CN103229004A - Air conditioner device - Google Patents
Air conditioner device Download PDFInfo
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- CN103229004A CN103229004A CN201180057064XA CN201180057064A CN103229004A CN 103229004 A CN103229004 A CN 103229004A CN 201180057064X A CN201180057064X A CN 201180057064XA CN 201180057064 A CN201180057064 A CN 201180057064A CN 103229004 A CN103229004 A CN 103229004A
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- heat exchanger
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- producing medium
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
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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
- F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
- F25B2313/0254—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements
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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
- F25B2400/12—Inflammable refrigerants
- F25B2400/121—Inflammable refrigerants using R1234
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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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Other Air-Conditioning Systems (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The present invention obtains an air conditioner device that can decrease the diameter of a low-pressure gas piping even when a refrigerant having a low refrigerant density at a low pressure is used. The air conditioner device is provided with: a refrigerant cycling circuit (10) in which a compressor (1), a heat-source-side heat exchanger (3), a throttle device (20), and a use-side heat exchanger (21) are connected by piping, and in which a refrigerant with a saturated refrigerant gas density at 0 DEG C being 35-65% of that of a R410A refrigerant is circulated; and a supercooling means (a supercooling heat exchanger (4), a throttle device (5), and a bypass loop (7)) that, during a cooling operation, enables the liquid temperature of a high-pressure liquid refrigerant sent from the heat-source-side heat exchanger (3) to the throttle device (20) to be no greater than 5 DEG C.
Description
Technical field
The present invention relates to aircondition.
Background technology
Before, there is a kind of aircondition, has supercooling mechanism, use the bypass-side cold-producing medium, will deliver to the refrigerant cools (for example with reference to patent documentation 1) of throttling arrangement from condenser.In aircondition with this supercooling mechanism, reduce owing to be sent to the circulating mass of refrigerant of throttling arrangement, so, can reduce the evaporimeter of throttling arrangement back segment and the pressure loss that prolongs pipe arrangement.
Technical literature formerly
Patent documentation
Patent documentation 1: Japanese kokai publication hei 6-265232 communique (Fig. 1, the 6th page)
Summary of the invention
The problem that invention will solve
In recent years, viewpoint for greenhouse effects of the earth, the trend of the HFC series coolant that restricted use greenhouse effects of the earth coefficient is high (for example R410A, R404A, R407C, R134a etc.) has proposed to use the aircondition of the little cold-producing medium (for example HFO1234yf, carbon dioxide etc.) of greenhouse effects of the earth coefficient.HFO1234yf compares with R410A, and the refrigerant density during low pressure reduces significantly, and the pressure characteristic under the uniform temp is more much lower than R410A.The little cold-producing medium of refrigerant density during this low pressure is used in when carrying out cooling operation in the aircondition, and the influence of the pressure loss in the low-pressure gas pipe arrangement is very big.Therefore, there is the problem that must strengthen the pipe arrangement diameter in order to reduce the pressure loss.
Especially use in the such big system of multi-connected air conditioner (10HP) at building, when using R410A, the diameter of low-pressure gas pipe arrangement is
About, and during the little cold-producing medium of the refrigerant density when using low pressure, the diameter of low-pressure gas pipe arrangement is the about 2 times of above-mentioned diameter
About.Therefore, the buckling work of pipe arrangement is very difficult, and processing cost rises significantly.In addition, the refrigerant piping of this thick pipe arrangement diameter uses on the market, usually hardly so price increases substantially.A big problem during the little cold-producing medium of the refrigerant density when for this reason, using low pressure is the diameter that reduces the low-pressure gas pipe arrangement.
The aircondition of patent documentation 1 record as mentioned above, is effective reducing aspect the pressure loss.But the little cold-producing medium of the refrigerant density when not considering to use low pressure is as the duty cryogen, so the effect that reduces of the pressure loss is not very big.Therefore, the little cold-producing medium of refrigerant density when merely using low pressure in this aircondition as mentioned above, can not solve the problem of the significantly big footpathization of low-pressure gas pipe arrangement.
The present invention makes in order to solve above-mentioned problem, even also can reduce the aircondition of low-pressure gas pipe arrangement diameter when the little cold-producing medium of the refrigerant density that provides when adopting low pressure is provided.
Solve the technical scheme of problem
Aircondition of the present invention, have: refrigerant circulation loop, connect compressor, heat source side heat exchanger, throttling arrangement and utilize the side heat exchanger with pipe arrangement, the saturated refrigerant gas density in the time of 0 ℃ is that 35～65% cold-producing medium of R410A cold-producing medium circulates in this refrigerant circulation loop; And supercooling mechanism, when cooling operation, making the liquid temperature of delivering to the high pressure liquid refrigerant of throttling arrangement from the heat source side heat exchanger is below 5 ℃.
The invention effect
According to the present invention, when cooling operation, making the liquid temperature of delivering to the high pressure liquid refrigerant of throttling arrangement from the heat source side heat exchanger is below 5 ℃, so, can improve refrigerating effect, can reduce refrigerant flow.Therefore, can reduce the diameter of low-pressure fitting pipe.
Description of drawings
Fig. 1 is the summary circuit structure figure that the loop of the aircondition of expression embodiment of the present invention 1 one of constitutes example.
Fig. 2 is the refrigerant loop figure that flows of the cold-producing medium of aircondition when the cooling operation pattern of expression embodiment of the present invention 1.
Fig. 3 is the figure of the structure example of the dual tubular type supercooling heat exchanger of expression.
Fig. 4 is the curve map of the relation of expression liquid temperature and flow-rate ratio.
Fig. 5 is an expression liquid temperature and the curve map of the relation of pressure loss ratio.
Fig. 6 is an expression liquid temperature and the curve map of the relation of pipe arrangement diameter ratio.
Fig. 7 is the refrigerant loop figure that flows of the cold-producing medium of aircondition when heating operation mode of expression embodiment of the present invention 1.
Fig. 8 is the summary circuit structure figure that the loop of the aircondition of expression embodiment of the present invention 2 one of constitutes example.
Fig. 9 is the refrigerant loop figure that flows of the cold-producing medium of aircondition when the cooling operation pattern of expression embodiment of the present invention 2.
Figure 10 is the cold and hot simultaneous type of embodiment of the present invention 3() the circuit structure figure of aircondition.
The specific embodiment
Below, with reference to the description of drawings embodiments of the present invention.
Fig. 1 is the summary circuit structure figure that the loop of the aircondition of expression embodiment of the present invention 1 one of constitutes example.Below, with reference to Fig. 1, illustrate that the detailed loop of aircondition constitutes.In Fig. 1, be that example is represented with the situation that has connected 4 indoor sets 20.In addition, in comprising the following drawings of Fig. 1, the magnitude relationship of each component parts and reality are inequality sometimes.In addition, in Fig. 1 and aftermentioned figure, the parts of annotating with same tag are identical or suitable parts, and this point all is the same in specification full text.In addition, the mode of the inscape of setting forth in the specification full text only as exemplifying, is not limited to the mode of being put down in writing.
As shown in Figure 1, aircondition 100 constitutes, and is generically and collectively referred to as indoor set 20 sometimes below off-premises station (heat source machine) 10 and the indoor set 20a～20d() be generically and collectively referred to as prolongation pipe arrangement 400 by prolonging pipe arrangement 400a and prolonging sometimes below the 400b() be connected.That is, in aircondition 100, many indoor sets 20 are connected in parallel with respect to off-premises station 10.Prolonging pipe arrangement 400 is refrigerant pipings that cold-producing medium (heat source side cold-producing medium) passes through.In addition, in aircondition 100, HFO1234y or HFO1234ze have been enclosed as cold-producing medium.
[off-premises station 10]
Off-premises station 10 has flow passage selector device 2, heat source side heat exchanger 3, supercooling heat exchanger 4 and reservoirs 6 such as compressor 1, cross valve, pass through pipe arrangement, utilize side heat exchanger 21 and throttling arrangement 22 to be connected with the aftermentioned of indoor set 20, constituted the refrigerant circulation loop of cold-producing medium circulation.Off-premises station 10 also has the supercooling heat exchanger 4 between heat source side heat exchanger 3 and throttling arrangement 22.In addition, off-premises station 10 has bypass circulation 7, and this bypass circulation 7 is connected to the entrance side of reservoir 6 from branch between supercooling heat exchanger 4 and the throttling arrangement 22 via the low-pressure side of throttling arrangement 5 and supercooling heat exchanger 4.Supercooling heat exchanger 4 makes the high-pressure side cold-producing medium between heat source side heat exchanger 3 and the throttling arrangement 22 and at throttling arrangement 5 the post-decompression low-pressure side cold-producing medium of the part of high-pressure side cold-producing medium is carried out heat exchange, with the high-pressure side refrigerant cools.
Heat source side heat exchanger (outdoor heat exchanger) 3 plays a role as evaporimeter heating when running, plays a role as radiator when cooling operation, is carrying out heat exchange from omitting between air that pressure fans such as illustrated fan supply with and the cold-producing medium.Reservoir 6 is located at the suction side of compressor 1, the different residual refrigerant that produce when being used to accumulate when heating operation mode with the cooling operation pattern, changes the residual refrigerant that (for example variation of the operating number of indoor set 2) produces with respect to the running of transition.
In addition, the outlet (hydraulic fluid side) at supercooling heat exchanger 4 is provided with pressure sensor 8 and temperature sensor 9.At off-premises station 10, also be provided with the sensor various sensors such as (not shown) of the inlet temperature and the discharge temperature that are used to detect compressor 1.
Be provided with control device 10A at off-premises station 10.Control device 10A is connected to, and can receive the various sensors in the off-premises station 10 and the detection signal of the various sensors of aftermentioned in the indoor set 20.Control device 10A according to the detection signal from various sensors, carries out the controls such as adjustment such as aperture of throttling arrangement 5 and throttling arrangement 22.In addition, control device 10A by the switching of flow passage selector device 2, carries out cooling operation pattern and the running that heats operation mode.Among Fig. 1, expression only is provided with the formation of control device 10A at off-premises station 10, but the sub-control device of the partial function with control device 10A also can be set in each indoor set 20, utilize the data communication between control device 10A and the sub-control device to carry out online process.
[indoor set 20]
In indoor set 20, utilize side heat exchanger (indoor side heat exchanger) 21(21a～21d) and throttling arrangement 22(22a～22d) be connected in series, constituted the part of refrigerant circulation loop.Utilize side heat exchanger 21 when heating running, to play radiator, when cooling operation, play evaporimeter, carrying out heat exchange from omitting between air that pressure fan such as illustrated fan supplies with and the cold-producing medium, generating and be used to supply with the heating of air-conditioning object space with air or cooling air.Throttling arrangement 22 has the function of pressure-reducing valve, expansion valve, and with cold-producing medium decompression and it is expanded, for example electronic expansion valve that can be controlled changeably by aperture etc. constitutes.
In embodiment 1, be that example is represented with the situation that has connected 4 indoor sets 20.Among the figure,, be expressed as indoor set 20a, indoor set 20b, indoor set 20c, indoor set 20d successively from the left side.In addition, with indoor set 20a～20d accordingly, utilize side heat exchanger 21, also from the left side, be expressed as successively and utilize side heat exchanger 21a, utilize side heat exchanger 21b, utilize side heat exchanger 21c, utilize side heat exchanger 21d.Similarly, throttling arrangement 22 also from the left side, is expressed as throttling arrangement 22a, throttling arrangement 22b, throttling arrangement 22c, throttling arrangement 22d successively.In addition, the connection platform number of indoor set 20 is not limited to 4.
In indoor set 20, be provided with temperature sensor 23a～23d, 24a～24d in the refrigerating fluid discharging and feeding of utilizing side heat exchanger 21.The detection signal of temperature sensor 23a～23d, 24a～24d is output to control device 10A.Be in the off-premises station control of control device 10A enforcement in the present embodiment, still, also can control device be set, control indoor set 20a～20d with this control device at each indoor set to indoor set.
In aircondition 100, as mentioned above, cold-producing medium uses HFO1234yf or the HFO1234ze as low pressure refrigerant.The saturated gas density of these cold-producing mediums in the time of 0 ℃ is as shown in table 1.As can be known from Table 1, with respect to the gas density of R410A, HFO1234yf is 58%, and HFO1234ze is 38%.That is to say, compare that the gas density the during low pressure of this cold-producing medium is about 35～65% with the R410A cold-producing medium that uses in present most airconditions.In addition, this value is from NIST(National Institute of Standards and Technology, national standard and technical research institute) obtain among the REFPROP Version8.0 that sells.
[table 1]
| Cold-producing medium | R410A | HFO1234yf | HFO1234ze |
| Saturated gas density [kg/m 3] | 30.575 | 17.646 | 11.724 |
Like this, during the little cold-producing medium of using gases density, if merely flow in pipe arrangement with identical refrigerant flow (kg/hr), the flow velocity of HFO1234yf is about 2 times of R410A.Because square being directly proportional of the pressure loss and flow velocity is so the pressure loss of HFO1234yf is about 4 times of R410A.As a result, when the pipe arrangement of use and R410A cold-producing medium same diameter, the pressure loss is 4 times, and performance reduces significantly.The performance that causes in order to suppress the HFO1234yf cold-producing medium with cold-producing medium (R410A) before the equal pressure loss to be arranged reduces, and the pipe arrangement diameter must be 2 times of refrigerant piping before.HFO1234yf and HFO1234ze are roughly the same density, so the pressure loss of HFO1234yf and HFO1234ze is roughly the same value.
In the such low capacity system of room air conditioner, even with pipe arrangement enlarged diameter to 2 times, because original pipe arrangement diameter is just little, so, in processing, there is not special problem.But, use in the such hicap of multi-connected air conditioner (10HP) at building, as above in the face of described in the explanation of prior art, the pipe arrangement diameter is
About, so, bigger harmful effect is being arranged aspect application property, the processing cost.
For this reason, in present embodiment 1, make from the temperature of delivering to the high pressure liquid refrigerant of throttling arrangement 22 as the heat source side heat exchanger 3 of radiator when the cooling operation pattern to be reduced to below 5 ℃.This is the emphasis of present embodiment 1.In addition, in this example, making condensation temperature is more than 49 ℃, and the target temperature of the liquid temperature of high pressure liquid refrigerant is that the degree of supercooling below 5 ℃ the time is more than 44 ℃.Like this, the liquid temperature by making high pressure liquid refrigerant is to compare in 44 ℃ of (5 ℃ of degree of supercoolings) times with making the liquid temperature for example below 5 ℃, can improve refrigerating effect.As a result, refrigerant flow can be reduced, the pipe arrangement size can be reduced.
Below, the various operation modes that aircondition 100 is carried out are described.
[cooling operation pattern]
Fig. 2 is the refrigerant loop figure that flows of the cold-producing medium of expression aircondition 100 when the cooling operation pattern.Among Fig. 2, be that example describes with the situation that drives whole indoor set 20.Among Fig. 2, arrow is represented the flow direction of cold-producing medium.
The cold-producing medium of low-temp low-pressure is compressed by compressor 1, becomes the gas refrigerant of HTHP and discharges.The gas refrigerant of the HTHP of discharging from compressor 1 by flow passage selector device 2, flows into heat source side heat exchanger 3.
Flow into the gas refrigerant of the HTHP of heat source side heat exchanger 3, by with carry out heat exchange from omitting the air that illustrated pressure fan supplies with, become liquid condition, flow out from heat source side heat exchanger 3.The cold-producing medium of the liquid condition that flows out from heat source side heat exchanger 3 flows into the high-pressure side of supercooling heat exchanger 4.A part of having passed through the cold-producing medium of supercooling heat exchanger 4 is become the cold-producing medium of the gas-liquid two-phase of low pressure by the decompression of the throttling arrangement 5 of bypass circulation 7, flows into the low-pressure side of supercooling heat exchanger 4.Like this, the on high-tension side liquid refrigerant of supercooling heat exchanger 4 carries out heat exchange with the cold-producing medium of low-pressure side and cools off, and liquid temperature drop low (increase degree of supercooling) also flows out from supercooling heat exchanger 4.The low pressure two-phase system cryogen of the low-pressure side of supercooling heat exchanger 4 carries out heat exchange with on high-tension side cold-producing medium and becomes the gas refrigerant of low pressure, comes out from supercooling heat exchanger 4, flows to reservoir 6.
Here, as mentioned above, in this example, adjust the aperture of throttling arrangement 5, the liquid temperature of the high pressure liquid refrigerant of supercooling heat exchanger 4 outlets is reduced to about 5 ℃.Like this, because the refrigerating effect raising, so the opening ratio of throttling arrangement 5 reduces when for example degree of supercooling is 5 ℃.Therefore, reduced utilizing the cold-producing medium quantity delivered of side heat exchanger 21.As a result, can reduce the pipe arrangement size.In addition, the aperture adjustment of throttling arrangement 5 be according to pressure sensor 8 and temperature sensor 9 detection signal, undertaken by control device 10A.
The supercooling heat exchanger 4 of present embodiment 1 as shown in Figure 3, adopts dual tube side formula, and the high-pressure side cold-producing medium is that high pressure liquid refrigerant flows at annulus, and the low-pressure side cold-producing medium is that gas-liquid two-phase system cryogen flows in interior pipe.This is because if make gas-liquid two-phase system cryogen flow to annulus, and liquid refrigerant can be partial to the bottom of annulus and cause heat exchange performance to reduce.
In addition, supercooling heat exchanger 4 is not limited to dual tube side formula, also can adopt heat-exchangers of the plate type.When adopting heat-exchangers of the plate type, high pressure liquid refrigerant flows (stream in opposite directions) from top to bottom by low-pressure gas-liquid two-phase system cryogen is flowed from the bottom up, can bring into play heat exchanger performance effectively.
Liquid refrigerant from supercooling heat exchanger 4 flows out by prolonging pipe arrangement 400a, towards indoor set 20, flows into indoor set 20a～indoor set 20d respectively.Flow into the cold-producing medium of indoor set 20a～indoor set 20d, expand (decompression) by throttling arrangement 22a～throttling arrangement 22d respectively, become the gas-liquid two-phase state of low-temp low-pressure.The cold-producing medium of this gas-liquid two-phase state flows into respectively and utilizes side heat exchanger 21a～utilize side heat exchanger 21d.Flow into and utilize side heat exchanger 21a～the utilize cold-producing medium of the gas-liquid two-phase state of side heat exchanger 21d, with carry out heat exchange and from air, absorb heat from omitting air (room air) that illustrated pressure fan supplies with, become the gas refrigerant of low pressure, flow out from utilizing side heat exchanger 21a～utilize side heat exchanger 21d.
Here, to the cold-producing medium quantity delivered of utilizing side heat exchanger 21, adjust according to the temperature sensor 23a～23d that is located at the refrigerating fluid discharging and feeding of utilizing side heat exchanger 21, the temperature information of 24a～24d.Specifically, control device 10A obtains the information from these temperature sensors 23a～23d, 24a～24d, according to the information that obtains, calculates the degree of superheat (refrigerant temperature of the refrigerant temperature-inlet of outlet side).Then, the aperture of decision throttling arrangement 22 is adjusted to the cold-producing medium quantity delivered of utilizing side heat exchanger 21 so that this degree of superheat becomes about 2～5 ℃.
From the low-pressure refrigerant gas that utilizes side heat exchanger 21a～utilize side heat exchanger 21d to flow out, flow out from indoor set 20a～indoor set 20d, by prolonging pipe arrangement 400b, flow into off-premises station 10.Flow into the cold-producing medium of off-premises station 10,, flow into reservoir 6 by flow passage selector device 2.The cold-producing medium that flow into reservoir 6 is separated into liquid refrigerant and gas refrigerant, and gas refrigerant is sucked by compressor 1 once more.
Under this cooling operation pattern, carry out degree of superheat control and make the degree of superheat become positive region at each indoor set 20, so the cold-producing medium of liquid condition does not flow into reservoir 6.But in transition state or when the indoor set 20 that stops to be arranged, a spot of sometimes liquid state (about mass dryness fraction 0.95) cold-producing medium can flow into reservoir 6.Flow into after the liquid refrigerant evaporates of reservoir 6 and aspirated by compressor 1 by compressor 1 suction or via the spill port that is located at reservoir 6 outlets (omitting diagram).
Below, illustrate the high pressure liquid refrigerant temperature of supercooling heat exchanger 4 outlets is reduced to the effect that is produced about 5 ℃.Fig. 4 represents the fluid temperature of supercooling heat exchanger outlet and the relation that refrigerant flow reduces ratio.Refrigerant flow ratio during 44 ℃ of liquid temperature (5 ℃ of degree of supercoolings) is made as 1.The tentative calculation condition of other calculating is that evaporating temperature is 0 ℃, and condensation temperature is 49 ℃.
As can be seen from Figure 4, be about 5 ℃ by the outlet fluid temperature that makes supercooling heat exchanger 4, flow is liquid temperature about 66% when being 44 ℃ (5 ℃ of degree of supercoolings), flows to the refrigerant flow that prolongs pipe arrangement 400a, 400b and also reduces by 34%.
Fig. 5 is the liquid temp of expression supercooling heat exchanger outlet and the figure that the pipe arrangement pressure loss reduces the relation of ratio.Pressure loss ratio during 44 ℃ of liquid temperature (5 ℃ of degree of supercoolings) is made as 1.As can be seen from Figure 5, be about 5 ℃ by the outlet fluid temperature that makes supercooling heat exchanger 4, the pressure loss is liquid temperature about 44% when being 44 ℃ (5 ℃ of degree of supercoolings), the pressure loss that prolongs pipe arrangement 400a, 400b also reduces by 56%.
Fig. 6 is the liquid temp of expression supercooling heat exchanger outlet and the figure that the pipe arrangement diameter reduces the relation of ratio.Pipe arrangement natural scale during 44 ℃ of liquid temperature (5 ℃ of degree of supercoolings) is made as 1.As can be seen from Figure 6, when being 5 ℃ of left and right sides by the outlet fluid temperature that makes supercooling heat exchanger 4, the pipe arrangement diameter is liquid temperature about 80% when being 44 ℃ (5 ℃ of degree of supercoolings), and the diameter that prolongs pipe arrangement 400a, 400b also reduces 20%.That is, the pipe arrangement diameter can be reduced 1 to 2 rank, can reduce to prolong the diameter of pipe arrangement 400a, 400b.The influence of the pressure loss that the low-pressure fitting pipe that gas refrigerant passes through promptly prolongs pipe arrangement 400b is big, and pipe arrangement 400a is thick than prolonging.Therefore, the pipe arrangement diameter that prolongs pipe arrangement 400b can be reduced the effect that 1～2 rank can obtain to reduce pipe arrangement cost, raising application property, reduction construction cost, very effective.
[heating operation mode]
Fig. 7 is the refrigerant loop figure that flows of the cold-producing medium of expression aircondition 100 when heating operation mode.Among Fig. 7, be that example describes with the situation that drives whole indoor set 20.Among Fig. 7, arrow is represented the flow direction of cold-producing medium.In addition, heating under the operation mode, throttling arrangement 5 cuts out.
The cold-producing medium of low-temp low-pressure is compressed by compressor 1, becomes the gas refrigerant of HTHP and discharges.The gas refrigerant of the HTHP of discharging from compressor 1 by flow passage selector device 2, flows out from off-premises station 10, by prolonging pipe arrangement 400b, flows into indoor set 20a～indoor set 20d respectively.
Flow into the gas refrigerant of the HTHP of indoor set 20a～indoor set 20d, utilizing side heat exchanger 21a～utilize side heat exchanger 21d, with carry out heat exchange and dispel the heat from omitting air (room air) that illustrated pressure fan supplies with to air, become liquid condition, flow out from utilizing side heat exchanger 21a～utilize side heat exchanger 21d.The liquid refrigerant of this high pressure is expanded (decompression) by throttling arrangement 22a～throttling arrangement 22d respectively, becomes the gas-liquid two-phase state of low-temp low-pressure, flows out from indoor set 20a～indoor set 20d.
To the cold-producing medium quantity delivered of utilizing side heat exchanger 21, according to adjusting from the information of temperature sensor 23a～23d that is located at the refrigerant outlet that utilizes side heat exchanger 21 and pressure sensor (not shown).Specifically, use from the information of these sensors and calculate degree of supercooling (refrigerant temperature of the saturation temperature-outlet side that converts from the detected pressures of the cold-producing medium of outlet side), the aperture of decision throttling arrangement 22 is adjusted the cold-producing medium quantity delivered to heat source side heat exchanger 3 so that this degree of supercooling becomes about 2～5 ℃.
The cold-producing medium of the gas-liquid two-phase state of the low-temp low-pressure that flows out from indoor set 20a～indoor set 20d by prolonging pipe arrangement 400a, flows into off-premises station 10.This cold-producing medium flows into heat source side heat exchanger 3 directly by supercooling heat exchanger 4.Flow into the cold-producing medium of gas-liquid two-phase state of the low-temp low-pressure of heat source side heat exchanger 3, and carry out heat exchange from omitting the air that illustrated pressure fan supplies with, from the air heat absorption, mass dryness fraction increases gradually.Then,, become the gas-liquid two-phase system cryogen of the big state of mass dryness fraction, flow out from heat source side heat exchanger 3 in the outlet of heat source side heat exchanger 3.Cold-producing medium from heat source side heat exchanger 3 flows out by flow passage selector device 2, flows into reservoir 6.The cold-producing medium that flow into reservoir 6 is separated into liquid refrigerant and gas refrigerant, and gas refrigerant is sucked by compressor 1 once more.
In the loop of present embodiment 1, heating under the operation mode, flow into the refrigerant flow that prolongs pipe arrangement 400b though can not reduce, but, to prolong among the pipe arrangement 400b be high-pressure gas refrigerant (cold-producing medium that density is big) owing to flow to, so the influence of the pressure loss is little, make cold-producing medium not flow to supercooling heat exchanger 4.In addition, when making cold-producing medium flow to supercooling heat exchanger 4, also can reduce the diameter of the low-pressure fitting pipe (pipe arrangement of the inlet of the outlet → evaporimeter of supercooling heat exchanger 4 → reservoir 6) of off-premises station 10.In addition, heating under the operation mode similarly, can make from the liquid temperature of utilizing side heat exchanger 21 to deliver to the high pressure liquid refrigerant of throttling arrangement 22 becomes below 5 ℃, and degree of supercooling is become more than 44 ℃.
As mentioned above, according to present embodiment 1, when the cooling operation pattern, by the high pressure liquid temperature being reduced to about 5 ℃, the diameter that prolongs pipe arrangement (low-pressure gas pipe arrangement) 400b can be reduced 1～2 rank with supercooling mechanism (supercooling heat exchanger 4, throttling arrangement 5 and bypass circulation 7).As a result, can reduce pipe arrangement cost and construction cost, and, can reduce the energy loss that causes because of discarded, also help environmental protection.In addition, owing to can reduce the pressure loss, so, can carry out the high running of efficiency, also have energy-saving effect.
In embodiment 1, constitute supercooling mechanism by supercooling heat exchanger 4, throttling arrangement 5 and bypass circulation 7, and in embodiment 2, the refrigerant circulation loop of being used by supercooling constitutes supercooling mechanism.
Fig. 8 is the skeleton diagram of the aircondition of embodiment of the present invention 2.This aircondition 101 has refrigerant circulation loop 101A and supercooling loop 101B.In addition, in embodiment 2, the difference of main explanation and embodiment 1, the part identical with embodiment 1 annotated with same tag.In addition, concrete example and modified example to the same structure with embodiment 1 partly is suitable for are applicable to present embodiment too.This point in embodiment described later too.
[refrigerant circulation loop 101A]
[supercooling loop 101B]
Supercooling has compressor 31, condenser 32, throttling arrangement 33 and supercooling heat exchanger 34 with loop 101B, and they have constituted the freeze cycle cold-producing medium circulation, that play the effect of supercooling mechanism by the pipe arrangement connection.Supercooling heat exchanger 34 makes the low-pressure side cold-producing medium that circulates in loop 101B in supercooling and at the heat source side heat exchanger 3 of refrigerant circulation loop 101A and the high-pressure side cold-producing medium between the throttling arrangement 22, carries out heat exchange.
Each equipment except utilizing side heat exchanger 21 and throttling arrangement 22 among the refrigerant circulation loop A and supercooling loop 101B are arranged in the same casing, constitute off-premises station 30.In addition, supercooling is being carried the little compressor of Capacity Ratio compressor 1 with the compressor 31 of loop 101B.
Be provided with control device 30A at off-premises station 30.Control device 30A is connected to, and can receive the various sensors in the off-premises station 30 and the detection signal of the various sensors of aftermentioned in the indoor set 20.Control device 30A carries out the controls such as aperture adjustment of throttling arrangement 33 and throttling arrangement 22 according to the detection signal from various sensors.In addition, control device 30A by the switching of flow passage selector device 2, carries out cooling operation pattern and the running that heats operation mode.Among Fig. 8, expression only is provided with control device 30A at off-premises station 30, but, the sub-control device of the partial function with control device 30A also can be set at each indoor set 20, utilize the data communication between control device 30A and the sub-control device to carry out online process.
Below, each operation mode that aircondition 101 is carried out is described.
[cooling operation pattern]
Fig. 9 is the refrigerant loop figure that flows of the cold-producing medium of aircondition when the cooling operation pattern of expression embodiment of the present invention 2.Among Fig. 9, be that example describes with the situation that drives whole indoor set 20.Among Fig. 9, arrow is represented the flow direction of cold-producing medium.
The action of refrigerant circulation loop 101A at first is described.The cold-producing medium of low-temp low-pressure is compressed by compressor 1, becomes the gas refrigerant of HTHP and discharges.The gas refrigerant of the HTHP of discharging from compressor 1 by flow passage selector device 2, flows into heat source side heat exchanger 3.
Flow into the gas refrigerant of the HTHP of heat source side heat exchanger 3, and carry out heat exchange, become liquid condition, flow out, flow into supercooling heat exchanger 34 from heat source side heat exchanger 3 from omitting the air that illustrated pressure fan supplies with.The liquid refrigerant that flow into supercooling heat exchanger 34 is by the gas-liquid two-phase refrigerant cools that generates with loop 101B in supercooling, and liquid temperature drop low (increase degree of supercooling) flows out from supercooling heat exchanger 34.
Here, in embodiment 2, also with embodiment 1 similarly, the liquid temperature of the high pressure liquid refrigerant of supercooling heat exchanger 34 outlet is reduced to about 5 ℃.The temperature of this high pressure liquid refrigerant depends on the heat exchange amount in the supercooling heat exchanger 34.Therefore, by adjusting the supercooling aperture of the throttling arrangement 33 of loop 101B, the rotating speed of compressor 31, it is about 5 ℃ that the liquid temperature of the high pressure liquid refrigerant of supercooling heat exchanger 34 outlets is reduced to.As a result, can obtain the effect same with embodiment 1.
Liquid refrigerant from supercooling heat exchanger 34 flows out by prolonging pipe arrangement 400a, towards indoor set 20, flows into indoor set 20a～indoor set 20d respectively.The cold-producing medium that flow into indoor set 20a～indoor set 20d is expanded (decompression) by throttling arrangement 22a～throttling arrangement 22d respectively, becomes the gas-liquid two-phase state of low-temp low-pressure.The cold-producing medium of this gas-liquid two-phase state flows into respectively and utilizes side heat exchanger 21a～utilize side heat exchanger 21d.Flow into and utilize side heat exchanger 21a～the utilize cold-producing medium of the gas-liquid two-phase state of side heat exchanger 21d, with carry out heat exchange and from air, absorb heat from omitting air (room air) that illustrated pressure fan supplies with, become the gas refrigerant of low pressure, flow out from utilizing side heat exchanger 21a～utilize side heat exchanger 21d.
Here, to the cold-producing medium quantity delivered of utilizing side heat exchanger 21, adjust according to the temperature sensor 23a～23d that is located at the refrigerating fluid discharging and feeding of utilizing side heat exchanger 21, the temperature information of 24a～24d.Specifically, control device 30A according to the temperature information from these temperature sensors 23a～23d, 24a～24d, calculates the degree of superheat (refrigerant temperature of the refrigerant temperature-entrance side of outlet side).Then, with embodiment 1 similarly, the aperture of decision throttling arrangement 22 is adjusted to the cold-producing medium quantity delivered of utilizing side heat exchanger 21 so that this degree of superheat becomes about 2～5 ℃.
From the low-pressure refrigerant gas that utilizes side heat exchanger 21a～utilize side heat exchanger 21d to flow out, flow out from indoor set 20a～indoor set 20d, by prolonging pipe arrangement 400b, flow into off-premises station 10.Flow into the cold-producing medium of off-premises station 10,, flow into reservoir 6 by flow passage selector device 2.The cold-producing medium that flow into reservoir 6 is separated into liquid refrigerant and gas refrigerant, and gas refrigerant is sucked by compressor 1 once more.
Under this cooling operation pattern, carry out degree of superheat control at each indoor set 20, so the cold-producing medium of liquid condition does not flow into reservoir 6.But,, have a spot of liquid state (about mass dryness fraction 0.95) cold-producing medium sometimes and flow into reservoir 6 in transition state or when the indoor set 20 that stops to be arranged.Aspirated by compressor 1 after flowing into the liquid refrigerant evaporates of reservoir 6, perhaps aspirated by compressor 1 via the spill port on the outlet pipe arrangement that is located at reservoir 6 (omitting diagram).
Below, the action of supercooling with loop 101B is described.Cold-producing medium is compressed by compressor 31, becomes the gas refrigerant of HTHP and discharges.The gas refrigerant of the HTHP of discharging from compressor 31 flows into condenser 32.Flow into the gas refrigerant of the HTHP of condenser 32, and carry out heat exchange, become liquid condition, flow out flow throttling device 33 from condenser 32 from omitting the air that illustrated pressure fan supplies with.As mentioned above, adjust the aperture of throttling arrangement 33, so that the temperature of the high pressure liquid refrigerant of supercooling heat exchanger 34 outlets is reduced to about 5 ℃.The cold-producing medium that flow into throttling arrangement 33 is depressurized the gas-liquid two-phase flow that becomes low pressure, flows into supercooling heat exchanger 34.Flow into the liquid refrigerant of supercooling heat exchanger 34, carry out heat exchange with the high pressure liquid refrigerant that generates at refrigerant circulation loop 101A.Gas-liquid two-phase system cryogen after the heat exchange becomes the gas refrigerant of low pressure, flows out from supercooling heat exchanger 34, is aspirated by compressor 31 once more.
In embodiment 2, also with embodiment 1 similarly, with supercooling heat exchanger 34 temperature of the high pressure liquid refrigerant that flows out from supercooling heat exchanger 34 is reduced to about 5 ℃.As a result, with embodiment 1 similarly, the pipe arrangement diameter that prolongs pipe arrangement (low-pressure gas pipe arrangement) 400b can be reduced 1～2 rank, can reduce pipe arrangement cost and construction cost.
In the loop of present embodiment 2, with embodiment 1 similarly, when heating operation mode, flow into the refrigerant flow that prolongs pipe arrangement 400b though can not reduce, but, be the gas refrigerant (cold-producing medium that density is big) of high pressure owing to what flow into, so, the influence of the pressure loss is little, does not make cold-producing medium flow to supercooling heat exchanger 34.That is, supercooling is not turned round with loop 101B.
In addition, in present embodiment 2, use among the 101B of loop at refrigerant circulation loop 101A and supercooling, use identical cold-producing medium HFO1234yf or HFO1234ze, but also can be in supercooling with using the little cold-producing medium of other greenhouse effects of the earth coefficient, for example carbon dioxide, HC cold-producing medium etc. among the 101B of loop.
In the aircondition of embodiment 3, can carry out the off-premises station 10 of off-premises station 40 employings of the refrigeration and the aircondition of heating type embodiment 1 shown in Figure 1 or the off-premises station 30 of embodiment 2 shown in Figure 8 simultaneously.
Figure 10 is the general structural map of the aircondition of embodiment of the present invention 3.Among Figure 10, expression has the situation of the off-premises station 10 among off-premises station 10 or the off-premises station 30.
This aircondition 102 is made of heat source machine (off-premises station) 40, thermal medium transcriber 60 and indoor set 50 substantially.Off-premises station 40 and thermal medium transcriber 60 via heat exchanger 61b between heat exchanger 61a and thermal medium between the thermal medium in the thermal medium transcriber 60, connect with refrigerant piping 401.In addition, thermal medium transcriber 60 and indoor set 50 also via heat exchanger 61b between heat exchanger 61a and thermal medium between thermal medium, connect with pipe arrangement 500.
[off-premises station 40]
Off-premises station 40 as mentioned above, has each equipment and the various sensor of the off-premises station 10 that constitutes embodiment 1 shown in Figure 1, with embodiment 1 and embodiment 2 similarly, the liquid temperature of high pressure liquid refrigerant is reduced to about 5 ℃.In addition,, flow towards a direction, also be provided with 4 check valve 41a～41d in order to make cold-producing medium at off-premises station 40.Under the situation that constitutes such loop, can only in cooling operation, reduce the temperature of high pressure liquid refrigerant.
The 1st connecting pipings 42a in off-premises station 40, couples together the refrigerant piping 401 between the refrigerant piping 401 between flow passage selector device 2 and the check valve 41d and check valve 41a and the thermal medium transcriber 60.The 2nd connecting pipings 42b in off-premises station 40, couples together the refrigerant piping 401 between the refrigerant piping 401 between check valve 41d and the thermal medium transcriber 60 and heat source side heat exchanger 12 and the check valve 41a.In addition, among Figure 10, expression is provided with the example of the 1st connecting pipings 42a, the 2nd connecting pipings 42b, check valve 41a, check valve 41b, check valve 41c and check valve 41d, but is not limited thereto, and not necessarily leaves no choice but be provided with these parts.
In addition, be provided with control device 40A at off-premises station 40.Control device 40A is connected to, and can receive the detection signal of the various sensors in off-premises station 40, indoor set 50 and the thermal medium transcriber 60.Control device 40A according to the detection signal from various sensors, carries out the controls such as aperture adjustment of throttling arrangement 5 and throttling arrangement 22.In addition, control device 10A by the switching of flow passage selector device 2, carries out cooling operation pattern and the running that heats operation mode.Among Figure 10, expression only is provided with the structure of control device 40A at off-premises station 40, but, the sub-control device of the partial function with control device 40A also can be set at each indoor set 50 and thermal medium transcriber 60, utilize the data communication between control device 30A and the sub-control device to carry out online process.In addition, also control device 30A can be set, can also control device 30A be set at thermal medium transcriber 60 in each unit.
[indoor set 50]
In indoor set 50, carried load side heat exchanger 51(51a～51d) respectively.This load side heat exchanger 51 is by pipe arrangement 500, with the heat medium flow amount adjusting apparatus 74(74a of thermal medium transcriber 60～74d) and the 2nd heat medium flow circuit switching device 73(73a～73d) be connected.This load side heat exchanger 51 makes from the air and the thermal medium that omit the air-conditioning object space that pressure fan such as illustrated fan supplies with and carries out heat exchange, generates to be used to supply with the heating with air or cooling air of the interior space.
Among this Figure 10, illustration 4 situations that indoor set 50 is connected with thermal medium transcriber 60.Among the figure,, be expressed as indoor set 50a, indoor set 50b, indoor set 50c, indoor set 50d successively from the below.In addition, with indoor set 50a～50d accordingly, load side heat exchanger 51 also from the below, is expressed as load side heat exchanger 51a, load side heat exchanger 51b, load side heat exchanger 51c, load side heat exchanger 51d successively.In addition, with Fig. 1 and Fig. 2 similarly, the platform number of indoor set 50 is not defined as shown in Figure 10 4.
[thermal medium transcriber 60]
Thermal medium transcriber 60 is equipped with heat exchanger 61(61a, 61b between 2 thermal mediums), 2 throttling arrangement 62(62a, 62b), 2 opening and closing device 63(63a, 63b), 2 flow passage selector device 64(64a, 64b), 2 pump 71(71a, 71b), 4 the 1st heat medium flow circuit switching device 72(72a～72d), 4 the 2nd heat medium flow circuit switching device 73(73a～73d) and 4 heat medium flow amount adjusting apparatus 74(74a～74d).Between thermal medium heat exchanger 61 be equivalent to constitute above-mentioned embodiment 1,2 refrigerant circulation loop utilize the side heat exchanger.
Heat exchanger 61b between heat exchanger 61a, thermal medium between heat exchanger 61(thermal medium between 2 thermal mediums), function with condenser (radiator) or evaporimeter, between heat source side cold-producing medium and thermal medium, carry out heat exchange, give thermal medium the cold energy or the thermal energy transfer that generate and be accumulated in the heat source side cold-producing medium at off-premises station 40.Heat exchanger 61a is located between the throttling arrangement 62a and flow passage selector device 64a among the refrigerant circulation loop A between thermal medium, when cooling and warming mixing operation mode, is used for the heating of thermal medium.In addition, heat exchanger 61b is located between the throttling arrangement 62b and flow passage selector device 64b among the refrigerant circulation loop A between thermal medium, when cooling and warming mixing operation mode, is used for the cooling of thermal medium.Here, be provided with heat exchanger 61 between 2 thermal mediums, but also can be provided with 1, also can be provided with more than 3.
2 throttling arrangement 62(throttling arrangement 62a, throttling arrangement 62b), have the function of pressure-reducing valve, expansion valve, the decompression of heat source side cold-producing medium is made its expansion.Be located at the upstream side of heat exchanger 61a between thermal medium in the flowing of the heat source side cold-producing medium of throttling arrangement 62a when cooling operation.Be located at the upstream side of heat exchanger 61b between thermal medium in the flowing of the heat source side cold-producing medium of throttling arrangement 62b when cooling operation.For example electronic expansion valve that 2 throttling arrangements 62 can be controlled changeably by aperture etc. constitutes.
2 opening and closing device 63(opening and closing device 63a, opening and closing device 63b) constitute by two-port valve etc., be used to open and close refrigerant piping 401.Opening and closing device 63a is located on the refrigerant piping 401 of entrance side of heat source side cold-producing medium.Opening and closing device 63b is located on the pipe arrangement that the refrigerant piping 401 with the entrance side of heat source side cold-producing medium and outlet side couples together.2 flow passage selector device 64(flow passage selector device 64a, flow passage selector device 64b) constitute by cross valve etc., according to operation mode, switch flowing of heat source side cold-producing medium.Be located at the downstream of heat exchanger 61a between thermal medium in the flowing of the heat source side cold-producing medium of flow passage selector device 64a when cooling operation.Be located at the downstream of heat exchanger 61b between thermal medium in the flowing of the heat source side cold-producing medium of flow passage selector device 64b when full cooling operation.
2 pump 71(71a, 71b as the thermal medium carrying device), make thermal medium circulation by pipe arrangement 500.Pump 71a is located between thermal medium on the pipe arrangement 500 between the heat exchanger 61a and the 2nd heat medium flow circuit switching device 73.Pump 71b is located between thermal medium on the pipe arrangement 500 between the heat exchanger 61b and the 2nd heat medium flow circuit switching device 73.2 pumps 71 can be made of pump of for example capacity controllable system etc.
4 the 1st heat medium flow circuit switching device 72(the 1st heat medium flow circuit switching device 72a～the 1st heat medium flow circuit switching device 72d) constitute by triple valve etc., be used to switch the stream of thermal medium.The 1st heat medium flow circuit switching device 72 be provided with indoor set 50 the corresponding number of platform number (being 4 here) is set.The 1st heat medium flow circuit switching device 72 is located at the outlet side of the thermal medium stream of load side heat exchanger 51, in its threeway one with thermal medium between heat exchanger 61a be connected, in the threeway one with thermal medium between heat exchanger 61b be connected, in the threeway one is connected with heat medium flow amount adjusting apparatus 74.In addition, with indoor set 50 accordingly, among the figure,, be expressed as the 1st heat medium flow circuit switching device 72a, the 1st heat medium flow circuit switching device 72b, the 1st heat medium flow circuit switching device 72c, the 1st heat medium flow circuit switching device 72d successively from the below.
4 the 2nd heat medium flow circuit switching device 73(the 2nd heat medium flow circuit switching device 73a～the 2nd heat medium flow circuit switching device 73d) constitute by triple valve etc., be used to switch the stream of thermal medium.The 2nd heat medium flow circuit switching device 73 be provided with indoor set 50 the corresponding number of platform number (being 4 here) is set.The 2nd heat medium flow circuit switching device 73 is located at the entrance side of the thermal medium stream of load side heat exchanger 51, in its threeway one with thermal medium between heat exchanger 61a be connected, in the threeway one with thermal medium between heat exchanger 61b be connected, in the threeway one is connected with load side heat exchanger 51.In addition, with indoor set 50 accordingly, among the figure,, be expressed as the 2nd heat medium flow circuit switching device 73a, the 2nd heat medium flow circuit switching device 73b, the 2nd heat medium flow circuit switching device 73c, the 2nd heat medium flow circuit switching device 73d successively from the below.
4 heat medium flow amount adjusting apparatus 74(heat medium flow amount adjusting apparatus 74a～heat medium flow amount adjusting apparatus 74d) constitute by the two-port valve that can control aperture area etc., be used for being controlled at the flow that pipe arrangement 500 flows.Heat medium flow amount adjusting apparatus 74 be provided with indoor set 50 the corresponding number of platform number (being 4 here) is set.Heat medium flow amount adjusting apparatus 74 is located at the outlet side of the thermal medium stream of load side heat exchanger 51, and a side is connected with load side heat exchanger 51, and the opposing party is connected with the 1st heat medium flow circuit switching device 72.In addition, with indoor set 50 accordingly, among the figure,, be expressed as heat medium flow amount adjusting apparatus 74a, heat medium flow amount adjusting apparatus 74b, heat medium flow amount adjusting apparatus 74c, heat medium flow amount adjusting apparatus 74d successively from the below.In addition, also heat medium flow amount adjusting apparatus 74 can be located at the entrance side of the thermal medium stream of load side heat exchanger 51.
In thermal medium transcriber 60, be provided with various checkout gears (82,4 the 3rd temperature sensors 83 of 81,4 the 2nd temperature sensors of 2 the 1st temperature sensors and pressure sensor 84).The detection signal of these checkout gears is sent to for example control device 40A, is used to control the driving frequency of compressor 1, the rotating speed of pressure fan (not shown), the switching of flow passage selector device 2, the driving frequency of pump 71, the switching of flow passage selector device 64, the switching of thermal medium stream etc.
2 the 1st temperature sensor 81(the 1st temperature sensor 81a, the 1st temperature sensor 81b) be used to detect the thermal medium that flows out from heat exchanger between thermal medium 61, be the temperature of the thermal medium in the exit of heat exchanger 61 between thermal medium, can constitute by for example thermistor etc.The 1st temperature sensor 81a is located on the pipe arrangement 500 of entrance side of pump 71a.The 1st temperature sensor 81b is located on the pipe arrangement 500 of entrance side of pump 71b.
4 the 2nd temperature sensor 82(the 2nd temperature sensor 82a～the 2nd temperature sensor 82d) be located between the 1st heat medium flow circuit switching device 72 and the heat medium flow amount adjusting apparatus 74, be used to detect the temperature of the thermal medium that flows out from load side heat exchanger 51, can constitute by thermistor etc.The 2nd temperature sensor 82 be provided with indoor set 50 the corresponding number of platform number (being 4 here) is set.In addition, with indoor set 50 accordingly, among the figure,, be expressed as the 2nd temperature sensor 82a, the 2nd temperature sensor 82b, the 2nd temperature sensor 82c, the 2nd temperature sensor 82d successively from the below.
4 the 3rd temperature sensor 83(the 3rd temperature sensor 83a～the 3rd temperature sensor 83d) be located at the entrance side or the outlet side of the heat source side cold-producing medium of heat exchanger 61 between thermal medium, the temperature of the heat source side cold-producing medium that is used to detect the temperature that flows into the heat source side cold-producing medium of heat exchanger 61 between thermal medium or flows out from heat exchanger between thermal medium 61 can be made of thermistor etc.The 3rd temperature sensor 83a is located between thermal medium between the heat exchanger 61a and flow passage selector device 64a.The 3rd temperature sensor 83b is located between thermal medium between the heat exchanger 61a and throttling arrangement 62a.The 3rd temperature sensor 83c is located between thermal medium between the heat exchanger 61b and flow passage selector device 64b.The 3rd temperature sensor 83d is located between thermal medium between the heat exchanger 61b and throttling arrangement 62b.
The pipe arrangement 500 of thermal medium conducting by with thermal medium between the pipe arrangement that is connected of heat exchanger 61a with thermal medium between the pipe arrangement that is connected of heat exchanger 61b constitute.Pipe arrangement 500 is branched (being to be divided into each 4) here according to the platform number of the indoor set 50 that is connected with thermal medium transcriber 60.Pipe arrangement 500 is connected with the 2nd heat medium flow circuit switching device 73 at the 1st heat medium flow circuit switching device 72.By the 1st heat medium flow circuit switching device 72 and the 2nd heat medium flow circuit switching device 73 being controlled, being decided is to make the thermal medium from heat exchanger 61a between thermal medium flow into load side heat exchanger 51, still make the thermal medium from heat exchanger 61b between thermal medium flow into load side heat exchanger 61a.
In aircondition 102, the refrigerant flow path of heat exchanger 61, throttling arrangement 62 and reservoir 65 between compressor 1, flow passage selector device 2, heat source side heat exchanger 3, opening and closing device 63, flow passage selector device 64, thermal medium, connect by refrigerant piping 401, constituted refrigerant circulation loop A.In addition, the thermal medium stream of heat exchanger 61, pump the 71, the 1st heat medium flow circuit switching device 72, heat medium flow amount adjusting apparatus 74, load side heat exchanger 51 and the 2nd heat medium flow circuit switching device 73 between thermal medium, connect by pipe arrangement 500, constituted thermal medium closed circuit B.That is, many load side heat exchangers 51 in parallel with each thermal medium between heat exchanger 61 be connected, B forms multisystem with the thermal medium closed circuit.
Therefore, in aircondition 102, off-premises station 40 and thermal medium transcriber 60 are connected via heat exchanger 61b between heat exchanger 61a between the thermal medium that is located in the thermal medium transcriber 60 and thermal medium, and thermal medium transcriber 60 and indoor set 50 also are connected via heat exchanger 61b between heat exchanger 61a between thermal medium and thermal medium.That is, in aircondition 102, heat source side cold-producing medium that circulates in refrigerant circulation loop A and the thermal medium that circulates in thermal medium closed circuit B at heat exchanger 61b between heat exchanger 61a and thermal medium between thermal medium, carry out heat exchange.
This aircondition 102 can according to from the indication of each indoor set 50, utilize this indoor set 50 to carry out cooling operation or heat running.That is, aircondition 102 can make whole indoor set 50 carry out identical running, and, can make each indoor set 50 carry out running inequality.
As mentioned above, according to embodiment 3, even can freeze simultaneously and the aircondition of heating type in, also with embodiment 1 and embodiment 2 similarly, the pipe arrangement diameter of low-pressure gas pipe arrangement can be reduced 1～2 rank.As a result, can reduce pipe arrangement cost and construction cost, and, can reduce the energy loss that causes because of discarded, help environmental protection.In addition, owing to can reduce the pressure loss, so, can carry out the high running of efficiency, also can obtain energy-saving effect.
In addition, thermal medium transcriber 60 also can separately constitute main thermal medium transcriber and the sub-thermal medium transcriber with gas-liquid separator and throttling arrangement.
The explanation of Reference numeral
1 ... compressor, 2 ... flow passage selector device, 3 ... the heat source side heat exchanger, 4 ... the supercooling heat exchanger, 5 ... throttling arrangement, 6 ... reservoir, 7 ... bypass circulation, 7 ... the interior space, 8 ... pressure sensor, 9 ... temperature sensor, 10 ... off-premises station, 10A ... control device, 20(20a～20d) ... indoor set, 21(21a～21d) ... utilize the side heat exchanger, 22(22a～22d) ... throttling arrangement, 23a～23d ... temperature sensor, 24a～24d ... temperature sensor, 30 ... off-premises station, 30A ... control device, 31 ... compressor, 32 ... condenser, 33 ... throttling arrangement, 34 ... the supercooling heat exchanger, 40 ... off-premises station, 40A ... control device, 41a～41d ... check valve, 42a ... the 1st connecting pipings, 42b ... the 2nd connecting pipings, 50(50a～50d) ... indoor set, 51(51a～51d) ... the load side heat exchanger, 60 ... the thermal medium transcriber, 61(61a, 61b) ... heat exchanger between thermal medium, 62(62a, 62b) ... throttling arrangement, 63(63a, 63b) ... opening and closing device, 64(64a, 64b) ... flow passage selector device, 71(71a, 71b) ... pump, 72(72a～72d) ... the 1st heat medium flow circuit switching device, 73(73a～73d) ... the 2nd heat medium flow circuit switching device, 74(74a～74d) ... the heat medium flow amount adjusting apparatus, 81(81a, 81b) ... the 1st temperature sensor, 82(82a～84d) ... the 2nd temperature sensor, 83(83a～83d) ... the 3rd temperature sensor, 84 ... pressure sensor, 100 ... aircondition, 101 ... aircondition, 101A ... refrigerant loop, 101B ... the loop is used in supercooling, 102 ... aircondition, 400(400a, 400b) ... prolong pipe arrangement, 401 ... refrigerant piping, 500 ... pipe arrangement, A ... refrigerant circulation loop, B ... the thermal medium closed circuit
Claims (9)
1. aircondition is characterized in that having:
Refrigerant circulation loop connects compressor, heat source side heat exchanger, throttling arrangement and utilizes the side heat exchanger with pipe arrangement, and the saturated refrigerant gas density in the time of 0 ℃ is that 35～65% cold-producing medium of R410A cold-producing medium circulates in this refrigerant circulation loop; And
Supercooling mechanism, when cooling operation, making the liquid temperature of delivering to the high pressure liquid refrigerant of above-mentioned throttling arrangement from above-mentioned heat source side heat exchanger is below 5 ℃.
2. aircondition as claimed in claim 1 is characterized in that, it is more than 44 ℃ that above-mentioned supercooling mechanism makes the degree of supercooling of above-mentioned high pressure liquid refrigerant.
3. aircondition as claimed in claim 1 or 2 is characterized in that, is heating when running, and making from the above-mentioned liquid temperature of utilizing the high pressure liquid refrigerant that the side heat exchanger delivers to above-mentioned throttling arrangement is below 5 ℃ or to make degree of supercooling be more than 44 ℃.
4. as each described aircondition in the claim 1 to 3, it is characterized in that, above-mentioned supercooling mechanism has the supercooling heat exchanger, this supercooling heat exchanger makes the high-pressure side cold-producing medium between above-mentioned heat source side heat exchanger and above-mentioned throttling arrangement and the post-decompression low-pressure side cold-producing medium of the part of above-mentioned high-pressure side cold-producing medium is carried out heat exchange, with above-mentioned high-pressure side refrigerant cools.
5. as each described aircondition in the claim 1 to 3, it is characterized in that above-mentioned supercooling mechanism has with pipe arrangement and connects compressor, condenser, throttling arrangement and supercooling heat exchanger and make the supercooling of cold-producing medium circulation use the loop; Above-mentioned supercooling heat exchanger makes the low-pressure side cold-producing medium that circulates in the loop in above-mentioned supercooling and carries out heat exchange at the above-mentioned heat source side heat exchanger of above-mentioned refrigerant circulation loop and the high-pressure side cold-producing medium between the above-mentioned throttling arrangement.
6. as claim 4 or 5 described airconditions, it is characterized in that above-mentioned supercooling heat exchanger is dual tubing heat exchanger, make the high-pressure side cold-producing medium low-pressure side cold-producing medium be circulated at interior pipe in the annulus circulation.
7. as claim 4 or 5 described airconditions, it is characterized in that above-mentioned supercooling heat exchanger is above-mentioned heat-exchangers of the plate type, above-mentioned high-pressure side cold-producing medium is flowed from top to bottom and above-mentioned low-pressure side cold-producing medium is flowed from the bottom up.
8. as each described aircondition in the claim 1 to 7, it is characterized in that above-mentioned cold-producing medium uses HFO1234y or HFO1234ze.
9. as each described aircondition in the claim 1 to 8, it is characterized in that,
Above-mentioned refrigerant circulation loop has between a plurality of thermal mediums heat exchanger as the above-mentioned side heat exchanger that utilizes, and heat exchanger makes above-mentioned cold-producing medium and the thermal medium that is different from above-mentioned cold-producing medium carry out heat exchange and can heat exchange becomes the thermal medium of different temperatures between above-mentioned thermal medium;
Also have with pipe arrangement and connect a plurality of pumps, load side heat exchanger and heat medium flow circuit switching device and the thermal medium closed circuit that constitutes;
Above-mentioned a plurality of pump makes between above-mentioned a plurality of thermal mediums heat exchanger carry out the above-mentioned thermal medium circulation of heat exchange respectively;
Above-mentioned load side heat exchanger makes the air of above-mentioned thermal medium and air-conditioning object space carry out heat exchange;
Above-mentioned heat medium flow circuit switching device switches the thermal medium by heat exchanger between above-mentioned a plurality of thermal mediums, makes it flow to above-mentioned load side heat exchanger.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2011/000406 WO2012101672A1 (en) | 2011-01-26 | 2011-01-26 | Air conditioner device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103229004A true CN103229004A (en) | 2013-07-31 |
| CN103229004B CN103229004B (en) | 2016-05-04 |
Family
ID=46580288
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201180057064.XA Active CN103229004B (en) | 2011-01-26 | 2011-01-26 | Aircondition |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20130213078A1 (en) |
| EP (1) | EP2669598B1 (en) |
| JP (1) | JPWO2012101672A1 (en) |
| CN (1) | CN103229004B (en) |
| AU (1) | AU2011357097B2 (en) |
| WO (1) | WO2012101672A1 (en) |
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| CN105387647A (en) * | 2015-12-10 | 2016-03-09 | 浪潮电子信息产业股份有限公司 | Novel efficient data center refrigeration and air-conditioning system |
| CN108061348A (en) * | 2017-12-29 | 2018-05-22 | 广东申菱环境系统股份有限公司 | A kind of urban track traffic integrated refrigeration station formula evaporative condenser air-conditioning system |
| CN113454408A (en) * | 2019-02-27 | 2021-09-28 | 三菱电机株式会社 | Air conditioning apparatus |
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| WO2015145712A1 (en) * | 2014-03-28 | 2015-10-01 | 日立アプライアンス株式会社 | Refrigeration cycle device |
| JP5908177B1 (en) * | 2014-06-25 | 2016-04-26 | 三菱電機株式会社 | Refrigeration cycle apparatus, air conditioner, and control method for refrigeration cycle apparatus |
| WO2019169187A1 (en) * | 2018-02-28 | 2019-09-06 | Treau, Inc. | Roll diaphragm compressor and low-pressure vapor compression cycles |
| CN108775727B (en) * | 2018-07-09 | 2023-10-24 | 浙江正理生能科技有限公司 | Refrigerating circulation system |
| JPWO2020188756A1 (en) * | 2019-03-19 | 2021-04-30 | 日立ジョンソンコントロールズ空調株式会社 | Room air conditioner |
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Also Published As
| Publication number | Publication date |
|---|---|
| AU2011357097A1 (en) | 2013-06-20 |
| EP2669598A4 (en) | 2016-12-07 |
| EP2669598A1 (en) | 2013-12-04 |
| CN103229004B (en) | 2016-05-04 |
| WO2012101672A1 (en) | 2012-08-02 |
| US20130213078A1 (en) | 2013-08-22 |
| JPWO2012101672A1 (en) | 2014-06-30 |
| AU2011357097B2 (en) | 2015-01-22 |
| EP2669598B1 (en) | 2019-05-22 |
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