CN101384862A - Refrigeration device - Google Patents
Refrigeration device Download PDFInfo
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- CN101384862A CN101384862A CNA2007800052131A CN200780005213A CN101384862A CN 101384862 A CN101384862 A CN 101384862A CN A2007800052131 A CNA2007800052131 A CN A2007800052131A CN 200780005213 A CN200780005213 A CN 200780005213A CN 101384862 A CN101384862 A CN 101384862A
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- Prior art keywords
- refrigerant
- heat exchanger
- intermediate pressure
- loop
- compressor
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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
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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
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- 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
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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
- 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
- F25B2400/05—Compression system with heat exchange between particular parts of the system
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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
- 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
- F25B2400/05—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
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
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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
- 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
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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
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
Abstract
A refrigeration device (20) has an intermediate-pressure heat exchanger (40) and a gas-liquid separator (51). In cooling operation, that portion of refrigerant which is condensed in an outdoor heat exchanger (36) flows into injection piping (43). The pressure of the refrigerant flowed into the injection piping (43) is reduced to an intermediate pressure when the refrigerant passes an injection expansion valve (44), and then the refrigerant is supplied to an intermediate pressure port (32) of a compressor (31) after evaporating at the intermediate- pressure heat exchanger (40). In heating operation, the pressure of the refrigerant condensed at an indoor heat exchanger (71) is reduced to an intermediate pressure when the refrigerant passes an indoor expansion valve (72), and then the refrigerant flows into the gas-liquid separator (51). The intermediate-pressure gas refrigerant in the gas-liquid separator (51) is supplied to the intermediate pressure port (32) of the compressor (31).
Description
Technical field
[0001] the present invention relates to a kind ofly the intermediate pressure gaseous refrigerant is fed to compressor promptly carry out the refrigerating plant that gas injects (gas injection).
Background technology
[0002] up to now, be purpose with the input power of cutting down compressor, carry out refrigerating plant that so-called gas injects (that is: the intermediate pressure gaseous refrigerant being fed to the action of compressor) for well-known.For example, example from the refrigerating plant that is carrying out the single stage compress kind of refrigeration cycle to the discharge chambe that is in compression process of compressor that supply with the intermediate pressure gaseous refrigerant in is disclosed in Fig. 1 of patent documentation 1.Also have, in Figure 13 of patent documentation 1, disclose the example of between stage compressor and advanced compression machine, supplying with the intermediate pressure gaseous refrigerant in the refrigerating plant that is carrying out twin-stage compression refrigeration circulation.
[0003] the intermediate pressure gaseous refrigerant is produced.Thus, in the refrigerating plant shown in Figure 1 of for example patent documentation 1, the gas-liquid separator that intermediate pressure refrigerant is separated into liquid refrigerant and gaseous refrigerant is arranged in the refrigerant loop, and supplies with the intermediate pressure gaseous refrigerant from this gas-liquid separator to compressor.Also have, in the refrigerating plant shown in Figure 9 of patent documentation 1, make intermediate pressure refrigerant carry out heat exchange and evaporate at intermediate pressure heat exchanger and high pressure liquid refrigerant, and from this intermediate pressure heat exchanger to compressor supply intermediate pressure gaseous refrigerant.
Patent documentation 1: the open 2001-033117 communique of Japan Patent
(inventing problem to be solved)
[0004] but, in described refrigerating plant, be arranged on compressor and heat in the refrigerant loop
Constitution equipments such as interchanger are configured in the position of apart from each other each other sometimes or are configured in mutually different height.For example, a kind of as refrigerating plant, air conditioner couples together outdoor unit and indoor units with connecting pipe mostly and constitutes.And, in the time of in air conditioner being arranged on building etc., following situation also appears sometimes, that is: the length of connecting pipe is near 100m, or has the difference in height about 20～30m between outdoor unit and the indoor units.
[0005] thus, the situation that is provided with of refrigerating plant is according to the difference of its purposes etc. and varied.And, in the described refrigerating plant that gas injects, the problem that might occur turning round smoothly of carrying out because it is provided with situation.Hereinafter, describe about this problem.
[0006] as mentioned above, carrying out the refrigerating plant that gas injects, supply with the intermediate pressure gaseous refrigerant from gas-liquid separator to compressor sometimes.Because liquid refrigerant and gaseous refrigerant coexistence in gas-liquid separator is so the liquid refrigerant of sending from gas-liquid separator becomes saturation state.When this refrigerating plant cooled off the action of object, the saturation state liquid refrigerant that flows out from gas-liquid separator was sent to and utilizes the side heat exchanger.Yet, in case utilize the side heat exchanger away from gas-liquid separator or when utilizing the side heat exchanger to be arranged on than the high position of gas-liquid separator, then occur following situation sometimes, that is: in pipeline, descend and cause the part evaporation of cold-producing medium from the pressure of gas-liquid separator cold-producing medium to utilizing side heat exchanger process of flowing.Thus, the influx that might cause flowing into the liquid refrigerant that utilizes the side heat exchanger reduces, thereby with utilizing the obtainable cooling capacity of side heat exchanger institute to reduce.
[0007] also has,, make intermediate pressure refrigerant and high pressure liquid refrigerant heat exchange at the intermediate pressure heat exchanger sometimes, and will in the intermediate pressure heat exchanger, vaporized intermediate pressure refrigerant feed to compressor carrying out the refrigerating plant that gas injects.When this refrigerating plant carries out the action of heating target thing, be imported into the intermediate pressure heat exchanger after the part of chilled cold-producing medium is decompressed to intermediate pressure in utilizing the side heat exchanger.But, in case the intermediate pressure heat exchanger is when utilizing side heat exchanger or intermediate pressure heat exchanger to be arranged on Billy with the high position of side heat exchanger, following situation then appears sometimes, that is: in pipeline, descend, thereby the part of cold-producing medium is evaporated and make the temperature of cold-producing medium reduce from the pressure that utilizes side heat exchanger cold-producing medium to intermediate pressure heat exchanger process of flowing.Thus, in the intermediate pressure heat exchanger, carry out the high-pressure refrigerant of heat exchange and the temperature difference of intermediate pressure refrigerant each other and diminish, and intermediate pressure refrigerant is gasified.
Summary of the invention
[0008] the present invention is the invention in view of described problem points, and its purpose is: carrying out the refrigerating plant that so-called gas injects, no matter how it is provided with situation or operating condition, this refrigerating plant is being turned round smoothly.
(solving the method for problem)
The described refrigerating plant of the following note of [0009] first invention is as the object of invention, this refrigerating plant is for having refrigerant loop 20, this refrigerant loop 20 constitutes compressor 31,34 and heat source side heat exchanger 36 and utilize side heat exchanger 71 to couple together, carry out kind of refrigeration cycle, and can make between cooling action and the heating action and switch, become condenser and the described side heat exchanger 71 that utilizes becomes evaporimeter at heat source side heat exchanger 36 described in this cooling action, utilize side heat exchanger 71 to become condenser described in moving and described heat source side heat exchanger 36 becomes evaporimeter in this heating.And, it is characterized in that: described refrigerant loop 20 has the intermediate pressure refrigerant that obtains that reduces pressure by a part that makes high pressure liquid refrigerant is fed to described compressor 31,34 injection path 43, make at described injection path 43 towards described compressor 31,34 intermediate pressure refrigerant that flow and high pressure liquid refrigerant carry out heat exchange and the intermediate pressure heat exchanger 40 that evaporates, and will be separated into the gas-liquid separator 51 of liquid refrigerant and gaseous refrigerant by the intermediate pressure refrigerant that high pressure liquid refrigerant is reduced pressure obtain, in described refrigerant loop 20, can change the circulation path of cold-producing medium, the intermediate pressure gaseous refrigerant of described injection path 43 feeds to described compressor 31 so that will flow through in described cooling action, 34, and in described heating action, will feed to described compressor 31 from the intermediate pressure gaseous refrigerant that described gas-liquid separator 51 flows out, 34.
[0010] in first invention, the supply source that intermediate pressure refrigerant is offered compressor 31,34 when being in cooling action and heating action has produced variation.When being in the cooling action, vaporized intermediate pressure refrigerant is fed to compressor 31,34 in intermediate pressure heat exchanger 40.At this moment, in intermediate pressure heat exchanger 40, high pressure liquid refrigerant is cooled owing to carrying out heat exchange with intermediate pressure refrigerant, so the supercooling degree of high pressure liquid refrigerant increases.Thus, even arrive from middle pressure heat exchanger 40 utilize side heat exchanger 71 before the pressure of high-pressure refrigerant occur to a certain degree descending, also can make to feed to the high-pressure refrigerant that utilizes side heat exchanger 71 and keep liquid condition or make feeding to the amount that the high-pressure refrigerant that utilizes side heat exchanger 71 evaporates reduce in flow process.On the other hand, when being in the heating action, intermediate pressure refrigerant is imported into gas-liquid separator 51, and the gaseous refrigerant in the gas-liquid separator 51 is fed to compressor 31,34.Thus, even from utilize side heat exchanger 71 arrive gas-liquid separators 51 before the pressure of cold-producing medium occur to a certain degree descending and when causing the part evaporation of cold-producing medium, also owing in gas-liquid separator 51, this cold-producing medium is separated into gaseous refrigerant and liquid refrigerant, thereby can positively supply with the intermediate pressure gaseous refrigerant to compressor 31,34.
[0011] second invention is the invention on the basis of described first invention, it is characterized in that: described refrigerant loop 20 utilize connecting pipe 21,22 will be provided with the heat source side loop 30 of described compressor 31,34 and described heat source side heat exchanger 36 and be provided with described utilize side heat exchanger 71 utilize side loop 70 to couple together to constitute, described injection path 43, described intermediate pressure heat exchanger 40 and described gas-liquid separator 51 are arranged on described heat source side loop 30.
[0012] in second invention, refrigerant loop 20 is by heat source side loop 30 and utilize side loop 70 and connecting pipe 21,22 to constitute.In the cooling action, the high pressure liquid refrigerant that has been cooled when by intermediate pressure heat exchanger 40 flows into via connecting pipe 21 and utilizes side heat exchanger 71.Thus, even it is long or when utilizing side loop 70 to be arranged on than high position, heat source side loop 30 when the length of connecting pipe 21,22, also can make to feed to the high-pressure refrigerant that utilizes side heat exchanger 71 and keep liquid condition, perhaps make to feed to the amount that the high-pressure refrigerant that utilizes side heat exchanger 71 evaporates reduce in flow process.On the other hand, when being in the heating action, chilled cold-producing medium flows into gas-liquid separator 51 by connecting pipe 21 in utilizing side heat exchanger 71, and the gaseous refrigerant in the gas-liquid separator 51 is fed to compressor 31,34.Thus, even when long or heat source side loop 30 is arranged on Billy with the high position of side loop 70, also can positively supply with gaseous refrigerant to compressor 31,34 when the length of connecting pipe 21,22.
[0013] the 3rd invention is the invention on the basis of described first invention, it is characterized in that: described gas-liquid separator 51 is made of container-like component 65, this container-like component 65 is arranged on the downstream that becomes described heat source side heat exchanger 36 when being in described cooling action in the described refrigerant loop 20 and becomes the described position that utilizes the downstream of side heat exchanger 71 when described heating is moved when being in, described intermediate pressure heat exchanger 40 is made of with parts 66 heat exchange of the inside that is incorporated in described container-like component 65, makes the intermediate pressure refrigerant of the described injection path 43 of flowing through and the liquid refrigerant heat exchange in the described container-like component 65 with parts 66 in this heat exchange.
[0014] in the 3rd invention, gas-liquid separator 51 is made of container-like component 65, and intermediate pressure heat exchanger 40 is made of with parts 66 heat exchange.When being in the cooling action, chilled cold-producing medium (high pressure liquid refrigerant) flows into container-like component 65 in heat source side heat exchanger 36.Also have, the part of high pressure liquid refrigerant flows into to be injected path 43 and flow into heat-exchanging part after reducing to intermediate pressure.The intermediate pressure refrigerant of inflow heat-exchanging part and the high pressure liquid refrigerant in the container-like component 65 carry out heat exchange and evaporate, and are fed to compressor 31,34 then.High pressure liquid refrigerants owing to carrying out heat exchange with intermediate pressure refrigerant in the chilled container-like component 65 are sent to from container-like component 65 and utilize side heat exchanger 71.On the other hand, when being in the heating action, flow into container-like component 65 after chilled cold-producing medium is depressurized to intermediate pressure in utilizing side heat exchanger 71.In container-like component 65, the intermediate pressure refrigerant that is flowed into is separated into liquid refrigerant and gaseous refrigerant.From container-like component 65, liquid refrigerant is sent to heat source side heat exchanger 36, and gaseous refrigerant is fed to compressor 31,34 by injecting path 43.
[0015] the 4th invention is the invention on the basis of described first invention, it is characterized in that: the position that becomes the downstream of described intermediate pressure heat exchanger 40 when being in described cooling action in described refrigerant loop 20 is provided with supercooling heat exchanger 60, in this supercooling heat exchanger 60, make high pressure liquid refrigerant and reduce to the low pressure refrigerant that low pressure obtains by a part and carry out heat exchange, cool off this high pressure liquid refrigerant high pressure liquid refrigerant.
[0016] in the 4th invention, supercooling heat exchanger 60 is arranged in the refrigerant loop 20.When being in the cooling action, the high pressure liquid refrigerant that flows through intermediate pressure heat exchanger 40 carries out heat exchange with the low pressure refrigerant that obtains by the part decompression that makes high pressure liquid refrigerant and cools off in supercooling heat exchanger 60.Just, in supercooling heat exchanger 60, the supercooling degree of high pressure liquid refrigerant increases.Chilled high pressure liquid refrigerant is sent to and utilizes side heat exchanger 71 in supercooling heat exchanger 60.
[0017] the 5th invention is the invention on the basis of described first invention, it is characterized in that: carry out the single stage compress kind of refrigeration cycle in described refrigerant loop 20, described compressor 31 constitutes and makes the intermediate pressure gaseous refrigerant flow into the discharge chambe that is in the compression process.
[0018] in the 5th invention, the intermediate pressure gaseous refrigerant is imported into the discharge chambe in the compression process of being in of compressor 31.After sucking, the intermediate pressure refrigerant that compressor 31 will become vaporized low pressure refrigerant and intermediate pressure heat exchanger 40 in the heat exchanger of evaporimeter or gas-liquid separator 51 in utilizing side heat exchanger 71 and heat source side heat exchanger 36 provided compresses.
[0019] the 6th invention is the invention on the basis of described first invention, it is characterized in that: in described refrigerant loop 20, rudimentary side compressor 33 and senior side compressor 34 are connected in series and carry out twin-stage compression refrigeration circulation, and described refrigerant loop 20 constitutes to the suction side of described senior side compressor 34 and supplies with the intermediate pressure gaseous refrigerant.
[0020] in the 6th invention, the intermediate pressure gaseous refrigerant is imported into the suction side of senior side compressor 34.The cold-producing medium that senior side compressor 34 will compress in rudimentary side compressor 33 and suck from the gaseous refrigerant of intermediate pressure heat exchanger 40 or gas-liquid separator 51.
(effect of invention)
[0021] in the present invention, to in intermediate pressure heat exchanger 40, vaporized intermediate pressure refrigerant feed to compressor 31,34 when being in when action cooling, will be in intermediate pressure heat exchanger 40 chilled high pressure liquid refrigerant be sent to and utilize side heat exchanger 71.Thus, even utilizing side heat exchanger 71 to be arranged on or utilizing side heat exchanger 71 to be arranged on the position higher than intermediate pressure heat exchanger 40 away from the position of intermediate pressure heat exchanger 40, and arrive from middle pressure heat exchanger 40 and to utilize being provided with under the situation that descending by a relatively large margin appears in the pressure of high-pressure refrigerant before the side heat exchanger 71, also can make to feed to the high-pressure refrigerant that utilizes side heat exchanger 71 and keep liquid condition, perhaps can cut down the amount that the high-pressure refrigerant that utilizes side heat exchanger 71 evaporates that feeds in flow process.Consequently in the cooling action, can guarantee amount, thereby can give full play to the cooling capacity of utilizing side heat exchanger 71 to the liquid refrigerant that utilizes side heat exchanger 71 to supply with.
[0022] also has, in the present invention, when being in the heating action, supply with the intermediate pressure gaseous refrigerant to compressor 31,34 from gas-liquid separator 51.Thus, be arranged on Billy with the high position of side heat exchanger 71 even be arranged on away from the position that utilizes side heat exchanger 71 or gas-liquid separator 51 at gas-liquid separator 51, and, also the intermediate pressure gaseous refrigerant positively can be fed to compressor 31,34 from utilizing side heat exchanger 71 to arrive being provided with under the situation that descending by a relatively large margin appears in the pressure of cold-producing medium before the gas-liquid separators 51.Consequently can avoid flowing into the problem appearance that compressor 31,34 causes compressor 31,34 to be damaged because of intermediate pressure liquid refrigerant.
[0023] so, according to the present invention, no matter refrigerating plant 10 is provided with under which kind of state, in cooling action and these two kinds of actions of heating action refrigerating plant 10 is turned round smoothly.
[0024] in described second invention, by heat source side loop 30, utilize side loop 70 and connecting pipe 21,22 to constitute refrigerant loop 20.In this constitutes, mostly be the heat source side loop 30 that is provided with intermediate pressure heat exchanger 40 and gas-liquid separator 51 greatly and be provided with utilize side heat exchanger 71 utilize side loop 70 to be set at the position of apart from each other each other or the two is set up at various height.Therefore, in the refrigerating plant 10 of refrigerant loop 20 with formation shown in the present, as mentioned above if in cooling action and heating action, change supply source from intermediate pressure refrigerant to compressor 31,34 that supply with, then can alleviate the restriction of the suffered situation that is provided with of refrigerating plant 10.
[0025] in described the 3rd invention, the heat exchange that constitutes intermediate pressure heat exchanger 40 is incorporated in the inside of the container-like component 65 that constitutes gas-liquid separator 51 with parts 66.Just, be connected in the refrigerant loop 20, then be equivalent in refrigerant loop 20, be provided with gas-liquid separator 51 and intermediate pressure heat exchanger 40 these two parts as if taking in the container-like component 65 of heat exchange in inside with parts 66.Therefore,, compare with the situation of intermediate pressure heat exchanger 40, can simplify the formation of refrigerant loop 20 with each self-forming gas-liquid separator 51 respectively according to this invention.
[0026] in described the 4th invention, in refrigerant loop 20, is provided with supercooling heat exchanger 60, thereby the supercooling degree that is sent to the high pressure liquid refrigerant that utilizes side heat exchanger 71 in the cooling action is increased.Thus, even under the situation that is provided with of utilizing the pressure of high-pressure refrigerant before the side heat exchanger 71 to occur to a certain degree descending from middle pressure heat exchanger 40 arrival, also can further positively make to feed to the high-pressure refrigerant that utilizes side heat exchanger 71 and keep liquid condition, perhaps can further cut down the amount that the high-pressure refrigerant that utilizes side heat exchanger 71 is evaporated that feeds in flow process.
Description of drawings
[0027] Fig. 1 is the piping diagram that the refrigerant loop of the air conditioner of expression embodiment one constitutes, the state during Fig. 1 (A) expression cooling operation, the state during Fig. 1 (B) expression warming operation.
Fig. 2 is the piping diagram that the refrigerant loop of the air conditioner of expression embodiment two constitutes, the state during Fig. 2 (A) expression cooling operation, the state during Fig. 2 (B) expression warming operation.
Fig. 3 is the piping diagram that the refrigerant loop of the related air conditioner of first variation of other embodiment of expression constitutes, the state during Fig. 3 (A) expression cooling operation, the state during Fig. 3 (B) expression warming operation.
Fig. 4 is the piping diagram that the refrigerant loop of the related air conditioner of second variation of other embodiment of expression constitutes, the state during Fig. 4 (A) expression cooling operation, the state during Fig. 4 (B) expression warming operation.
(symbol description)
[0028] 20 refrigerant loop
21 hydraulic fluid side connecting pipes
22 gas side connecting pipes
30 outdoor loops (heat source side loop)
31 compressors
33 rudimentary side compressors
34 senior side compressors
36 outdoor heat converters (heat source side heat exchanger)
40 intermediate pressure heat exchangers
43 flow in pipes (injection path)
51 gas-liquid separators
65 container-like component
66 heat exchange parts
70 indoor loops (utilizing side loop)
71 indoor heat converters (utilizing the side heat exchanger)
The specific embodiment
[0029] below, with reference to the accompanying drawings embodiments of the present invention is elaborated.
[0030] " working of an invention mode one "
Describe about embodiments of the present invention one.What present embodiment was related is the air conditioner 10 that is made of refrigerating plant of the present invention.
[0031] as shown in Figure 1, the air conditioner 10 of present embodiment has an outdoor unit 11 and two indoor units 12.In addition, the quantity of indoor units 12 only is simple example.In outdoor unit 11, take in outdoor loop 30 as heat source side loop 30.In each indoor units 12, take in as the indoor loop 70 that utilizes side loop.
[0032] in air conditioner 10,, thereby formed refrigerant loop 20 by usefulness hydraulic fluid side connecting pipe 21 and gas side connecting pipe 22 junction chamber external loops 30 and indoor loop 70.In this refrigerant loop 20, two indoor loops 70 are connected in parallel with each other for an outdoor loop 30.
[0033] in each indoor loop 70, is respectively arranged with as utilizing the indoor heat converter 71 of side heat exchanger and indoor expansion valve 72 each.Indoor heat converter 71 is the air heat exchangers that make room air and cold-producing medium carry out heat exchange.In each indoor loop 70, indoor heat converter 71 is one another in series with indoor expansion valve 72 and is connected.In each indoor loop 70, the end of close indoor expansion valve 72 1 sides is connected with hydraulic fluid side connecting pipe 21, and the end of close indoor heat converter 71 1 sides is connected with gas side connecting pipe 22.
[0034] in outdoor loop 30, is provided with compressor 31, four-way change-over valve 35, outdoor heat converter 36, outdoor expansion valve 37 and reservoir (accumulator) 38 as the heat source side heat exchanger.And, in this outdoor loop 30, also be provided with intermediate pressure heat exchanger 40, gas-liquid separator 51, by-pass line 50, flow in pipes 43 and intermediate-pressure gas pipeline 52.
[0035] compressor 31 is displacement type compressors 31, and the cold-producing medium that constitutes sucking discharge chambe compresses.Compressor 31 is provided with the intermediate pressure port (port) 32 that is used for the discharge chambe importing of intermediate pressure refrigerant in being in compression process.The ejection side of this compressor 31 is connected on first valve port of four-way change-over valve 35, and the suction side of this compressor 31 is connected on second valve port of four-way change-over valve 35 via reservoir 38.In addition, though in outdoor loop 30, only be provided with a compressor 31 in the present embodiment, also can be arranged in parallel multiple compressors.
[0036] outdoor heat converter 36 is the air heat exchangers that make outdoor air and cold-producing medium carry out heat exchange.Intermediate pressure heat exchanger 40 is the heat exchangers that carry out heat exchange between the cold-producing medium that makes in double-pipe exchange (double-pipe exchanger) and the plate-type exchanger etc.In this intermediate pressure heat exchanger 40, be formed with first stream 41 and second stream 42.One end of outdoor heat converter 36 is connected on the 3rd valve port of four-way change-over valve 35, and the other end is connected an end of first stream 41 of intermediate pressure heat exchanger 40 via outdoor expansion valve 37.The other end of first stream 41 of intermediate pressure heat exchanger 40 is connected on the hydraulic fluid side connecting pipe 21 via first check-valves 45.First check-valves 45 is provided as the cold-producing medium that only allows from middle pressure heat exchanger 40 flows to hydraulic fluid side connecting pipe 21 to be passed through.
[0037] flow in pipes 43 has formed the injection path.The top of this flow in pipes 43 is connected between the intermediate pressure heat exchanger 40 and first check-valves 45, and the end of this flow in pipes 43 is connected on the intermediate pressure port 32 of compressor 31.Second stream 42 of intermediate pressure heat exchanger 40 is arranged on this flow in pipes 43 midway.On flow in pipes 43, inject with expansion valve 44 and be set between second stream 42 of the top of this flow in pipes 43 and intermediate pressure heat exchanger 40.
[0038] gas-liquid separator 51 is tubular airtight containers of lengthwise.The bottom of this gas-liquid separator 51 is arranged on by-pass line 50 midway.The top of by-pass line 50 is connected between first check-valves 45 and the hydraulic fluid side connecting pipe 21, and the end of this by-pass line 50 is connected between first stream 41 and outdoor expansion valve 37 of intermediate pressure heat exchanger 40.Also have, on by-pass line 50, second check-valves 55 is arranged between the end and gas-liquid separator 51 of this by-pass line 50.Second check-valves 55 is provided as and only allows the cold-producing medium of this direction of flowing out from gas-liquid separator 51 to pass through.
[0039] end of intermediate-pressure gas pipeline 52 is connected the top of gas-liquid separator 51.The other end of intermediate-pressure gas pipeline 52 is connected between second stream 42 and compressor 31 of the intermediate pressure heat exchanger 40 on the flow in pipes 43.Be provided with magnetic valve 53 midway at this intermediate-pressure gas pipeline 52.
[0040] as mentioned above, first valve port of four-way change-over valve 35 is connected the ejection side of compressor 31, and second valve port of this four-way change-over valve 35 and the 3rd valve port are connected on reservoir 38 and the outdoor heat converter 36.Also have, the 4th valve port of four-way change-over valve 35 is connected on the gas side connecting pipe 22.This four-way change-over valve 35 can be communicated with first valve port and the 3rd valve port and make second valve port and first state (state shown in Fig. 1 (A)) that the 4th valve port is communicated with and make first valve port and the 4th valve port is communicated with and makes between second state (state shown in Fig. 1 (B)) that second valve port and the 3rd valve port be communicated with and switches.
[0041]-the running action-
In described air conditioner 10, cooling operation and warming operation are switched.
[0042]＜cooling operation 〉
On one side with reference to Fig. 1 (A), on one side running action during to cooling operation describe.In the refrigerant loop 20 when cooling operation, outdoor heat converter 36 becomes condenser, and indoor heat converter 71 becomes evaporimeter, and cold-producing medium circulates.Just, in refrigerant loop 20, cool off action.
[0043] specifically, when at cooling operation, four-way change-over valve 35 is set to first state.Also have, outdoor expansion valve 37 is set at full-gear, injects and is suitably regulated respectively with the aperture of expansion valve 44 and indoor expansion valve 72, and magnetic valve 53 cuts out simultaneously.
[0044] high-pressure gaseous refrigerant from compressor 31 ejections condenses to the outdoor air heat release at outdoor heat converter 36.High pressure liquid refrigerant cold-producing medium heat release in second stream 42 the process of first stream 41 that passes through intermediate pressure heat exchanger 40 from outdoor heat converter 36 outflows.The part of the high pressure liquid refrigerant that flows out from first stream 41 of middle pressure heat exchanger 40 flows into flow in pipes 43, and rest parts is assigned to each indoor loop 70 by hydraulic fluid side connecting pipe 21.
[0045] in each indoor loop 70, the high pressure liquid refrigerant that is flowed into is decompression by indoor expansion valve 72 time, thereafter in indoor heat converter 71 from the room air heat absorption and evaporate.Vaporized cold-producing medium is inhaled into compressor 31 by gas side connecting pipe 22 return chamber's external loops 30 after by reservoir 38 in indoor heat converter 71.
[0046] on the other hand, the high pressure liquid refrigerant that flows into flow in pipes 43 is being depressurized to the intermediate pressure refrigerant that intermediate pressure becomes the gas-liquid two-phase state when injecting with expansion valve 44.This intermediate pressure refrigerant cold-producing medium from first stream 41 in the process of second stream 42 of the intermediate pressure heat exchanger 40 of flowing through absorbs heat and evaporates.The intermediate pressure gaseous refrigerant that flows out from second stream 42 of middle pressure heat exchanger 40 is sent to the intermediate pressure port 32 of compressor 31.
[0047] compressor 31 sucks discharge chambe by reservoir 38 with low pressure refrigerant and compresses.Also have, the intermediate pressure gaseous refrigerant that flows into from middle pressure port 32 is imported into the discharge chambe that is in the compression process.And compressor 31 sprays after the cold-producing medium in the discharge chambe is compressed into high pressure.
[0048] so, in cooling operation, the high pressure liquid refrigerant that makes the supercooling degree increase that is cooled during by intermediate pressure heat exchanger 40 is sent to indoor loop 70 by hydraulic fluid side connecting pipe 21.Thus, even the length in hydraulic fluid side connecting pipe 21 is set at the position that exceeds certain altitude than outdoor loop 30 above certain-length or indoor loop 70, and in case the liquid refrigerant that is sent to hydraulic fluid side connecting pipe 21 from outdoor loop 30 will occur before arriving indoor loop 70 under the situation of high pressure liquid refrigerant part evaporation during for saturation state, the high-pressure refrigerant that also can guarantee to flow into indoor loop 70 is the single-phase state of liquid.Also have, if with the liquid refrigerant that is admitted to hydraulic fluid side connecting pipe 21 from outdoor loop 30 is that the situation of saturation state is compared, even the part of high pressure liquid refrigerant evaporation before arriving indoor loop 70, the amount of the high pressure liquid refrigerant that this evaporated is also less relatively.
[0049]＜warming operation 〉
On one side with reference to Fig. 1 (B), on one side running action during to warming operation describe.In the refrigerant loop 20 when being in warming operation, indoor heat converter 71 becomes condenser, and outdoor heat converter 36 becomes evaporimeter, and cold-producing medium circulates.Just, in refrigerant loop 20, heat action.
[0050] specifically, when at warming operation, four-way change-over valve 35 is set to second state.Also have, the aperture of outdoor expansion valve 37 and indoor expansion valve 72 is suitably regulated respectively, injects to be set to full-shut position with expansion valve 44, and magnetic valve 53 is opened simultaneously.
[0051] high-pressure gaseous refrigerant from compressor 31 ejections is assigned to each indoor loop 70 by gas side connecting pipe 22.In the indoor heat converter 71 in each indoor loop 70, high-pressure gaseous refrigerant condenses to the room air heat release.In each indoor loop 70, the intermediate pressure refrigerant of the cold-producing medium that flows out from indoor heat converter 71 decompression by indoor expansion valve 72 time becoming gas-liquid two-phase state.Pass through hydraulic fluid side connecting pipe 21 and return chamber's external loop 30 from the intermediate pressure refrigerant that flow out in each indoor loop 70, and flowing into gas-liquid separators 51 by by-pass line 50 backs.
[0052] liquid refrigerant in the intermediate pressure refrigerant that gas-liquid separator 51 flows into accumulates in the bottom of gas-liquid separator 51, and the gaseous refrigerant in this intermediate pressure refrigerant accumulates in the top of gas-liquid separator 51.Intermediate pressure liquid refrigerant in the gas-liquid separator 51 by-pass line 50 of flowing through once more, and decompression by outdoor expansion valve 37 time are imported into outdoor heat converter 36 then.In outdoor heat converter 36, cold-producing medium evaporates from the outdoor air heat absorption.Vaporized cold-producing medium is inhaled into compressor 31 after by reservoir 38 in outdoor heat converter 36.On the other hand, the intermediate pressure gaseous refrigerant in the gas-liquid separator 51 is successively by being imported into the intermediate pressure port 32 of compressor 31 behind intermediate-pressure gas pipeline 52 and the flow in pipes 43.
[0053] compressor 31 sucks discharge chambe by reservoir 38 with low pressure refrigerant and compresses.Also have, the intermediate pressure gaseous refrigerant that flows into from middle pressure port 32 is imported into the discharge chambe that is in the compression process.And compressor 31 sprays after the cold-producing medium in the discharge chambe is compressed into high pressure.
[0054] so, in warming operation, will be by hydraulic fluid side connecting pipe 21 cold-producing medium of return chamber's external loop 30 be separated into liquid refrigerant and gaseous refrigerant after importing gas-liquid separator 51, only the gaseous refrigerants in the gas-liquid separator 51 are fed to the intermediate pressure port 32 of compressor 31.Just, even when flowing into the cold-producing medium in outdoor loop 30 and being the gas-liquid two-phase state, also can only gaseous refrigerant positively be fed to the intermediate pressure port 32 of compressor 31.Thus, even the length in hydraulic fluid side connecting pipe 21 is configured in the position that exceeds certain altitude than indoor loop 70 above certain-length or outdoor loop 30, and arrive under the vaporized situation of a part of cold-producing medium before the outdoor loop 30, the cold-producing medium that also can guarantee to flow into the intermediate pressure port 32 of compressor 31 is the single-phase state of gas.
[0055]-effect of embodiment one-
In the cooling operation of described air conditioner 10, to in intermediate pressure heat exchanger 40, vaporized intermediate pressure refrigerant feed to the intermediate pressure port 32 of compressor 31, and will in intermediate pressure heat exchanger 40, feed to indoor loop 70 by chilled high pressure liquid refrigerant.Thus, even extremely long or indoor loop 70 is configured in the position higher than outdoor loop 30 in the length of the hydraulic fluid side connecting pipe 21 in junction chamber external loop 30 and indoor loop 70, and under the situation that is provided with that the pressure of cold-producing medium reduces significantly in the process of hydraulic fluid side connecting pipe 21 of flowing through, the high-pressure refrigerant that also can guarantee to feed to indoor loop 70 is a liquid condition, perhaps can cut down the amount that the high-pressure refrigerant that feeds to indoor loop 70 evaporates in flow process.Consequently can in cooling operation, guarantee to feed to the amount of the liquid refrigerant in indoor loop 70, thereby can give full play to the refrigerating capacity of indoor units 12.
[0056] at this, as described shown in the air conditioner 10, when a plurality of indoor loops 70 are connected in parallel with each other, in order suitably to regulate the refrigerating capacity of each indoor units 12, the aperture of indoor expansion valve 72 that can be by each indoor loop 70 of indivedual controls comes the allocation proportion of the cold-producing medium of distributing to indoor loop 70 is regulated.Yet, in case when the cold-producing medium by indoor expansion valve 72 is the gas-liquid two-phase state, makes the discharge characteristic of indoor expansion valve 72 become unstable, thereby might suitably control the allocation proportion of the cold-producing medium of distributing to each indoor loop 70.Relative therewith, in the air conditioner 10 of present embodiment, when being in cooling operation, can easily make the cold-producing medium that flows into indoor loop 70 keep liquid condition.Therefore, according to present embodiment, in air conditioner 10, can suitably control the refrigerating capacity of each indoor units 12 with a plurality of indoor units 12.
[0057] also has, in the heating action of described air conditioner 10, to be separated into liquid refrigerant and gaseous refrigerant from the cold-producing medium that indoor loop 70 turns back to outdoor loop 30 with gas-liquid separator 51, only the intermediate pressure gaseous refrigerant be offered compressor 31 from gas-liquid separator 51.Thus, even extremely long or outdoor loop 30 is configured in the position higher than indoor loop 70 in the length of the hydraulic fluid side connecting pipe 21 in junction chamber external loop 30 and indoor loop 70, and under the situation that is provided with that the pressure of cold-producing medium reduces significantly in the process of hydraulic fluid side connecting pipe 21 of flowing through, also can only gaseous refrigerant positively be fed to the intermediate pressure port 32 of compressor 31.Consequently can avoid owing to intermediate pressure liquid refrigerant flows into the problem appearance that compressor 31 causes compressor 31 to be damaged.
[0058] so, according to present embodiment, no matter air conditioner 10 is provided with under which kind of state, in cooling operation and these two kinds of runnings of warming operation air conditioner 10 is turned round smoothly.
[0059] " working of an invention mode two "
Describe about embodiments of the present invention two.Present embodiment is the example of having set up supercooling heat exchanger 60 and supercooling usefulness pipeline 63 on the basis of the air conditioner 10 of described embodiment one.At this, the air conditioner 10 of present embodiment and the difference of described embodiment one are described.
[0060] as shown in Figure 2, supercooling heat exchanger 60 is arranged in the outdoor loop 30.Supercooling heat exchanger 60 is the heat exchangers that carry out heat exchange between the cold-producing medium that makes in double-pipe exchange and the plate-type exchanger etc.In this supercooling heat exchanger 60, be formed with first stream 61 and second stream 62.First stream 61 of supercooling heat exchanger 60 is arranged between the intermediate pressure heat exchanger 40 and first check-valves 45 in the outdoor loop 30.
[0061] supercooling is connected between the supercooling heat exchanger 60 and first check-valves 45 with the top of pipeline 63, and this supercooling is connected between reservoir 38 and the four-way change-over valve 35 with the end of pipeline 63.Second stream 62 of supercooling heat exchanger 60 is configured in this supercooling with pipeline 63 midway.With on the pipeline 63, supercooling is arranged between second stream 62 of the top of this supercooling usefulness pipeline 63 and supercooling heat exchanger 60 with expansion valve 64 in supercooling.
[0062]-the running action-
＜cooling operation 〉
Shown in Fig. 2 (A), in the refrigerant loop 20 when being in cooling operation, the situation of cold-producing medium and described embodiment one circulates roughly the samely.Specifically, only following 2 different with the cold-producing medium circulating path in the described embodiment one, that is: the high pressure liquid refrigerant that flows out from middle pressure heat exchanger 40 flows into supercooling pipeline 63 in the part by supercooling heat exchanger 60 back influent side connecting pipes 21 and high pressure liquid refrigerant.
[0063] in the cooling operation of the air conditioner 10 of present embodiment, supercooling is suitably regulated with the aperture of expansion valve 64.The high pressure liquid refrigerant that flows out from first stream 41 of middle pressure heat exchanger 40 is the cold-producing medium heat release in second stream 62 the process of first stream 61 by supercooling heat exchanger 60.The part of the high pressure liquid refrigerant that flows out from first stream 61 of supercooling heat exchanger 60 flows into supercooling with pipeline 63, and rest parts is assigned to each indoor loop 70 by hydraulic fluid side connecting pipe 21.Just, by intermediate pressure heat exchanger 40 and supercooling heat exchanger 60 these two cools down high pressure liquid refrigerant fed to indoor loop 70.
[0064] on the other hand, flow into supercooling and be reduced to the low pressure refrigerant that low pressure becomes the gas-liquid two-phase state during with expansion valve 64 by supercooling with the high pressure liquid refrigerant of pipeline 63.This low pressure refrigerant cold-producing medium from first stream 61 in the process of second stream 62 of the supercooling heat exchanger 60 of flowing through absorbs heat and evaporates.The low-pressure gaseous refrigerant that flows out from second stream 62 of supercooling heat exchanger 60 is with being inhaled into compressor 31 from indoor loop 70 by the low pressure refrigerant that gas side connecting pipe 22 turns back to outdoor loop 30.
[0065]＜warming operation 〉
Shown in Fig. 2 (B), in the refrigerant loop 20 when being in warming operation, cold-producing medium carries out and described embodiment one identical circulation.Specifically, when warming operation, supercooling is a full-shut position with expansion valve 64.And the intermediate pressure refrigerant that flows into outdoor loop 30 from hydraulic fluid side connecting pipe 21 flows into gas-liquid separator 51 by by-pass line 50, and is separated into liquid refrigerant and gaseous refrigerant.
[0066]-effect of embodiment two-
In the present embodiment, in outdoor loop 30, be provided with supercooling heat exchanger 60, thereby the feasible degree of superheat that is sent to the high pressure liquid refrigerant in indoor loop 70 increases in cooling operation.Thus, even under the situation that is provided with that the pressure that arrives high-pressure refrigerant before the indoor loop 70 from outdoor loop 30 has reduced, also can further positively make the high-pressure refrigerant that feeds to indoor loop 70 keep liquid condition, perhaps can further cut down the amount that the high-pressure refrigerant that feeds to indoor loop 70 evaporates in flow process.
[0067] " other embodiment "
Also described embodiment can be set at following formation.
[0068]-first variation-
In described each embodiment, also can make gas-liquid separator 51 and intermediate pressure heat exchanger 40 realize integrated.At this,, describe about the example of in the air conditioner 10 of described embodiment two, using this variation on one side on one side with reference to Fig. 3.
[0069] container-like component 65 of the tubular of lengthwise constitutes the gas-liquid separator 51 of this variation by forming slightly.The bottom of the container-like component 65 of formation gas-liquid separator 51 is connected the part between outdoor expansion valve 37 and supercooling heat exchanger 60 in the outdoor loop 30.In addition, in the outdoor loop 30 of this variation, by-pass line 50, first check-valves 45 and second check-valves 55 have been saved.
[0070], is provided with the heat exchange parts 66 that heat-transfer pipe formed coil spring shape in the inside of container-like component 65.Heat exchange is set at bottom in the container-like component 65 with parts 66 to be immersed in form in the liquid refrigerant that lodges in the container-like component 65.Heat exchange is configured in the downstream of the injection usefulness expansion valve 44 on the flow in pipes 43 with parts 66.In this variation, this heat exchange has constituted intermediate pressure heat exchanger 40 with parts 66.
Action during [0071] about cooling operation describes.When cooling operation, identical with the situation of described embodiment two, inject and suitably regulated with the aperture of expansion valve 64 with expansion valve 44 and supercooling, magnetic valve 53 cuts out.
[0072] when being in cooling operation, chilled cold-producing medium flows into container-like component 65 by outdoor expansion valve 37 backs of full-gear in outdoor heat converter 36.The intermediate pressure refrigerant heat release of high pressure liquid refrigerant in the container-like component 65 in the heat exchange usefulness parts 66 of flowing through.Just, in container-like component 65, high pressure liquid refrigerant is owing to being cooled with the intermediate pressure refrigerant heat exchange in the parts 66 with heat exchange, thereby the supercooling degree of high pressure liquid refrigerant increases.The part of chilled high pressure liquid refrigerant flows into flow in pipes 43 in container-like component 65, and rest parts is further cooled when first stream 61 by supercooling heat exchanger 60.
[0073] chilled high pressure liquid refrigerant is fed to indoor loop 70 by hydraulic fluid side connecting pipe 21 in supercooling heat exchanger 60.On the other hand, the high pressure liquid refrigerant that flows into to flow in pipes 43 is being decompressed to intermediate pressure when injecting with expansion valve 44, thereby becomes intermediate pressure refrigerant and be sent to heat exchange usefulness parts 66.Absorb heat and evaporate from the high pressure liquid refrigerant in the container-like component 65 to intermediate pressure refrigerant that heat exchange flows into parts 66, fed to the intermediate pressure port 32 of compressor 31 then.
Action during [0074] about warming operation describes.When warming operation, identical with the situation of described embodiment two, injecting with expansion valve 44 and supercooling is full-shut position with expansion valve 64, and magnetic valve 53 is opened.
[0075] when being in warming operation, chilled cold-producing medium is decompressed to intermediate pressure by indoor expansion valve 72 time in indoor heat converter 71, and first stream 61 by hydraulic fluid side connecting pipe 21 and supercooling heat exchanger 60 flows into container-like component 65 successively thereafter.In container-like component 65, the intermediate pressure refrigerant of gas-liquid two-phase state is separated into liquid refrigerant and gaseous refrigerant.And the intermediate pressure gaseous refrigerant that accumulate on the top in container-like component 65 is fed to the intermediate pressure port 32 of compressor 31 by flow in pipes 43.Also have, the intermediate pressure liquid refrigerant that accumulate the bottom in container-like component 65 is decompressed to low pressure by outdoor expansion valve 37 time, then be imported into outdoor heat converter 36.
[0076] as mentioned above, in this variation, the heat exchange that constitutes intermediate pressure heat exchanger 40 is incorporated in the inside of the container-like component 65 that constitutes gas-liquid separator 51 with parts 66.Just, if will take in heat exchange in inside when being connected in the outdoor loop 30, then be equivalent in outdoor loop 30, be provided with gas-liquid separator 51 and intermediate pressure heat exchanger 40 these two parts with the container-like component 65 of parts 66.Therefore,, compare with the situation of intermediate pressure heat exchanger 40, the formation in outdoor loop 30 is oversimplified with each self-forming gas-liquid separator 51 respectively according to this variation.
[0077]-second variation-
In described each embodiment, also rudimentary side compressor 33 and senior side compressor 34 can be set in outdoor loop 30, thereby in refrigerant loop 20, carry out twin-stage compression refrigeration circulation.At this,, describe about the example of in the air conditioner 10 of described embodiment two, using this variation on one side on one side with reference to Fig. 4.
[0078] in the outdoor loop 30 of this variation, rudimentary side compressor 33 and senior side compressor 34 are connected in series.Specifically, the suction side of rudimentary side compressor 33 is connected second valve port of four-way change-over valve 35 via reservoir 38.The ejection side of rudimentary side compressor 33 is connected the suction side of senior side compressor 34.The ejection side of senior side compressor 34 is connected first valve port of four-way change-over valve 35.Also have, in this variation, the end of flow in pipes 43 is connected on the pipeline that the suction side with the ejection side of rudimentary side compressor 33 and senior side compressor 34 couples together.And the intermediate pressure gaseous refrigerant of the flow in pipes 43 of flowing through is inhaled into senior side compressor 34 with the intermediate pressure refrigerant from rudimentary side compressor 33 ejections.
[0079] in addition, above embodiment is desirable in essence example, but intention is not limited the present invention, suitable thing of the present invention or its purposes scope.
(utilizing on the industry possibility)
[0080] as described above shown in, the present invention is for the intermediate pressure gaseous refrigerant is fed to compression The refrigerating plant that machine namely carries out gas inject has practicality.
Claims (6)
1. refrigerating plant, has refrigerant loop (20), this refrigerant loop (20) constitutes compressor (31,34), heat source side heat exchanger (36) and utilize side heat exchanger (71) to couple together and carry out kind of refrigeration cycle, and can make between cooling action and the heating action and switch, become condenser and the described side heat exchanger (71) that utilizes becomes evaporimeter at heat source side heat exchanger (36) described in this cooling action, described heat source side heat exchanger (36) becomes evaporimeter utilizing side heat exchanger (71) to become condenser described in this heating action, it is characterized in that:
Described refrigerant loop (20) has: the intermediate pressure refrigerant that obtains that will reduce pressure by a part that makes high pressure liquid refrigerant feeds to described compressor (31,34) injection path (43), make at described injection path (43) towards described compressor (31,34) intermediate pressure refrigerant of Liu Donging and high pressure liquid refrigerant carry out heat exchange and the intermediate pressure heat exchanger (40) that evaporates, and will be separated into the gas-liquid separator (51) of liquid refrigerant and gaseous refrigerant by the intermediate pressure refrigerant that high pressure liquid refrigerant is reduced pressure obtain
In described refrigerant loop (20), can change the circulation path of cold-producing medium, the intermediate pressure gaseous refrigerant of described injection path (43) feeds to described compressor (31,34) so that will flow through in described cooling action, and will feed to described compressor (31,34) from the intermediate pressure gaseous refrigerant that described gas-liquid separator (51) flows out in described heating action.
2. refrigerating plant according to claim 1 is characterized in that:
Described refrigerant loop (20) utilize connecting pipe (21,22) will be provided with the heat source side loop (30) of described compressor (31,34) and described heat source side heat exchanger (36) and be provided with described utilize side heat exchanger (71) utilize side loop (70) to couple together to constitute
Described injection path (43), described intermediate pressure heat exchanger (40) and described gas-liquid separator (51) are arranged on described heat source side loop (30).
3. refrigerating plant according to claim 1 is characterized in that:
Described gas-liquid separator (51) is made of container-like component (65), this container-like component (65) is arranged on the downstream that becomes described heat source side heat exchanger (36) when being in described cooling action in the described refrigerant loop (20) and becomes the described position that utilizes the downstream of side heat exchanger (71) when described heating is moved when being in
Described intermediate pressure heat exchanger (40) is made of with parts (66) the heat exchange of the inside that is incorporated in described container-like component (65), makes the intermediate pressure refrigerant of the described injection path (43) of flowing through and the liquid refrigerant heat exchange in the described container-like component (65) with parts (66) in this heat exchange.
4. refrigerating plant according to claim 1 is characterized in that:
The position that becomes the downstream of described intermediate pressure heat exchanger (40) when being in described cooling action in described refrigerant loop (20) is provided with supercooling heat exchanger (60), in this supercooling heat exchanger (60), make high pressure liquid refrigerant and reduce to the low pressure refrigerant that low pressure obtains by a part and carry out heat exchange, cool off this high pressure liquid refrigerant high pressure liquid refrigerant.
5. refrigerating plant according to claim 1 is characterized in that:
In described refrigerant loop (20), carry out the single stage compress kind of refrigeration cycle,
Described compressor (31) constitutes and makes the intermediate pressure gaseous refrigerant flow into the discharge chambe that is in the compression process.
6. refrigerating plant according to claim 1 is characterized in that:
In described refrigerant loop (20), rudimentary side compressor (33) and senior side compressor (34) are connected in series and carry out twin-stage compression refrigeration circulation,
Described refrigerant loop (20) constitutes to the suction side of described senior side compressor (34) and supplies with the intermediate pressure gaseous refrigerant.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006059482A JP4715561B2 (en) | 2006-03-06 | 2006-03-06 | Refrigeration equipment |
| JP059482/2006 | 2006-03-06 | ||
| PCT/JP2007/054186 WO2007102463A1 (en) | 2006-03-06 | 2007-03-05 | Refrigeration device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101384862A true CN101384862A (en) | 2009-03-11 |
| CN101384862B CN101384862B (en) | 2010-08-18 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007800052131A Expired - Fee Related CN101384862B (en) | 2006-03-06 | 2007-03-05 | Refrigeration device |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US20100229582A1 (en) |
| EP (1) | EP1992887A4 (en) |
| JP (1) | JP4715561B2 (en) |
| KR (1) | KR100960196B1 (en) |
| CN (1) | CN101384862B (en) |
| AU (1) | AU2007223486B2 (en) |
| WO (1) | WO2007102463A1 (en) |
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| CN103238034A (en) * | 2011-01-31 | 2013-08-07 | 三菱电机株式会社 | Air-conditioning device |
| CN103348197A (en) * | 2011-07-05 | 2013-10-09 | 松下电器产业株式会社 | Refrigeration cycle device |
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| CN113063234A (en) * | 2019-12-31 | 2021-07-02 | Lg电子株式会社 | Multistage compression type refrigerating device |
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| CN103238034A (en) * | 2011-01-31 | 2013-08-07 | 三菱电机株式会社 | Air-conditioning device |
| CN103238034B (en) * | 2011-01-31 | 2015-04-01 | 三菱电机株式会社 | Air-conditioning device |
| CN103348197A (en) * | 2011-07-05 | 2013-10-09 | 松下电器产业株式会社 | Refrigeration cycle device |
| CN103348197B (en) * | 2011-07-05 | 2016-02-10 | 松下知识产权经营株式会社 | Refrigerating circulatory device |
| CN105526727A (en) * | 2012-05-28 | 2016-04-27 | 大金工业株式会社 | Refrigeration device |
| CN105526727B (en) * | 2012-05-28 | 2018-02-23 | 大金工业株式会社 | Refrigerating plant |
| CN104185766A (en) * | 2012-07-10 | 2014-12-03 | 夏普株式会社 | Heat-pump-type heating device |
| CN113063234A (en) * | 2019-12-31 | 2021-07-02 | Lg电子株式会社 | Multistage compression type refrigerating device |
Also Published As
| Publication number | Publication date |
|---|---|
| AU2007223486A1 (en) | 2007-09-13 |
| KR20080087902A (en) | 2008-10-01 |
| EP1992887A1 (en) | 2008-11-19 |
| CN101384862B (en) | 2010-08-18 |
| AU2007223486B2 (en) | 2010-03-04 |
| JP2007240026A (en) | 2007-09-20 |
| WO2007102463A1 (en) | 2007-09-13 |
| EP1992887A4 (en) | 2015-12-16 |
| US20100229582A1 (en) | 2010-09-16 |
| KR100960196B1 (en) | 2010-05-27 |
| JP4715561B2 (en) | 2011-07-06 |
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