CN101144656A - Air conditioner - Google Patents
Air conditioner Download PDFInfo
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- CN101144656A CN101144656A CNA200710104123XA CN200710104123A CN101144656A CN 101144656 A CN101144656 A CN 101144656A CN A200710104123X A CNA200710104123X A CN A200710104123XA CN 200710104123 A CN200710104123 A CN 200710104123A CN 101144656 A CN101144656 A CN 101144656A
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- Prior art keywords
- heat exchanger
- cold
- mentioned
- producing medium
- subcooler
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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
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/001—Compression cycle type
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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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
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0401—Refrigeration circuit bypassing means for the 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0417—Refrigeration circuit bypassing means for the subcooler
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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
- F25B2600/2515—Flow 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
This invention relates to an air conditioner. The indoor heat exchanger (25) of the interior unit (2) in the air conditioner (1) has the first heat exchanger (26) and the second heat exchanger (27), and the second heat exchanger (27) is connected to the first heat exchanger 26 by the branch pipe (28). The branch pipe (28) which establishes the flow control valve (31) is connected to the inside channel (35) of the refrigerant type subcooler (32). The refrigerant type subcooler (32) has double tube structure and inflow the outside channel (41) by the refrigerant of the second heat exchanger (27). The second heat exchanger (27) functions as an air cooling subcooler. For this reason, the first heat exchanger 26 has sufficient capacity to change a gas refrigerant into an abbreviated saturated liquid state at the time of cooling operation.
Description
Technical field
The present invention relates to air-cooled type subcooler and aircondition with subcooler.
Background technology
Aircondition circulates between off-premises station heat exchanger and indoor heat converter according to the cold-producing medium that compressor is sprayed and carries out the mode that cold-room operation and greenhouse move and constitute.Known have: when cold-room moves, if will supply with indoor set after the cold-producing medium supercooling, then can the efficient of freeze cycle be improved in the gasification that prevents liquid refrigerant from off-premises station towards the pipe arrangement of indoor set.As the mechanism that is used for the supercooling cold-producing medium, can list the subcooler that utilizes with the cold-producing medium formula of the heat exchange of the subcooler of the air-cooled type of the heat exchange of air and utilization and cold-producing medium.
At this, in the existing aircondition, when cold-room moves, will supply with the air-cooled type subcooler after by accumulator and carry out supercooling, and utilize cold-producing medium formula subcooler to carry out supercooling (for example, with reference to patent documentation 1) once more then by the chilled cold-producing medium of outdoor heat converter.Liquid refrigerant from the air-cooled type subcooler flows out is diverged and is reduced pressure afterwards as low-temperature heat source the supply system cryogen formula subcooler by capillary (capillary) in its part.Remaining liquid refrigerant is directly supplied with subcooler as high temperature heat source.In cold-producing medium formula subcooler, after seizing the heat that is equivalent to evaporation latent heat (latent heat) from the liquid refrigerant towards indoor set, the cold-producing medium that is depressurized as low-temperature heat source gasifies, thus will be towards the cold-producing medium supercooling of indoor set.In addition, as the cold-producing medium that low-temperature heat source diverged, under the state of bypass (bypass) indoor set, reclaim by compressor.
Patent documentation 1: TOHKEMY 2006-90563 communique
But, if make part fork generate low-temperature heat source by the liquid refrigerant behind the air-cooled type subcooler, then the pressure of liquid refrigerant (supplying with the cold-producing medium of indoor set) reduces, and its result flows into cold-producing medium formula subcooler under the state that the supercooling degree that is obtained by the air-cooled type subcooler reduces.For this reason, be difficult to obtain sufficient supercooling degree.
In order to improve the supercooling degree in the cold-producing medium formula subcooler, need only the amount of the cold-producing medium that increases fork as low-temperature heat source, but the pressure of liquid refrigerant when the amount of the cold-producing medium that diverges increases (supplying with the cold-producing medium of indoor set) further reduces, and subcooler descends thus.Like this, in the existing aircondition, exist and improve the supercooling degree more, the cold-room ability reduces such problem more.
Summary of the invention
The present invention makes in view of such truth, and its main purpose is to obtain sufficient supercooling degree.
In order to solve the above problems, the invention that claim 1 of the present invention is relevant, it is a kind of aircondition, it makes the cold-producing medium inflow heat exchanger after the compressor compresses and carries out heat exchange with air and move cold-room or operation greenhouse, the above-mentioned heat exchanger of off-premises station, has first heat exchanger that when cold-room moves, becomes condenser and when greenhouse moves, become evaporimeter, become the air-cooled type subcooler when moving and when greenhouse moves, become second heat exchanger of evaporimeter with cold-room, and a part that the cold-room operation time makes the cold-producing medium that flows out from above-mentioned first heat exchanger fork and make the bypass loop of indoor set bypass before flowing into above-mentioned second heat exchanger is set, and flow rate regulating valve is set on above-mentioned bypass loop, the cold-producing medium that flows through above-mentioned bypass loop with employing makes by the further overcooled cold-producing medium formula subcooler of the cold-producing medium after the above-mentioned second heat exchanger supercooling.
This aircondition, the part with first heat exchanger institute condensed refrigerant during cold-room operation does not flow into cold-producing medium formula subcooler by the air-cooled type subcooler.If with this cold-producing medium as low-temperature heat source and with the cold-producing medium of second heat exchanger institute air cooling as high temperature heat source, then make towards the further supercooling of the cold-producing medium of off-premises station by cold-producing medium formula subcooler.
According to the present invention, to carry out supercooling cold-producing medium before by air cooling uses as low-temperature heat source, and make the further supercooling of cold-producing medium after the supercooling of air cooling institute, the pressure that prevents the cold-producing medium after the caused supercooling of air cooling thus reduces, thereby can improve the ability of cold-producing medium formula subcooler.For this reason, supercooling degree can be fully guaranteed, thereby the gasification of the liquid refrigerant in the pipe arrangement can be prevented towards the cold-producing medium of off-premises station.In addition, having under the situation of a plurality of indoor sets, can prevent the generation of the ability between indoor set.
Description of drawings
Fig. 1 is the figure of the schematic configuration of the relevant aircondition of expression embodiments of the present invention.
Fig. 2 is the chart of the relation of expression bypass amount and cold-room ability, supercooling degree.
Fig. 3 is the figure of schematic configuration that expression is provided with the aircondition of accumulator.
Fig. 4 is the outside drawing of expression off-premises station.
Among the figure: 1,61-aircondition, 2,62-off-premises station, 3-off-premises station, 25-outdoor heat converter, 26-the first heat exchanger, 27-the second heat exchanger, 30,36,64-bypass pipe arrangement (bypass loop), 31-flow rate regulating valve, 32-cold-producing medium formula subcooler, 63-accumulator, 71-outer box, 74-discharge fan, 81,82-suction inlet (opening).
The specific embodiment
With reference to accompanying drawing the best mode that is used to carry out an invention is described in detail.In addition, in each following embodiment, identical inscape is paid same symbol.In addition, omit the explanation that repeats in each embodiment.
(first embodiment)
As shown in Figure 1, aircondition 1, wherein off-premises station 2 and indoor set 3 is situated between and is connected by liquid pipe arrangement 4 and gas pipe arrangement 5.Indoor set 3, wherein two indoor units 10 connect side by side.Each indoor unit 10, wherein indoor heat converter 11 and expansion valve 12 are connected in series, and air are sent into the periphery of indoor heat converter 11 by fan 13.Among Fig. 1, indoor set 3 is made of two indoor units 10, but the number of indoor unit also can be one, also can be for more than three.
Off-premises station 2 has the compressor 21 that is used for compressed gas refrigerant, the ejection pipe arrangement 22 that is connected with the ejiction opening of compressor 21, is connected with the first port 23a of cubic valve 23.Four directions valve 23 has four ports, when the first port 23a is connected with the second port 23b the 3rd port 23c is connected with the 4th port 23d.When in addition, the first port 23a is connected with the 3rd port 23c the second port 23b is connected with the 4th port 23d.The second port 23b of four directions valve 23 is connected with the inflow outlet of outdoor heat converter 25 by pipe arrangement 24.
Bifurcated pipe 28 has and is used for making when cold-room moves from the inflow outlet of the first heat exchanger 26 bypass pipe arrangement 30 (bypass loop) towards the part fork of the liquid refrigerant of the inflow outlet of second heat exchanger 27, and bypass pipe arrangement 30 is provided with flow rate regulating valve 31 backs and is connected with cold-producing medium formula subcooler 32.Flow rate regulating valve 31 is to generate the mechanism that is used at the low-temperature heat source of cold-producing medium formula subcooler 32 uses when the refrigerant amount of institute's bypass is adjusted, and carries out aperture control by control device 33.
Cold-producing medium formula subcooler 32 has the double pipe structure, and the inlet 35a of inboard stream 35 is connected with the bypass pipe arrangement 30 of bifurcated pipe 28.The outlet 35b of inboard stream 35 is situated between and is connected with accumulator 40 by bypass pipe arrangement 36 (bypass loop).In addition, the pipe arrangement 42 that is connected with a side's of the stream 41 in the outside inflow outlet 41a when being provided with greenhouse behind the employed expansion valve 43, exporting with the inflow of second heat exchanger 27 and to be connected.The opposing party's of the stream 41 in the outside inflow outlet 41b is connected with liquid pipe arrangement 44.Liquid pipe arrangement 44, flow into outlet 41b near be provided for measuring the thermometer 45 of the temperature of cold-producing medium, being situated between simultaneously is connected with liquid pipe arrangement 4 by valve 46.
In addition, gas pipe arrangement 5 Jie are connected with gas pipe arrangement 48 by valve 47.Gas pipe arrangement 48 is connected with the 3rd port 23c of cubic valve 23.The 4th port 23d of four directions valve 23 is connected with pipe arrangement 49.Pipe arrangement 49 is connected with accumulator 40 after collaborating with the bypass pipe arrangement 36 that extends from cold-producing medium formula subcooler 32 halfway.Be extended with suction pipe arrangement 50 from accumulator 40, its suction inlet with compressor 21 is connected.
Then, the action to this aircondition 1 describes.
Cold-room when operation, the first port 23a of cubic valve 23 is connected with the second port 23b, and the 3rd port 23c is connected with the 4th port 23d.In addition, flow rate regulating valve is opened a little.From the gas refrigerant of the HTHP of compressor 21 ejection first heat exchanger 26 by cubic valve 23 supply chamber outer heat-exchangers 25.First heat exchanger 26 plays a role as condenser, and gas refrigerant carries out heat exchange with the air of being sent here by blowing fan 29, and forms roughly saturated liquid refrigerant.This liquid refrigerant flows out its a part of the supply system cryogen formula subcooler 32 from bifurcated pipe 28.At this moment, by the flow rate regulating valve of opening a little 31, become the liquid refrigerant of low temperature after the thermal expansion of breaking.The liquid refrigerant of this low temperature flows into the stream 35 of the inboard of cold-producing medium formula subcooler 32 as low-temperature heat source.On the other hand, the liquid refrigerant from bifurcated pipe 28 inflows second heat exchanger 27 carries out supercooling by the air-supply that blowing fan 29 is finished.This liquid refrigerant is by a side's of the stream 41 in the outside of pipe arrangement 42 inflow cold-producing medium formula subcoolers 32 inflow outlet 41a.This liquid refrigerant becomes the relatively large high temperature heat source of described relatively its heat of low-temperature heat source.
In the cold-producing medium formula subcooler 32, between the refrigerant of low temperature of the liquid refrigerant of flows outside and flows inside, carry out heat exchange.Particularly, the cold-producing medium of stream 35 that becomes the inboard of low-temperature heat source seizes heat from the liquid refrigerant of the stream 41 in the outside that becomes high temperature heat source and gasifies.Thus, make the amount of the required evaporation latent heat of the cold-producing medium evaporation of stream 35 of liquid refrigerant supercooling inboard of stream 41 in the outside.Liquid refrigerant after the supercooling is supplied with indoor set 3 by liquid pipe arrangement 44.
In the indoor set 3, carry out heat exchange, seize the laggard promoting the circulation of qiization of the heat that is equivalent to evaporation latent heat from air by indoor heat converter 11.Thus, use cooled air that indoor (cold-room) cooled off.Reclaim by off-premises station 2 by gas pipe arrangement 5 from indoor heat converter 11 effluent air cold-producing mediums.In the off-premises station 2, the 3rd port 23c, the 4th port 23d by cubic valve 23 flows into pipe arrangement 49 from gas pipe arrangement 48, behind the gas refrigerant interflow that flows into from cold-producing medium formula subcooler 32, flows into accumulator 40.Further, suck by compressor 21 from accumulator 40 gas refrigerants.
At this, on one side the temperature of control device 33 one side monitoring temperature meters 45 is adjusted the aperture of flow rate regulating valve 31.As shown in Figure 2, supercooling degree in the cold-producing medium formula subcooler 32, increase and the amount of the cold-producing medium that the inboard of cold-producing medium formula subcooler 32 passes through is increased along with the bypass amount increases just aperture with flow rate regulating valve 31, the ability of cold-producing medium formula subcooler 32 is risen.The supercooling degree of air-cooled type subcooler does not rely on the constant that is changed to of bypass amount, thus, increases as the supercooling degree of the total of air-cooled type subcooler and cold-producing medium formula subcooler 32.Though reduce the refrigerant amount of supplying with indoor set 3 by increasing the bypass amount, but owing to increase as the supercooling degree that amounts to, so the difference of the thermal content (enthalpy) between can the entrance and exit of formula indoor heat converter 11 increases, and can suppress the reduction of cold-room ability thus.For example, if the supercooling degree of the liquid refrigerant that will flow out from cold-producing medium formula subcooler 32 forms 20K, even then when liquid pipe arrangement 4 is longer or indoor unit 10 have when a plurality of, liquid refrigerant does not gasify yet halfway, and can obtain sufficient cold-room ability.
In addition, greenhouse when operation, close flow rate regulating valve 31 and do not use cold-producing medium formula subcooler 32.In addition, two sides with first, second heat exchanger 26,27 use as evaporimeter.Second heat exchanger 27 also uses as evaporimeter, can improve the greenhouse ability thus.
This embodiment, air-cooled type subcooler and cold-producing medium formula subcooler 32 are with roughly parallel way setting, with the air-cooled type subcooler overcooled previous cold-producing medium import cold-producing medium formula subcooler 32 as low-temperature heat source, even also can make the supercooling degree stable during the air themperature change thus.As prior art, under the situation with two kinds of subcooler series connection settings, because the part of the liquid refrigerant behind the air cooling is used as low-temperature heat source, so the pressure of liquid refrigerant reduces and the supercooling degree of cold-producing medium formula subcooler 32 inlets reduces, even the supercooling degree is increased by cold-producing medium formula subcooler 32, but in the present embodiment, because the cold-producing medium before the air cooling is used as low-temperature heat source, the ability of cold-producing medium formula subcooler 32 is increased.Though the amount of the cold-producing medium that indoor set 3 is circulated by bypass reduces, owing to make the ability increase of cold-producing medium formula subcooler 32 and can prevent that the cold-room ability from reducing significantly.Thus, during for long pipe arrangement or be connected with under the situation of many indoor units 10, can prevent the ability reduction of indoor unit 10 or the discrete discrepancy of ability at liquid pipe arrangement 4 and gas pipe arrangement 5.
(second embodiment)
As shown in Figure 3, aircondition 61, its outdoor heat converter 25 have first heat exchanger 26 and second heat exchanger 27, and these heat exchangers 26,27 Jie are connected by accumulator 63.Further, from accumulator 63 with liquid refrigerant the supply system cryogen formula subcooler 32.More specifically, the pipe arrangement 62 that is connected with the inflow outlet (flow export during the cold-room operation) of first heat exchanger 26 is inserted in the accumulator 63.The pipe arrangement 65 that is connected with the inflow outlet (inflow entrance during the cold-room operation) of second heat exchanger 27 also is inserted in the accumulator 63.Be extended with the bypass pipe arrangement 66 that is used to form bypass loop from the roughly bottom of accumulator 63, after flow rate regulating valve 31 is set, be connected with the inlet 35a of the stream 35 of the inboard of cold-producing medium formula subcooler 32.Other structure is identical with first embodiment.
Then, the action to this aircondition 61 describes.
During the cold-room operation, the gas refrigerant that compressor 21 is sprayed flows into first heat exchanger 26.First heat exchanger 26 forms the liquid refrigerant of high pressure thus as condenser performance function by heat exchange.This liquid refrigerant flows into accumulator 63 from pipe arrangement 64.Liquid refrigerant reduces pressure by being detained in accumulator 63.Bypass pipe arrangement 66 is connected with the roughly bottom of accumulator 63, because flow rate regulating valve 31 is opened a little, so only take out the cold-producing medium that the utmost point is similar to saturated liquid, after by flow rate regulating valve 31 decompression, as the stream 35 of the inboard of low-temperature heat source the supply system cryogen formula subcooler 32.
In addition, also supply with liquid refrigerant from accumulator 63 to second heat exchanger 27.Liquid refrigerant to second heat exchanger 27 (air-cooled type subcooler) is supplied with further carries out supercooling by cold-producing medium formula subcooler 32 after air cooling is by supercooling, supply with indoor set 3.
In addition, the liquid refrigerant that is used for low-temperature heat source that is taken out is sucked by compressor 21 under the state of bypass indoor set 3.The aperture of flow rate regulating valve 31 is according to by similarly measuring the supercooling degree for example to make the supercooling degree be that the mode of 20K is adjusted with above-mentioned.
During the greenhouse operation, close flow rate regulating valve 31.Second heat exchanger 27 can be brought into play higher greenhouse ability thus as its effect of evaporimeter except that first heat exchanger 26.
According to this embodiment, the part of liquid refrigerant was diverged from accumulator 63 before by the air-cooled type subcooler, use as the low-temperature heat source of cold-producing medium formula subcooler 32, can obtain the effect identical thus with first embodiment.Particularly, use accumulator 63 when the cold-producing medium that low-temperature heat source is used diverges, can make the aridity of cold-producing medium of institute's bypass minimum thus.Thus, the inlet 35a of low-temperature heat source side of cold-producing medium formula subcooler 32 and the difference of the thermal content of outlet between the 35b are increased.Thereby, when being carried out bypass, identical refrigerant amount also can increase the supercooling degree, and not only suppress the decline of cold-room ability thus, and improve the supercooling degree.
The service condition change further, condenser (first heat exchanger 26) separated with the function of air-cooled type subcooler (second heat exchanger 27), even also can make the ability of air-cooled type subcooler stable thus by accumulator 63.
(the 3rd embodiment)
Fig. 4 represents the outside drawing of the off-premises station 2 of aircondition 1.Off-premises station 2 wherein is accommodated in each inscape in the outer box 71 of cuboid roughly.On the top surface 72 of box 71 outlet 73 is set outside, and disposes discharge fan 74 (blowing fans) at this.The sidepiece of box 71 is front 75, two sides 76,77 and the back sides 78 outside, forms suction inlet 81,82 (suction inlet at the side 77 and the back side 78 is not shown) respectively as the opening that is used to be taken into air.75 inboard disposes second heat exchanger 27 that works as the air-cooled type subcooler according to the mode of facing with suction inlet in front.First heat exchanger 26 disposes according to the mode of facing with two sides 76,77 and the back side 78 suction inlet 82 separately, for example shown in dotted line like that, in the plane is looked, form roughly U word shape.In addition, each face 75～78 also can all form suction inlet.In addition, also can form suction inlet in the part of the panel that is used to form each face.
If aircondition 1 operation, the then discharge on top fan 74 rotation.Air is inhaled into from four suction inlets 81,82 of four faces 75～78 of side, discharges from the outlet 73 on top by first, second heat exchanger 26,27.At this moment, and the cold-producing medium that flows of first, second heat exchanger 26,27 between carry out heat exchange.
In this off-premises station 2, dispose first, second heat exchanger 26,27, can improve thus and discharge fan efficient according in looking, surrounding the mode of discharging fan 74 along the plane of the direction of the rotating shaft of discharging fan 74.For this reason, can not only not reduce the air quantity that in first heat exchanger 26, flows, and make the full blast amount be increased in the amount of the air quantity that flows in second heat exchanger 27.Will first heat exchanger 26 and second heat exchanger 27 separately in flow air guarantee that respectively air separately can not exert an influence to the characteristic of mutual heat exchanger thus, thereby can obtain stable performance.Hence one can see that, when cold-room moves, can obtain bigger supercooling degree when guaranteeing the condensation ability, even also can suppress the reduction of cold-room ability under the state of long pipe arrangement.Also can seek to follow the air quantity increase when in addition, greenhouse moves and the greenhouse ability is improved.
At this, also the off-premises station 62 of the aircondition in second embodiment 61 can be formed identical shape.Can obtain and above-mentioned same effect and effect.
In addition, the present invention is defined in each above-mentioned embodiment, can use broad.
In addition, thermometer 45 is arranged on the outlet 35b side of stream 35 of the inboard of cold-producing medium formula subcooler 32, can infers the supercooling degree of the liquid refrigerant of supplying with indoor set 3 according to the temperature of the cold-producing medium that flows out, the aperture of controlling flow rate regulating valve 31 also can.
Also second heat exchanger 27 can be configured in the above scope in two sides among Fig. 4.First heat exchanger 26 also can only be disposed at one side, also can be configured in the scope at two sides or four sides.
Claims (3)
1. an aircondition makes by the cold-producing medium inflow heat exchanger after the compressor compresses and carries out heat exchange with air and move greenhouse or cold-room,
The above-mentioned heat exchanger of off-premises station, has first heat exchanger that when cold-room moves, becomes condenser and when greenhouse moves, become evaporimeter, become the air-cooled type subcooler when moving and when greenhouse moves, become second heat exchanger of evaporimeter with cold-room, and a part that the cold-room operation time makes the cold-producing medium that flows out from above-mentioned first heat exchanger fork and with the bypass loop of indoor set bypass before flowing into above-mentioned second heat exchanger is set, and flow rate regulating valve is set on above-mentioned bypass loop, the cold-producing medium that flows through above-mentioned bypass loop with employing makes by the further overcooled cold-producing medium formula subcooler of the cold-producing medium after the above-mentioned second heat exchanger supercooling.
2. aircondition according to claim 1 is characterized in that,
Between above-mentioned first heat exchanger and above-mentioned second heat exchanger, accumulator is set, and the roughly bottom of above-mentioned accumulator is connected with above-mentioned bypass loop.
3. according to claim 1 or the described aircondition of claim 2, it is characterized in that,
Above-mentioned off-premises station has the outer box of the roughly cuboid of the fan that air-supply usefulness is installed, dispose above-mentioned first heat exchanger and above-mentioned second heat exchanger according to observing the mode that surrounds said fans from the rotating shaft direction of said fans in the box outside above-mentioned, the sidepiece of facing with above-mentioned first heat exchanger and above-mentioned second heat exchanger of box is formed with the opening that is used for ventilating air outside above-mentioned.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006249470 | 2006-09-14 | ||
| JP2006249470A JP2008070053A (en) | 2006-09-14 | 2006-09-14 | Air conditioner |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101144656A true CN101144656A (en) | 2008-03-19 |
Family
ID=39207306
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA200710104123XA Pending CN101144656A (en) | 2006-09-14 | 2007-05-16 | Air conditioner |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2008070053A (en) |
| KR (1) | KR20080024937A (en) |
| CN (1) | CN101144656A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102105758A (en) * | 2008-09-16 | 2011-06-22 | 拉斯·克里斯汀·伍尔夫·齐默曼 | Symmetric refrigerant regulator for flooded multichannel evaporator |
| CN102679609A (en) * | 2012-06-07 | 2012-09-19 | 四川同达博尔置业有限公司 | Air-cooled heat pump air conditioner |
| CN103256748A (en) * | 2011-12-12 | 2013-08-21 | 三星电子株式会社 | Air conditioner |
| CN104272036A (en) * | 2012-04-25 | 2015-01-07 | 株式会社日立制作所 | Air-conditioning/hot-water supply system |
| CN104729162A (en) * | 2013-12-24 | 2015-06-24 | 珠海格力电器股份有限公司 | Cooling system and air conditioner with same |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011007482A (en) * | 2009-05-29 | 2011-01-13 | Daikin Industries Ltd | Air conditioner |
| KR101118137B1 (en) * | 2011-08-25 | 2012-03-14 | 주식회사 티알엑서지 | Air cooling type heat pump system |
-
2006
- 2006-09-14 JP JP2006249470A patent/JP2008070053A/en active Pending
- 2006-11-17 KR KR1020060113931A patent/KR20080024937A/en not_active Application Discontinuation
-
2007
- 2007-05-16 CN CNA200710104123XA patent/CN101144656A/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102105758A (en) * | 2008-09-16 | 2011-06-22 | 拉斯·克里斯汀·伍尔夫·齐默曼 | Symmetric refrigerant regulator for flooded multichannel evaporator |
| CN103256748A (en) * | 2011-12-12 | 2013-08-21 | 三星电子株式会社 | Air conditioner |
| CN104272036A (en) * | 2012-04-25 | 2015-01-07 | 株式会社日立制作所 | Air-conditioning/hot-water supply system |
| CN104272036B (en) * | 2012-04-25 | 2016-11-09 | 株式会社日立制作所 | Air regulation hot water supply system |
| CN102679609A (en) * | 2012-06-07 | 2012-09-19 | 四川同达博尔置业有限公司 | Air-cooled heat pump air conditioner |
| CN104729162A (en) * | 2013-12-24 | 2015-06-24 | 珠海格力电器股份有限公司 | Cooling system and air conditioner with same |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2008070053A (en) | 2008-03-27 |
| KR20080024937A (en) | 2008-03-19 |
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