reduced, and is introduced into the outdoor heat exchanger (36).
  • the outdoor heat exchanger (36) the refrigerant absorbs heat from the outdoor air and evaporates.
  • the refrigerant evaporated in the outdoor heat exchanger (36) is drawn by way of the accumulator (38) into the compressor (31).
  • the gas refrigerant of intermediate pressure in the gas/liquid separator ( 51 ) sequentially passes through the intermediate pressure gas piping (52) and the injection piping (43) and is introduced to the intermediate pressure port (32) of the compressor (31).
  • the compressor (31) draws low pressure refrigerant into the compression chamber through the accumulator (38) and compresses it.
  • the intermediate pressure gas refrigerant admitted in through the intermediate pressure port (32) is introduced into the compression chamber being in the process of compression.
  • the compressor (31) compresses the refrigerant in the compression chamber up to a high pressure and discharges it.
  • the refrigerant is introduced into the gas/liquid separator (51) and separated into liquid refrigerant and gas refrigerant, and only the gas refrigerant within the gas/liquid separator (51) is supplied to the intermediate pressure port (32) of the compressor (31).
  • the intermediate pressure port (32) of the compressor (31) is supplied to the compressor (31).
  • intermediate pressure refrigerant evaporated in the intermediate pressure heat exchanger (40) is supplied to the intermediate pressure port (32) of the compressor (31) and high pressure liquid refrigerant cooled in the intermediate pressure heat exchanger (40) is supplied to the indoor circuit (70).
  • the degree of opening of the indoor expansion valve (72) of each indoor circuit (70) is controlled individually to regulate the rate of distribution of the refrigerant to each indoor circuit (70) , in order to properly control the cooling capacity of each indoor unit (12).
  • the indoor expansion valve (72) if the refrigerant passing through the indoor expansion valve (72) enters the gas/liquid two-phase state, then the indoor expansion valve (72) lacks stability in the characteristic of flow rate, thereby producing the possibility that it becomes impossible to properly regulate the rate of distribution of the refrigerant to each indoor circuit (70).
  • the air conditioning system (10) it becomes easy to hold the refrigerant flowing into the indoor circuit (70) during the cooling mode in the liquid state. Therefore, in accordance with the present embodiment, it becomes possible to accurately control, in the air conditioning system (10) provided with a plurality of indoor units (12), the cooling capacity of each indoor unit (12).
  • the second embodiment is an embodiment characterized in that the air conditioning system (10) of the first embodiment additionally includes a supercooling heat exchanger (60) and supercooling piping (63).
  • the difference from the first embodiment in terms of the air conditioning system (10) of the present embodiment is described below.
  • the supercooling heat exchanger (60) is disposed in the outdoor circuit (30).
  • the supercooling heat exchanger (60) is a heat exchanger intended for refrigerant to refrigerant heat exchange, such as a double-pipe heat exchanger, a plate type heat exchanger et cetera.
  • a first flowpath (61) and a second flowpath (62) are formed in the supercooling heat exchanger (60).
  • the first flowpath (61) of the supercooling heat exchanger (60) lies between the intermediate pressure heat exchanger (40) and the first check valve (45) in the outdoor circuit (30).
  • the supercooling piping (63) has a start end and a termination end the former of which is connected to between the supercooling heat exchanger (60) and the first check valve (45) and the latter of which is connected to between the accumulator (38) and the four-way selector valve (35).
  • the second flowpath (62) of the supercooling heat exchanger (60) lies along the supercooling piping (63).
  • the supercooling piping (63) is provided, between its start end and the second flowpath (62) , with a supercooling expansion valve (64).
  • the second embodiment has a refrigerant circulation path which differs from that of the first embodiment only in the following points. That is, high pressure liquid refrigerant leaving the intermediate pressure heat exchanger (40) flows, after passing through the supercooling heat exchanger (60), into the liquid side interconnecting piping (21) and a part of the high pressure liquid refrigerant flows into the supercooling piping (63).
  • the degree of opening of the supercooling expansion valve (54) is properly controlled.
  • High pressure liquid refrigerant flowing out of the first flowpath (41) of the intermediate pressure heat exchanger (40) passes through the first flowpath (61) of the supercooling heat exchanger (60) during which passage it dissipates heat to the refrigerant in the second flowpath (62) .
  • a part of the high pressure liquid refrigerant flowing out of the first flowpath (61) of the supercooling heat exchanger (60) flows into the supercooling piping (63) and the rest of the high pressure liquid refrigerant is distributed by way of the liquid side interconnecting piping (21) to each indoor circuit (70).
  • the high pressure liquid refrigerant cooled in both the intermediate pressure heat exchanger (40) and the supercooling heat exchanger (60) is supplied to each indoor circuit (70).
  • the high pressure liquid refrigerant admitted into the supercooling piping (63) passes through the supercooling expansion valve (64) during which passage it is pressure reduced down to a low pressure and changes to low pressure refrigerant in the gas/liquid two-phase state.
  • This low pressure refrigerant passes through the second flowpath (62) of the supercooling heat exchanger (60) during which passage it absorbs heat from the refrigerant in the first flowpath (61) and evaporates.
  • This low pressure gas refrigerant existing the second flowpath (62) of the supercooling heat exchanger (60) is drawn, together with the low pressure refrigerant returned to the outdoor circuit (30) from the indoor circuit (70) by way of the gas side interconnecting piping (22), into the compressor (31).
  • the supercooling heat exchanger (60) is disposed in the outdoor circuit (30) thereby increasing the degree of supercooling of the high pressure liquid refrigerant to be supplied to the indoor circuit (70) during the cooling mode. Consequently, even in an installation situation that causes a pressure drop in the high pressure refrigerant during its flow from the outdoor circuit (30) to the indoor circuit (70), it is still possible to further ensure that the high pressure refrigerant to be supplied to the indoor circuit (70) is maintained in the liquid state or to further reduce the amount by which the high pressure refrigerant to be supplied to the indoor circuit (70) evaporates along the way thereto.
  • the gas/liquid separator (51) and the intermediate pressure heat exchanger (40) may be made integral with each other.
  • description will be made in terms of an example in which the present modification is applied to the air conditioning system (10) of the second embodiment.
  • the gas/liquid separator (51) of the present modification is formed by a container-shaped member (65) shaped like a somewhat vertically elongated cylinder.
  • the container-shaped member (65) constituting the gas/liquid separator (51) is connected, at its bottom, to a portion of the outdoor circuit (30) between the outdoor expansion valve (37) and the supercooling heat exchanger (60). Note that in the outdoor circuit (30) of the present modification, the bypass piping (50), the first check valve (45) , and the second check valve (55) are omitted.
  • the container-shaped member (65) contains a heat exchange member (66) which is a heat transfer tube shaped like a coil spring.
  • the heat exchange member (66) is arranged in the inner bottom of the container-shaped member (65) so that it is immersed in the liquid refrigerant collected in the container-shaped member (65) .
  • the heat exchange member (66) is arranged upstream of the injection expansion valve (44) in the injection piping (43) .
  • the heat exchange member (66) constitutes the intermediate pressure heat exchanger ( 40 ).
  • refrigerant condensed in the outdoor heat exchanger (36) passes through the outdoor expansion valve (37) in the fully closed state and then flows into the container-shaped member (65).
  • the high pressure liquid refrigerant within the container-shaped member (65) dissipates heat to the intermediate pressure refrigerant flowing in the heat exchange member (66).
  • the high pressure liquid refrigerant is cooled by heat exchange with the intermediate pressure refrigerant within the heat exchange member (66), and the degree of supercooling of the high pressure liquid refrigerant increases.
  • the high pressure liquid refrigerant cooled in the supercooling heat exchanger (60) is supplied through the liquid side interconnecting piping (21) to the indoor circuit (70).
  • the high pressure liquid refrigerant admitted into the injection piping ( 43 ) passes through the injection expansion valve (44) during which passage it is pressure reduced down to an intermediate pressure refrigerant and changes to intermediate pressure refrigerant.
  • the intermediate pressure refrigerant is fed to the heat exchange member (66) .
  • the intermediate pressure refrigerant admitted into the heat exchange member (66) absorbs heat from the high pressure liquid refrigerant within the container-shaped member (65), evaporates, and is supplied to the intermediate pressure port (32) of the compressor (31).
  • refrigerant condensed in the indoor heat exchanger (71), passes sequentially through the indoor expansion valve (72) during which passage it is pressure reduced down to an intermediate pressure, through the liquid side interconnecting piping (21) , and through the first flowpath (61) of the supercooling heat exchanger (60) and flows into the container-shaped member (65) .
  • the intermediate pressure refrigerant in the gas/liquid two-phase state is separated into liquid refrigerant and gas refrigerant.
  • the gas refrigerant of intermediate pressure collected in an inner upper portion of the container-shaped member (65) , is supplied through the injection piping (43) to the intermediate pressure port (32) of the compressor (31).
  • the liquid refrigerant of intermediate pressure collected in an inner lower portion of the container-shaped member (65), passes through the outdoor expansion valve (37) during which passage it is pressure reduced down to a low pressure and is then introduced into the outdoor heat exchanger (36).
  • the heat exchange member (66) constituting the intermediate pressure heat exchanger (40) is housed in the inside of the container-shaped member (65) constituting the gas/liquid two-phase separator (51) .
  • the container-shaped member (65) with the heat exchange member (66) housed therein is connected to the outdoor circuit (30) , this is the same as arranging both the gas/liquid separator (51) and the intermediate pressure heat exchanger (40) in the outdoor circuit (30). Therefore, in accordance with the present modification, the outdoor circuit (30) can be simplified in configuration in comparison with the case where the gas/liquid separator (51) and the intermediate pressure heat exchanger (40) are formed separately from each other.
  • the lower stage compressor (33) and the higher stage compressor (34) are connected together in series. More specifically, the suction side of the lower stage compressor (33) is connected through the accumulator (38) to the second port of the four-way selector valve (35). The discharge side of the lower stage compressor (33) is connected to the suction side of the higher stage compressor (34). The discharge side of the higher stage compressor (34) is connected to the first port of the four-way selector valve (35) .
  • the termination end of the injection piping (43) is connected to piping by which the discharge side of the lower stage compressor (33) and the suction side of the higher stage compressor (34) are connected together. And, gas refrigerant of intermediate pressure flowing through the injection piping (43) is drawn, together with intermediate pressure refrigerant discharged from the lower stage compressor (33), into the higher stage compressor (34).
  • the present invention finds useful application in a refrigeration system that performs a gas injection operation by supplying gas refrigerant of intermediate pressure to a compressor.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP07737771.1A 2006-03-06 2007-03-05 Dispositif de réfrigération Withdrawn EP1992887A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006059482A JP4715561B2 (ja) 2006-03-06 2006-03-06 冷凍装置
PCT/JP2007/054186 WO2007102463A1 (fr) 2006-03-06 2007-03-05 Dispositif de réfrigération

Publications (2)

Publication Number Publication Date
EP1992887A1 true EP1992887A1 (fr) 2008-11-19
EP1992887A4 EP1992887A4 (fr) 2015-12-16

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US (1) US20100229582A1 (fr)
EP (1) EP1992887A4 (fr)
JP (1) JP4715561B2 (fr)
KR (1) KR100960196B1 (fr)
CN (1) CN101384862B (fr)
AU (1) AU2007223486B2 (fr)
WO (1) WO2007102463A1 (fr)

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EP2689202A2 (fr) * 2011-03-24 2014-01-29 Airbus Operations GmbH Contenant à réfrigérant multifonctionnel et procédé de fonctionnement d'un tel contenant à réfrigérant
EP2426437A3 (fr) * 2010-09-02 2015-03-11 Guangzhou Deron Heat Source Facilities Co., Ltd. Système de pompe à chaleur à ultra basse température avec mécanisme d'injection de réfrigérant secondaire

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EP2689202A2 (fr) * 2011-03-24 2014-01-29 Airbus Operations GmbH Contenant à réfrigérant multifonctionnel et procédé de fonctionnement d'un tel contenant à réfrigérant
EP2530409A3 (fr) * 2011-06-03 2013-09-04 Glen Dimplex Deutschland GmbH Installation de pompe à chaleur et procédé de fonctionnement dýune installation de pompe à chaleur

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JP4715561B2 (ja) 2011-07-06
US20100229582A1 (en) 2010-09-16
KR100960196B1 (ko) 2010-05-27
WO2007102463A1 (fr) 2007-09-13
EP1992887A4 (fr) 2015-12-16
CN101384862B (zh) 2010-08-18
KR20080087902A (ko) 2008-10-01
CN101384862A (zh) 2009-03-11
AU2007223486A1 (en) 2007-09-13
JP2007240026A (ja) 2007-09-20
AU2007223486B2 (en) 2010-03-04

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