CN100387914C - Refrigerating device and refrigerator - Google Patents
Refrigerating device and refrigerator Download PDFInfo
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- CN100387914C CN100387914C CNB2006100598985A CN200610059898A CN100387914C CN 100387914 C CN100387914 C CN 100387914C CN B2006100598985 A CNB2006100598985 A CN B2006100598985A CN 200610059898 A CN200610059898 A CN 200610059898A CN 100387914 C CN100387914 C CN 100387914C
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- heat
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- cold
- refrigerant
- refrigerating plant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
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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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
- F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2507—Flow-diverting valves
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2519—On-off valves
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
- F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
- F25D11/022—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures with two or more evaporators
Abstract
An object is to provide a refrigerating device capable of realizing a high-efficiency operation in a case where a compressor having an intermediate pressure section is applied, and a refrigerator including this refrigerating device. A refrigerating device 30 includes: a compressor 1; a radiator 2; an expansion valve 3; a gas-liquid separator 4; and a heat absorbing unit 8 through which a liquid refrigerant discharged from this gas-liquid separator circulates. The refrigerating device further includes: a refrigerant pipe in which the refrigerant discharged from the heat absorbing unit 8 can be introduced into a suction port of the compressor 1 and which introduces a gas refrigerant separated by the gas-liquid separator 4 into the intermediate pressure section of the compressor 1; and a refrigerant pipe which introduces an intermediate-pressure refrigerant of the compressor 1 into the gas-liquid separator 4.
Description
Technical field
The present invention relates to possess the middle splenium that the gas refrigerant by gas-liquid separator separates can be imported compressor mechanism refrigerating plant and have the refrigerator of this refrigerating plant.
Background technology
Known, refrigerating plant generally possesses 2 sections compressors, radiator, pressure reducer and gas-liquid separators, possesses to be imported mechanism's (with reference to patent documentation 1) of the middle splenium between the 1st section and the 2nd section of above-mentioned compressor by the gas refrigerant of this gas-liquid separator separates.In this kind refrigerating plant, because will be, import the middle splenium of above-mentioned compressor with the previous status of gas, so can improve the efficient of this compressor by the gas refrigerant of above-mentioned gas-liquid separator separates.
Patent documentation 1: the spy opens the 2003-106693 communique
, in this kind refrigerating plant, the 2nd section the refrigerant temperature that imports 2 sections compressors sometimes rises, and this compressor operation efficient is reduced, thereby has the low problem of running efficiency of freeze cycle integral body.
Summary of the invention
, the objective of the invention is to for this reason, a kind of refrigerator that can realize the refrigerating plant of high efficiency running and have this refrigerating plant when use has the compressor of middle splenium is provided.
Refrigerating plant of the present invention, a kind of refrigerating plant, possess: compressor with middle splenium, the radiator that is connected with the discharge side of this compressor, the 1st mechanism of decompressor that is connected with the outlet side of this radiator, inflow is become the cold-producing medium of gas-liquid mixed state and is separated into gas refrigerant and the gas-liquid separator of liquid refrigerant by described the 1st mechanism of decompressor decompression, and comprise the 2nd mechanism of decompressor of the liquid refrigerant circulation that makes to come out from described gas-liquid separator and the heat-absorbing body of the 1st heat dump, can be from the cold-producing medium that described heat-absorbing body comes out to the more suction inlet importing of low-pressure side of described middle splenium than described compressor, the feature of described refrigerating plant is to possess: the 1st refrigerant piping that imports described gas refrigerant to described middle splenium, with the 2nd refrigerant piping that compacting cryogen in the middle of the described compressor is imported to described gas-liquid separator.
The described invention of the 2nd invention as the described refrigerating plant of the 1st invention, is characterized in that: possess oil eliminator in described the 2nd refrigerant piping, it is used for being separated in contained oil in the mobile cold-producing medium of this refrigerant piping.
The described invention of the 3rd invention as the described refrigerating plant of the 2nd invention, is characterized in that: possess oil pipe line, this oil pipe line can be to the oil of described the 1st refrigerant piping circulation by described oil eliminator separation.
The described invention of the 4th invention, as the described refrigerating plant of any invention in the 1st～the 3rd invention, it is characterized in that: described heat-absorbing body possesses: the 1st heat-absorbing body that comprises the 3rd mechanism of decompressor and the 2nd heat dump, with the 2nd heat-absorbing body that possesses and comprise the 4th mechanism of decompressor and the 3rd heat dump with the 1st heat-absorbing body side by side, the mode that can import to the suction inlet of described low-pressure side behind the cold-producing medium interflow of coming out according to the cold-producing medium that comes out from described the 1st heat-absorbing body with from described the 2nd heat-absorbing body constitutes, from the described refrigerant piping of cold-producing medium before the interflow that described the 1st heat-absorbing body comes out, the switching mechanism that possesses the refrigerant piping that is used to switch the cold-producing medium circulation that makes to come out from described the 1st heat-absorbing body is connected with described the 1st refrigerant piping from a side's of this switching mechanism branch refrigerant piping.
The described invention of the 5th invention as the described refrigerating plant of the 4th invention, is characterized in that: described the 2nd heat dump and described the 3rd heat dump, under different temperature, work selectively.
The described invention of the 6th invention, as the described refrigerating plant of the 5th invention, it is characterized in that: compare with described the 2nd heat dump, described the 3rd heat dump is more being worked under the low temperature.
The described invention of the 7th invention, as the described refrigerating plant of any invention in the 1st～the 6th invention, it is characterized in that: described compressor is with by the cold-producing medium of the 1st section compressing section compresses, uses 2 sections compressors of the 2nd section compressing section compresses again.
The described invention of the 8th invention as the described refrigerating plant of any invention in the 1st～the 7th invention, is characterized in that: with the high-voltage section of supercriticality running freeze cycle.
The described invention of the 9th invention as the described refrigerating plant of any invention in the 1st～the 8th invention, is characterized in that: adopt carbon dioxide as cold-producing medium.
10. refrigerator of the present invention is characterized in that: possess as the described refrigerating plant of any invention in the 1st～the 9th invention.
Description of drawings
Fig. 1 is the refrigerant lines figure of an embodiment of expression refrigerating plant of the present invention.
Fig. 2 is the concise and to the point profile of the compressor of expression one embodiment of the invention.
Fig. 3 is the concise and to the point pie graph of the application examples of refrigerating plant in refrigerator of expression one embodiment of the invention.
Fig. 4 is the refrigerant lines figure of the refrigerating plant of expression other embodiments of the invention.
Fig. 5 is the concise and to the point pie graph of the application examples of refrigerating plant in refrigerator of expression other embodiments of the invention.
Fig. 6 is the refrigerant lines figure of the refrigerating plant of expression another other embodiment of the present invention.
Among the figure, 1-compressor, 2-radiator, 3,65, the 66-expansion valve, 4-gas-liquid separator, 5-oil eliminator, 7,52,53-check-valves, 8,10,10B, 11,11B-heat-absorbing body, 12, the 13-capillary, 14,57, the 58-heat dump, 21,41-refrigerating chamber, 22,42-refrigerating chamber, 23-selection approach, 26-control device, 30,50,70-refrigerating plant, the 40-refrigerator, 48,63, the 64-fan, 91, the 92-triple valve, the 112-airtight container, the electronic key element of 114-, the electronic key element of 116-, 118-rotates compression unit.
The specific embodiment
Below, implement preferred embodiment of the present invention with reference to description of drawings.
Describe one embodiment of the invention in detail based on accompanying drawing.Fig. 1 represents the refrigerant lines figure as the refrigerating plant of one embodiment of the invention.Refrigerating plant 30, possess compressor 1, the radiator 2 that is connected with the discharge side of this compressor, the expansion valve 3 that is connected with the outlet side of this radiator 2, the gas-liquid separator 4 that is connected with the outlet side of this expansion valve 3, circulation heat-absorbing body 8 and oil eliminator 5 by the liquid refrigerant of this gas-liquid separator separates, circulation is connected with the middle splenium of compressor 1 by the refrigerant piping 4C of gas-liquid separator 4 gas separated cold-producing mediums, the outlet side of heat-absorbing body 8 is connected with the suction inlet of compressor 1, constitutes freeze cycle.In addition, have check-valves 7 among the refrigerant piping 4C between the middle splenium of gas-liquid separator 4 and compressor 1, simultaneously between the suction inlet of heat-absorbing body 8 and compressor 1, have check-valves 53.
Heat-absorbing body 8 comprises: as the triple valve 91 of stream switching mechanism, as the 1st capillary 12 of the mechanism of decompressor, and and Resistance Value that be set up in parallel 2nd capillary 13 bigger than the 1st capillary 12 with the 1st capillary 12, with the heat dump that is connected later 14 that is connected from the suction inlet of the junction of two streams 9 of the refrigerant piping of above-mentioned the 1st capillary 12 and the 2nd capillary 13 and compressor 1.This heat-absorbing body 8 is worked under different humidity provinces selectively, from the liquid refrigerant that gas-liquid separator 4 comes out, if pass through the switching of triple valve 91, cold-producing medium is to the 1st capillary 12 side flow, just increase the flow of the cold-producing medium that flows along heat dump 14, refrigerate running.In addition, if the switching by triple valve 91, cold-producing medium is to the 2nd capillary 13 side flow, just reduces the flow of the cold-producing medium that flows along heat dump 14, carries out freezing running.In addition, the switching of this refrigeration running and freezing running, as mentioned above, except that the method for being undertaken by the switching of the 1st capillary 12 and the 2nd capillary 13, also can adopt by changing the rotation number of compressor 1, the method of the flow of the cold-producing medium that control is flowed along heat dump 14 in addition, also can realize by the combination said method.
In addition, refrigerating plant 30, its formation possesses selection mechanism 23, and this selection mechanism 23 is used for importing to a plurality of chambers that are controlled in the different temperatures district (refrigerating chamber 21, refrigerating chamber 22) selectively by utilizing not shown fan air-supply at the cold air that heat dump 14 produces.This selection mechanism 23 comprises air-supply passage 24 and switches air door 25, has passage 57A between this switching air door 25 and refrigerating chamber 21, and refrigerating chamber 22 between have passage 58A.In addition, switching connection control device 26 on the air door 25.This control device 26 is connected with above-mentioned triple valve 91, for example, when freezing running, triple valve 91 is switched to the 2nd capillary 13 sides, switch air door 25 simultaneously, make cold wind flow channel 58A, import cold wind to refrigerating chamber 22, when the refrigeration running, triple valve 91 is switched to the 1st capillary 12 sides, switch air door 25 simultaneously, make cold wind flow channel 57A, import cold wind to refrigerating chamber 2.
In addition, as mentioned above, gas-liquid separator 4 is the cold-producing mediums that are inflated the middle 2 phase mixtures of pressing of valve 3 decompressions formation to wherein flowing into, and the cold-producing medium of this 2 phase mixture is separated into the separator of gas refrigerant and liquid refrigerant.Adopt this gas-liquid separator 4, gas-liquid separation is from the cold-producing medium of 2 phase mixtures of refrigerant piping 4A inflow in gas-liquid separator 4, and a side gas refrigerant flows out from refrigerant piping 4C, and the opposing party's liquid refrigerant flows out from refrigerant piping 4B.In addition, in the middle of 1 section compression unit 1A discharge, suppress cryogen after being separated,,, flow into refrigerant piping 4C, so constitute gas-liquid separator 4 with the above-mentioned gas refrigerant mixed of in gas-liquid separator 4, separating from refrigerant piping 5C inflow by oil eliminator 5 oil.In addition, as mentioned above, refrigerant piping 4C, the mode that is imported the middle splenium of compressor 1 by gas-liquid separator 4 gas separated cold-producing mediums can be connected, this gas refrigerant, utilize the pressure reduction in the refrigerant piping 4C, shown in dotted arrow, be imported into the suction inlet of 2 sections compression unit 1B of compressor 1.
Below, with reference to Fig. 2 compressor 1 in the present embodiment is described.Fig. 2 is the concise and to the point profile of compressor 1.This compressor 1 is 2 sections compression type rotary compressors of internal high pressure type, and this compressor 1 possesses sealed at both ends lengthwise airtight container 112 roughly cylindraceous up and down, and the bottom of sealing container 112 is as oil groove.Airtight container 112, the rotation compression unit 118 that the 1st compression unit 1A that possesses electronic key element 114, driven by the rotating shaft by electronic key element 114 116 and the 2nd compression unit 1B constitute, in its outside, bottom foot 210 is set, is used for this compressor 1 is fixed on for example not shown refrigerator framework.
Airtight container 112, constitute by end cap (lid) 112B on roughly the rim of a bowl of end of electronic key element 114 sides that have the vessel 112A that takes in electronic key element 114 and rotation compression unit 118, stop up this vessel 112A, on this end cap 112B, form circular installing hole 112D, binding post 120 (omission distribution) is installed on this installing hole 112D, is used for to electronic key element 114 supply capabilities.
In addition, in rotating shaft 116, connect oily path 182 is set to the transition of mind-set vertical direction in the axle, one end of rotation compression unit 118 sides of this oil path 182 is at the oil groove opening of airtight container 112 bottoms, and the other end of electronic in addition key element 144 sides is at end cap 112B side opening.In addition, this oil path 182 also is communicated with the sliding part of each section compression unit 1A, 1B, and formation can be supplied with the formation of oil to this compression unit 1A, 1B.
1 section compression unit 1A and 2 sections compression unit 1B of rotation compression unit 18 are made of clamping central dividing plate 136 between above-mentioned cylinder 128,140 the 1st cylinder 138 and the 2nd cylinder 140.In addition, each section compression unit 1A, 1B are made of following respectively: the 1st cylinder 138 and the 2nd cylinder 140, and it is configured in the both sides (about being) of central dividing plate 136 in Fig. 1; The 1st rolls the 146 and the 2nd rolls 146, and it is located on the rotating shaft 116, is entrenched on the 1st eccentric part 142 and the 2nd eccentric part 144 of the phase difference with 180 degree, along the 1st cylinder 138 and the 140 interior eccentric rotations of the 2nd cylinder; The 1st blade 150 and the 2nd blade 152, it rolls 146,148 and contacts with above-mentioned respectively, will divide into low-pressure chamber side and hyperbaric chamber side in the cylinder 138,140 respectively; Holding components 154,156, its respectively electronic key element 114 sides of inaccessible cylinder 140 opening surface and with the opening surface of electronic key element 114 opposition sides of cylinder 138, the bearing of double as rotating shaft 116.
The outside of blade 150,152 (being the right side in Fig. 1) is provided with spring 174,176, and its outboard end with blade 150,152 contacts, and makes this blade 150,152 to rolling 146,148 side active forces.In addition, metal pin 222,223 is set, is used to prevent that spring 174,176 from coming off in airtight container 112 sides of spring 174,176.In addition, on the 2nd blade 152, form not shown back pressure chamber, this back pressure chamber is applied the pressure of the hyperbaric chamber side in the cylinder 140 with back pressure.
In addition, be provided with on holding components 154,156 and discharge anechoic chamber 162,164, it is by making its part depression, with baffle plate 200 and cover 168 these depressed parts of capping and forming respectively.That is, discharge anechoic chamber 162 and form, discharge anechoic chamber 164 and form by the depressed part that covers 168 capping holding components 156 by depressed part with baffle plate 200 capping holding components 154.
Discharge in anechoic chamber 162 and the airtight container 112, by connect baffle plate 200 and be communicated with at the discharge line 221 of electronic key element 144 side openings, discharge the refrigerant gas of the high pressure that is compressed by 2 sections compression unit 1B from electronic key element 114 sides of this discharge line 221 to airtight container 112 in.At this moment, in refrigerant gas, sneak into the oil of supplying with 2 sections compression unit 1B, but should the also discharge of electronic key element 114 sides in airtight container 112 of oil.Then, separate the oil of sneaking into the refrigerant gas, be stored in the oil groove of airtight container 112 inner bottom parts from refrigerant gas.
In addition, insert connection in airtight container 112: cold-producing medium ingress pipe 194 is used for refrigerant gas is imported 1 section compression unit 1A; Intermediate refrigerant discharge pipe 192 is used for discharging the refrigerant gas that is reached middle pressure by 1 section compression unit 1A compression outside airtight container 112; Intermediate refrigerant ingress pipe 193 is used for as mentioned above via intercooler 1C, oil eliminator 5 and gas-liquid separator 4, will import 2 sections compression unit 1B of compressor 1 from the middle compacting cryogen that this intermediate refrigerant discharge pipe 192 is discharged; Refrigerant discharge leader 196 is used for discharging from compressor 1, is compressed to high pressure by 2 sections compression unit 1B, the refrigerant gas after discharging in airtight container 112 by discharge line 221 as mentioned above.
Then, in the refrigerating plant 30 of present embodiment, as cold-producing medium, consider combustibility and toxicity etc., enclosing the little natural cold-producing medium of carrying capacity of environment is carbon dioxide coolant (CO
2).In addition, the oil as the lubricating oil of compressor 1 can use for example mineral oil, alkylbenzene oil, ether oil, PAG (PAG), POE (polyol ester) etc.
So, owing in refrigerating plant 30, adopt carbon dioxide as cold-producing medium, so for example under outdoor temperature reaches situation more than the critical-temperature (approximately+31 ℃) of carbon dioxide, from the high-voltage section of freeze cycle is the discharge side of 2 sections compression unit 1B, via radiator 2, entrance side to expansion valve 3 is supercriticality, thus with overcritical cycle operation refrigerating plant 30.
By above formation, the work of the refrigerating plant 30 in the present embodiment is described with reference to Fig. 1.Refrigerating plant 30 can be selected mainly to use the freezing running of the 2nd capillary 13 as required and mainly use the refrigeration of the 1st capillary 12 to turn round.
At first, freezing running is described.In addition, so-called this freezing running is that near in accordance with regulations temperature (for example ,-26 ℃) makes heat dump 14 work, the running of cooling off refrigerating chamber 22.
In this freezing running, if running compressor 1, the cold-producing medium of discharging from compressor 1 just is cooled by being dispelled the heat by radiator 2.Thereafter, the cold-producing medium that comes out from radiator 2 arrives expansion valve 3, is depressurized at this, becomes 2 phase mixtures of gas/liquid, imports to this gas-liquid separator 4 from the refrigerant piping 4A of gas-liquid separator 4.Then, as mentioned above, in this gas-liquid separator 4 cold-producing medium is separated into gas refrigerant and liquid refrigerant, gas refrigerant after via check-valves 7, imports to the middle splenium of compressor 1 to refrigerant piping 4C circulation.In addition, the liquid refrigerant by gas-liquid separator 4 separates to refrigerant piping 4B circulation, arrives triple valve 91.Then, this liquid refrigerant circulates to the 2nd capillary 13 by triple valve 91, and is depressurized.Then, the cold-producing medium that this is depressurized with heat dump 14 evaporation, after absorb heat on every side, turns back to the suction inlet of compressor 1.In addition, when freezing running,, make cold wind logical, so cooling refrigerating chamber 22 to passage 58A effluent owing to the switching of switching air door 25 by control device 26.
Then, the refrigeration running is described.In addition, so-called should the refrigeration running, be that near temperature high by than above-mentioned freezing running time the (for example ,-5 ℃) makes above-mentioned heat dump 14 work, the running of refrigerated compartment 21.
In this refrigeration running, the humidity province that absorbing mechanism 8 plays a role is different during with above-mentioned freezing running.That is,, to 12 circulations of the 1st capillary, after being depressurized,, hot from absorbing on every side with heat dump 14 evaporations at triple valve 91 from the cold-producing medium that gas-liquid separator 4 comes out.In addition, when the refrigeration running,, make cold wind logical, so refrigerated compartment 21 to passage 57A effluent owing to the switching of switching air door 25 by control device 26.In the refrigerating plant 30 of present embodiment, when freezing running, when refrigeration is turned round, can both form freeze cycle as mentioned above, cool off each chamber 21,22.
In addition, in refrigerating plant 30,,, make its suction inlet that turns back to 1 section compression unit 1A, can reduce the compression efficiency of compressor 1 even utilize heat-absorbing body 8 to make its circulation can not be used for cooling by gas-liquid separator 4 gas separated cold-producing mediums.
Therefore, in the present embodiment, will be owing to form by gas-liquid separator 4 gas separated cold-producing mediums, be refrigerant piping 4C via the middle splenium of compressor 1, import the formation of the suction inlet of 2 sections compression unit 1B, so can suppress the decline of the compression efficiency of compressor 1.Especially, the refrigerating plant 30 of present embodiment, owing in refrigerant loop, enclose carbon dioxide coolant, so compare with used in the past freon system or HC (hydrocarbon) series coolant etc., ratio height by the gas in the ratio of gas-liquid separator 4 gas separated and liquid, partly import the middle splenium of compressor 1 owing to will be somebody's turn to do many gas, so can improve the efficient of freeze cycle more.
In addition, the middle compacting cryogen of discharging from 1 section compression unit 1A contains big gauging, if make its original state flow into gas-liquid separator 4, separating oil in this gas-liquid separator 4, the oil that separates flows into heat-absorbing body 8 mostly, significantly be reduced in the cooling performance of heat dump 14, simultaneously the problem to the oil supply amount of 2 sections compression unit 1B appears reducing in a large amount of oil of circulation between 1 section compression unit 1A, gas-liquid separator 4 and the heat-absorbing body 8 of compressor 1.
But, the refrigerating plant 30 of present embodiment, because being formed on 1 section compression unit 1A possesses oil eliminator 5, can utilize oil pipe line 5B, will in the middle of above-mentioned, suppress the oil that cryogen separates at this, at junction of two streams 9E, with the cold-producing medium that in refrigerant piping 4C, circulates together, supply with the formation of 2 sections compression unit 1B,, can will supply with 2 sections compression unit 1B with the oil that middle compacting cryogen is together discharged from 1 section compression unit 1A so can avoid aforesaid problem.
In addition, the compressor 1 of present embodiment, be 2 sections compression type rotary compressors of internal high pressure type, owing to form the cold-producing medium that contains from the oil of 2 sections compression unit 1B, after in airtight container 112, discharging by discharge line 221, by constituting that refrigerant discharge leader 196 is discharged, so cold-producing medium by discharge line 221 discharges, in airtight container 112 behind the separated oil, discharge from refrigerant discharge leader 196, therefore can excessively not reduce the oil mass in the oil groove of airtight container 112 bottoms, can each section of proper lubrication compression unit 1A, 1B.
Herein, in oil pipe line 5B and refrigerant piping 4C, owing to result from the pressure loss that causes from intercooler 1C, refrigerant piping 5A, 5C, 4C and the gas-liquid separator 4 etc. of the suction inlet of discharge side to the 2 section compression unit 1B of 1 section compression unit 1A, reach minimal pressure near the suction inlet of 2 sections compression unit 1B, so can successfully carry out fuel feeding to these 2 sections compression unit 1B.
, usually, be inflated the cold-producing medium of 2 phase mixtures of valve 3 decompressions, and discharge from 1 section compression unit 1A and to be compared temperature by the cooled cold-producing medium of intercooler 1C low.But, in the present embodiment, as mentioned above, because will be from 1 section compression unit 1A discharge and the cold-producing medium that is cooled off by intercooler 1C, after in flowing into gas-liquid separator 4, with at this gas-liquid separator 4 from above-mentioned 2 mixture gas separated refrigerant mixed mutually, so can cool off the suction cold-producing medium of 1 section compression unit 1B further, can improve the compression efficiency of compressor 1.
In addition, refrigerating plant 30, owing to be the formation of carrying out 2 sections expansions by expansion valve 3 and the 1st capillary 12 or the 2nd capillary 13, so between between the outlet side of expansion valve 3 and the 1st capillary 12 and the 2nd capillary 13 suction sides and the suction side of the discharge side of 1 section compression unit 1A of compressor 1 and 2 sections compression unit 1B, become the intermediate pressure part in this freeze cycle.
Below, the application examples of refrigerating plant 30 in refrigerator of present embodiment is described with reference to Fig. 3.Fig. 3 represents to have the concise and to the point pie graph of the refrigerator of refrigerating plant 30.
This refrigerator 40 is formed on epimere and possesses refrigerating chamber 41, possesses the formation of refrigerating chamber 42 at hypomere.In the inside of this refrigerating chamber 42 case endoseptum 43 is set, in the wind path 44 that separates with this case endoseptum 43, above-mentioned heat dump 14 is set.At the inlet A of above-mentioned wind path 44, dispose the 1st and switch air door 45, the 1 and switch air doors 45, the position of the inlet A that closes wind path 44 (dotted line position) and open wind path 44 inlet A position (solid line position) between switching.In addition, form dorsal part wind path 46 on the rear wall 47 of refrigerator 40, when the 1st switching air door 45 was switched to dotted line position, via dorsal part wind path 46, the inlet A of wind path 44 and refrigerating chamber 41 were communicated with.In addition, configuration fan 48 and the 2nd switches air door 49 on the outlet B of above-mentioned wind path 44, the 2nd switches air door 49, the position of the inlet B that closes wind path 44 (dotted line position) and open wind path 44 inlet B position (solid line position) between switch, at the opening 51 of these solid line position the 2nd air door 49 capping intermediate bulkheads 50.
According to above formation, when freezing running, be placed on the position (solid line position) of the inlet A that opens wind path 44 by switching air door 45 the 1st, switching air door 49 with the 2nd is placed on the position (solid line position) of the inlet B that opens wind path 44, air in the circulating frozen chamber 42 is by heat dump 14 coolings.In addition, when the refrigeration running, be placed on the position (dotted line position) of the inlet A that closes wind path 44 by switching air door 45 the 1st, switching air door 49 with the 2nd is placed on the position (dotted line position) of the inlet B that closes wind path 44, via the air in the dorsal part wind path 46 circulation refrigerating chambers 41, by heat dump 14 coolings.
Below, with reference to Fig. 4 other embodiments of the invention are described.Fig. 4 represents the refrigerant lines figure of the refrigerating plant 50 of this moment.In the present embodiment, the formation of the symbol that additional and the foregoing description 1 are identical has identical or same function or effect.In the present embodiment, compare with the foregoing description 1, difference is, replaces heat-absorbing body 8, the 2nd heat-absorbing body 11 that has the 1st heat-absorbing body 10 and be set up in parallel with it at the outlet side of triple valve 91.
The 1st heat-absorbing body 10, the 1st heat dump 57 that comprises the 1st capillary 12 and connect and be provided with the 1st capillary 12.The 2nd heat-absorbing body 11 comprises the 2nd capillary 13, the 2nd heat dump 58, the check-valves 52 of connecting and having with the 2nd capillary 13 in addition.In addition, the refrigerant pipe of the outlet side of the 1st heat-absorbing body 10 and the 2nd heat-absorbing body 11, same with the refrigerating plant 30 of the foregoing description 1 behind junction of two streams 9B interflow, via check-valves 53, be connected with the suction inlet of compressor 1.In addition, the 1st heat-absorbing body 10 and the 2nd heat-absorbing body 11 play a role in different humidity provinces mutually selectively.
More than, because the refrigerating plant 50 of present embodiment has the 1st heat-absorbing body 10 and the 2nd heat-absorbing body 11, heat dump 57,58 plays a role in different humidity provinces respectively, so can utilize from passage 57A, the 58A of each heat dump 57,58, difference is refrigerated compartment 21 and refrigerating chamber 22 selectively.Thus, in humidity province different freezing running and refrigeration running, can use the heat dump that is fit to this operating temperature, thereby improve the running efficiency in each running.
Below, the application examples of refrigerating plant 50 in refrigerator of present embodiment is described with reference to Fig. 5.Fig. 5 represents to have the concise and to the point pie graph of the refrigerator of refrigerating plant 50.
This refrigerator 40 is formed on epimere and possesses refrigerating chamber 41, possesses the formation of refrigerating chamber 42 at hypomere.In the inside of each chamber 41,42 case endoseptum 61,62 is set respectively, in the wind path 44 that separates with this case endoseptum 61,62, above-mentioned heat dump 57,58 and fan 63,64 is set.In this formation, the 1st heat-absorbing body 10 and the 2nd heat-absorbing body 11 are switched in, thermal cutoff logical according to the thermal conductance of refrigeration running and freezing running, to either party heat dump 57,58 flow system cryogens, and drive the fan 63,64 corresponding with it.To heat dump 57 flow system cryogens the time, supply with cold wind to refrigerating chamber 41, to heat dump 58 flow system cryogens the time, supply with cold wind to refrigerating chamber 42.
Thus, the refrigerator 40 of present embodiment, owing to possess refrigerating plant 50 as mentioned above, so can improve cooling performance and running efficiency.
Below, with reference to Fig. 6 another other embodiment of the present invention is described.Fig. 6 represents the refrigerant lines figure of the refrigerating plant 70 of this moment.In addition, in Fig. 6, the formation of the symbol that additional and the foregoing description 1,2 are identical has identical or same function or effect.The refrigerating plant 70 of present embodiment, comparing with the foregoing description 2, difference is, there is not triple valve 91, replace the 1st heat-absorbing body 10 and the 2nd heat-absorbing body 11, have the 3rd heat-absorbing body 10B and the 4th heat-absorbing body 11B, in addition, have the triple valve 92 as the stream switching mechanism, the refrigerant piping 92A that draws from this triple valve 92 is connected with above-mentioned refrigerant piping 4C.
The 3rd heat-absorbing body 10B, comprise circulation from the cold-producing medium of branch point 9C as the 1st expansion valve 65 of the mechanism of decompressor and the heat dump 57 of refrigeration usefulness.The 4th heat-absorbing body 11B comprises the 2nd expansion valve 66 and the freezing heat dump 58 as the mechanism of decompressor that are set up in parallel with described the 3rd heat-absorbing body 10B.In addition, the refrigerant piping of the refrigerant piping of heat dump 57 outlet sides and heat dump 58 outlet sides after junction of two streams 9D connects, is connected with the suction inlet of compressor 1.In addition, between heat dump 57 and junction of two streams 9D, has triple valve 92, between heat dump 57 and triple valve, has refrigerant piping 9C, has refrigerant piping 92B between this external triple valve 92 and the junction of two streams 9D, on residue one side of triple valve 92, connect refrigerant piping 92A in addition, this refrigerant piping 92A at junction of two streams 9F, connects with the refrigerant piping 4C that is connected with the suction inlet of 2 sections compression unit 1B from gas-liquid separator 4 simultaneously.
Other the 1st expansion valve 65 and the 2nd expansion valve 66, same with above-mentioned expansion valve 3, formation can change the formation of throttle degree.In addition, by changing the degree of this throttling,, in the refrigerating plant 70 of present embodiment, can select freezing running, refrigeration running and freezing and refrigeration running as required in addition by switch three-way valve 92.
At first, freezing running is described.So-called this freezing running, same with the foregoing description 2, be that near in accordance with regulations temperature (for example ,-26 ℃) makes heat dump 58 work, the running of cooling off refrigerating chamber 22.In this freezing running, utilize not shown control device, make the 1st expansion valve 65 Close Alls, the 2nd expansion valve is opened to the liquid refrigerant of suitable amount in accordance with regulations decompression by this expansion valve 66, the aperture that heat dump 58 is played a role is closed triple valve 92 simultaneously.
In this freezing running, if running compressor 1, the cold-producing medium of discharging from compressor 1 just is cooled by being dispelled the heat by radiator 2.Thereafter, the cold-producing medium that comes out from radiator 2 arrives expansion valve 3, is depressurized at this, becomes 2 phase mixtures of gas/liquid, imports gas-liquid separator 4 from refrigerant piping 4A.Then, separated cold-producing medium in this gas-liquid separator 4 arrives branch point 9C by refrigerant piping 4B, after the 2nd expansion valve 66 is depressurized, with heat dump 58 evaporations, from absorbing heat on every side.Then, the cold-producing medium that comes out from heat dump 58, from junction of two streams 9D via check-valves 53 after, turn back to the suction inlet of compressor 1A.Thus, in this freezing running, cooling refrigerating chamber 22.
Then, the refrigeration running is described.In addition, so-called should the refrigeration running, same with the foregoing description 2, be that near temperature high by than above-mentioned freezing running time the (for example ,-5 ℃) makes above-mentioned heat dump 57 work, the running of refrigerated compartment 21.In this refrigeration running, utilize not shown control device, the 1st expansion valve 65 is opened to the liquid refrigerant of suitable amount in accordance with regulations decompression by this expansion valve 66, the aperture that heat dump 57 is played a role, Close All the 2nd expansion valve 66, switch three-way valve 92 is communicated with refrigerant piping 92C and 92B simultaneously.That is, close the refrigerant piping 92A side of triple valve 92.
Even in this refrigeration running, if running compressor 1, the cold-producing medium of discharging from compressor 1 just is cooled by being dispelled the heat by radiator 2.Then, the cold-producing medium that comes out from radiator 2 arrives expansion valve 3, is depressurized at this, becomes 2 phase mixtures of gas/liquid, imports gas-liquid separator 4 from refrigerant piping 4A.Then, separated cold-producing medium in this gas-liquid separator 4 arrives branch point 9C by refrigerant piping 4B, after the 1st expansion valve 65 is depressurized, with heat dump 57 evaporations, from absorbing heat on every side.Then, the cold-producing medium from heat dump 57 comes out by triple valve 92, is passed to refrigerant piping 9B, after via check-valves 53, turns back to the suction inlet of compressor 1A from junction of two streams 9D.Thus, in this refrigeration running, refrigerated compartment 21.
In addition, the freezing and refrigeration running is described.So-called this freezing and refrigeration running is that near near temperature (for example, make heat dump 57-5 ℃, make heat dump 58-26 ℃) makes heat dump 57 and heat dump 58 work, the running of refrigerated compartment 21 and refrigerating chamber 22 simultaneously in accordance with regulations.In the running of this freezing and refrigeration, utilize not shown control device, the 1st expansion valve 65 is all opened, promptly be opened to suitable the 3rd heat-absorbing body 10B and gas-liquid separator 4 etc. and form middle the pressure equally, the 2nd expansion valve 66 is measured the liquid refrigerant of decompression by this expansion valve 66 in accordance with regulations, the aperture that heat dump 58 is played a role, switch three-way valve 92 is communicated with refrigerant piping 92C side and 92B side simultaneously.That is, close the refrigerant piping 92B side of triple valve 92.
Even in the running of this freezing and refrigeration, if running compressor 1, the cold-producing medium of discharging from compressor 1 just is cooled by being dispelled the heat by radiator 2.Then, the cold-producing medium that comes out from radiator 2 arrives expansion valve 3, is depressurized at this, becomes 2 phase mixtures of gas/liquid, imports gas-liquid separator 4 from refrigerant piping 4A.Then, the cold-producing medium that separates in this gas-liquid separator 4 arrives branch point 9C, and a side is logical towards the 4th heat-absorbing body 11B effluent, by heat dump 58 evaporations, after absorbing heat on every side, via check-valves 53, imports the suction inlet of compressor 1A from junction of two streams 9D.In addition, the opposing party is logical towards the 3rd heat-absorbing body 10B effluent, evaporating by heat dump 57, after absorbing heat on every side, at junction of two streams 9F, with arrive triple valve 92 from refrigerant piping 92C, from triple valve 92 via refrigerant piping 92A, in refrigerant piping 4C, flow by mixing such as gas-liquid separator 4 gas separated cold-producing mediums.In addition then, via check-valves 7, import the suction inlet of 2 sections compressor 1B.Thus, in the running of this freezing and refrigeration, refrigerated compartment 21 and refrigerating chamber 22.
As above detailed description, refrigerating plant 70 according to present embodiment, can distinguish individual operation each heat-absorbing body 10B, 11B by forming, get final product the formation of freezing running of independent operation and refrigeration running, can apply high load capacity to either party chamber in each chamber 21,22, when needs are concentrated the cooling of this side chamber, also can carry out each running separately, can improve freeze cycle efficient and cooling capacity.In addition, when not needing each chamber 21,22 of individual operation, when perhaps refrigerating chamber 21 and refrigerating chamber 22 being applied high load etc., also can obtain high cooling capacity by selecting the freezing and refrigeration running as mentioned above.
In addition, the refrigerating plant 70 of present embodiment, same with the refrigerating plant 50 of the foregoing description 2, also can be used in refrigerator certainly.
More than, by the various embodiments described above the present invention has been described, but the present invention is not limited thereto, also can implement numerous variations.For example, in the various embodiments described above, in refrigerant lines, enclose carbon dioxide coolant, but also be not limited to this, also can enclose its freon series coolant in addition etc.
In addition, in the various embodiments described above, also can as required capillary be changed to expansion valve, expansion valve is changed to capillary.
In addition, compressor 1 is not limited to 2 sections above-mentioned compressors, for example, so long as 1 section compressor, so long as that refrigerant piping 4C turns back to the middle splenium of 1 section compressor is just passable.In addition, also can be the formation that connects multiple compressors.
Claims (10)
1. refrigerating plant, possess: have the compressor of middle splenium, the radiator that is connected with the discharge side of this compressor, the 1st mechanism of decompressor that is connected with the outlet side of this radiator, flow into and become the cold-producing medium of gas-liquid mixed state by described the 1st mechanism of decompressor decompression and be separated into gas refrigerant and the gas-liquid separator of liquid refrigerant and comprising makes the 2nd mechanism of decompressor of the liquid refrigerant circulation of coming out from described gas-liquid separator and the heat-absorbing body of the 1st heat dump
The cold-producing medium that comes out from described heat-absorbing body to than splenium in the middle of described compressor described more the suction inlet of low-pressure side import,
The feature of described refrigerating plant is to possess:
The 1st refrigerant piping that the gas refrigerant that described gas-liquid separator separates is come out splenium in the middle of described imports and
The 2nd refrigerant piping that cryogen imports to described gas-liquid separator will be suppressed in the middle of the described compressor.
2. refrigerating plant as claimed in claim 1 is characterized in that: possess oil eliminator in described the 2nd refrigerant piping, it is used for being separated in contained oil in the mobile cold-producing medium of described the 2nd refrigerant piping.
3. refrigerating plant as claimed in claim 2 is characterized in that: possess oil pipe line, the oil that this oil pipe line is separated by described oil eliminator to described the 1st refrigerant piping circulation.
4. as any one described refrigerating plant in the claim 1～3, it is characterized in that:
Described heat-absorbing body possesses: comprises the 1st heat-absorbing body of the 3rd mechanism of decompressor and the 2nd heat dump and possesses and comprise the 2nd heat-absorbing body of the 4th mechanism of decompressor and the 3rd heat dump with the 1st heat-absorbing body side by side,
Wherein, described the 2nd mechanism of decompressor comprises the 3rd mechanism of decompressor and the 4th mechanism of decompressor, and described the 1st heat dump comprises the 2nd heat dump and the 3rd heat dump,
The mode that can import to the suction inlet of the low-pressure side of described compressor behind the cold-producing medium interflow of coming out according to the cold-producing medium that comes out from described the 1st heat-absorbing body with from described the 2nd heat-absorbing body constitutes,
From the refrigerant piping of cold-producing medium before described interflow that described the 1st heat-absorbing body comes out, possess and be used for switching mechanism that the refrigerant piping that makes the cold-producing medium circulation of coming out from described the 1st heat-absorbing body is switched, be connected with described the 1st refrigerant piping from a side's of this switching mechanism branch refrigerant piping.
5. refrigerating plant as claimed in claim 4 is characterized in that: described the 2nd heat dump and described the 3rd heat dump, under different temperature, work selectively.
6. refrigerating plant as claimed in claim 5 is characterized in that: compare with described the 2nd heat dump, described the 3rd heat dump is more being worked under the low temperature.
7. as any one described refrigerating plant in the claim 1～3,5,6, it is characterized in that: described compressor is with by the cold-producing medium of the 1st section compressing section compresses, again with the further 2 sections compressors of compression of the 2nd section compression unit.
8. as any one described refrigerating plant in the claim 1～3,5,6, it is characterized in that:, wherein, adopt carbon dioxide as cold-producing medium with the high-voltage section of supercriticality running freeze cycle.
9. as any one described refrigerating plant in the claim 1～3,5,6, it is characterized in that: adopt carbon dioxide as cold-producing medium.
10. a refrigerator is characterized in that: possess as any one described refrigerating plant in the claim 1～9.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005100184A JP2006275495A (en) | 2005-03-30 | 2005-03-30 | Refrigerating device and refrigerator |
| JP2005100184 | 2005-03-30 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1840986A CN1840986A (en) | 2006-10-04 |
| CN100387914C true CN100387914C (en) | 2008-05-14 |
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|---|---|---|---|
| CNB2006100598985A Expired - Fee Related CN100387914C (en) | 2005-03-30 | 2006-03-21 | Refrigerating device and refrigerator |
Country Status (4)
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| US (1) | US20060230782A1 (en) |
| EP (1) | EP1707899A2 (en) |
| JP (1) | JP2006275495A (en) |
| CN (1) | CN100387914C (en) |
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| JP2009133585A (en) * | 2007-11-30 | 2009-06-18 | Daikin Ind Ltd | Refrigerating device |
| JP4964160B2 (en) * | 2008-02-04 | 2012-06-27 | 三菱電機株式会社 | Refrigeration cycle equipment |
| JP2009204220A (en) * | 2008-02-27 | 2009-09-10 | Daikin Ind Ltd | Refrigerating device |
| WO2010137120A1 (en) * | 2009-05-26 | 2010-12-02 | 三菱電機株式会社 | Heat pump type hot water supply device |
| CA2778365C (en) * | 2009-11-18 | 2018-07-03 | Shell Internationale Research Maatschappij B.V. | Method of handling a boil off gas stream and an apparatus therefor |
| JP5573302B2 (en) * | 2010-03-31 | 2014-08-20 | ダイキン工業株式会社 | Refrigeration equipment |
| JP5287831B2 (en) * | 2010-10-29 | 2013-09-11 | 株式会社デンソー | Two-stage boost refrigeration cycle |
| DE102011079206A1 (en) * | 2011-07-14 | 2013-01-17 | BSH Bosch und Siemens Hausgeräte GmbH | Refrigerating appliance with several chambers |
| DE102011122248A1 (en) * | 2011-12-23 | 2013-06-27 | Gea Bock Gmbh | compressor |
| US9696077B2 (en) | 2012-02-21 | 2017-07-04 | Whirlpool Corporation | Dual capillary tube / heat exchanger in combination with cycle priming for reducing charge migration |
| US9285161B2 (en) | 2012-02-21 | 2016-03-15 | Whirlpool Corporation | Refrigerator with variable capacity compressor and cycle priming action through capacity control and associated methods |
| US9618246B2 (en) | 2012-02-21 | 2017-04-11 | Whirlpool Corporation | Refrigeration arrangement and methods for reducing charge migration |
| US9140478B2 (en) * | 2012-05-21 | 2015-09-22 | Whirlpool Corporation | Synchronous temperature rate control for refrigeration with reduced energy consumption |
| JP5770157B2 (en) * | 2012-12-28 | 2015-08-26 | 三菱電機株式会社 | Refrigeration equipment |
| US20150369526A1 (en) * | 2013-02-07 | 2015-12-24 | Panasonic Intellectual Property Management Co., Ltd. | Sealed compressor and refrigeration device |
| EP2868998B1 (en) * | 2013-11-04 | 2023-08-23 | LG Electronics Inc. | Refrigerator |
| US10309704B2 (en) | 2013-11-25 | 2019-06-04 | The Coca-Cola Company | Compressor with an oil separator between compressing stages |
| US10139143B2 (en) * | 2013-12-17 | 2018-11-27 | Lennox Industries Inc. | Air conditioner with multiple expansion devices |
| DE102014213542A1 (en) * | 2014-07-11 | 2016-01-14 | Siemens Aktiengesellschaft | Method for operating a heat pump with at least two evaporators |
| DE102014217673A1 (en) * | 2014-09-04 | 2016-03-10 | BSH Hausgeräte GmbH | Refrigerating appliance and chiller for it |
| CN106568269B (en) * | 2016-10-24 | 2019-08-27 | 青岛海尔股份有限公司 | Refrigerator |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN1840986A (en) | 2006-10-04 |
| US20060230782A1 (en) | 2006-10-19 |
| EP1707899A2 (en) | 2006-10-04 |
| JP2006275495A (en) | 2006-10-12 |
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