CN100419344C - Air conditioner - Google Patents
Air conditioner Download PDFInfo
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- CN100419344C CN100419344C CNB200480001832XA CN200480001832A CN100419344C CN 100419344 C CN100419344 C CN 100419344C CN B200480001832X A CNB200480001832X A CN B200480001832XA CN 200480001832 A CN200480001832 A CN 200480001832A CN 100419344 C CN100419344 C CN 100419344C
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- 239000003507 refrigerant Substances 0.000 claims abstract description 203
- 239000007788 liquid Substances 0.000 claims abstract description 43
- 238000007906 compression Methods 0.000 claims abstract description 9
- 238000004781 supercooling Methods 0.000 claims description 23
- 239000012530 fluid Substances 0.000 claims description 22
- 238000004088 simulation Methods 0.000 claims description 11
- 230000006835 compression Effects 0.000 claims description 7
- 238000003860 storage Methods 0.000 claims description 5
- 239000003795 chemical substances by application Substances 0.000 claims description 4
- 238000005057 refrigeration Methods 0.000 claims description 4
- 239000000203 mixture Substances 0.000 abstract description 5
- 229920006395 saturated elastomer Polymers 0.000 abstract 1
- 238000010438 heat treatment Methods 0.000 description 12
- 239000000463 material Substances 0.000 description 10
- 238000000034 method Methods 0.000 description 9
- 238000004378 air conditioning Methods 0.000 description 7
- 230000015572 biosynthetic process Effects 0.000 description 7
- 230000007423 decrease Effects 0.000 description 6
- 239000012071 phase Substances 0.000 description 5
- 238000001704 evaporation Methods 0.000 description 4
- 230000008020 evaporation Effects 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 230000033228 biological regulation Effects 0.000 description 2
- 238000009835 boiling Methods 0.000 description 2
- 239000002826 coolant Substances 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 239000013028 medium composition Substances 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 229910000975 Carbon steel Inorganic materials 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 239000010962 carbon steel Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
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Classifications
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line 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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
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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
- F25B2313/027—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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0313—Pressure sensors near the outdoor heat exchanger
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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
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor heat exchanger
-
- 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
- F25B2313/031—Sensor arrangements
- F25B2313/0315—Temperature sensors near the outdoor heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/21—Reduction of parts
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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
- F25B2600/2513—Expansion valves
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
An air conditioner (1) is equipped with a plurality of use units (5), a vapor-compression refrigerant loop (10) and a liquid accumulator (25). The vapor-compression refrigerant loop (10) comprises the following components, a high-pressure part (10a) comprising components flowing through the high-pressure refrigerant with the maximum allowable pressure of 3.3MPa or higher, and a low-pressure part (10b) comprising components flowing through the low-pressure refrigerant of lower than the maximum allowable pressure of 3.3 MPa. The liquid accumulator (25) is one of components of the low-pressure part, and can store the refrigerant circulating in the refrigerant loop as liquid refrigerant. The refrigerant flowing in the low-pressure part and the high-pressure part is the simulated azeotropic mixture refrigerant, the azeotropic mixture refrigerant or the single refrigerant with the saturated pressure characteristic higher than that of R407C. Even if the highest use pressure in the refrigerant loop increases in the air conditioner with a plurality of use units, using of the invention can avoid the cost increase of the components of the refrigerant loop.
Description
Technical field
The present invention relates to a kind of aircondition, relate in particular to a kind of a plurality of airconditions that utilize the unit that have.
Background technology
At the aircondition of the air conditioning that is used for skyscraper,, a kind of HFC series coolant, be that R407 replaces R22 just gradually agent is used as running refrigerating from the viewpoint of protection environment.
The aircondition of this air conditioning that is used for skyscraper is owing to have a plurality of unit that utilize, the operating load change is very big, be accompanied by the change of operating load, the increase and decrease of residual refrigerant takes place in the also change of circulating mass of refrigerant in the refrigerant loop in refrigerant loop.This residual refrigerant is stored in the reservoir that is connected with the compressor suction side as liquid refrigerant.
Yet, if residual refrigerant is stored in the storage, because R407 is a mixed non-azeotropic refrigerant, evaporation process in the freeze cycle process, promptly utilize in the evaporation process (during heating operation) of the cold-producing medium in the heat source side heat exchanger of the evaporation process of utilizing cold-producing medium in the side heat exchanger (during refrigerating operaton) of unit or heat source unit, can make cold-producing medium take place to form changes, during gas phase in reservoir, the R32 of low boiling point component becomes the high concentration state, during liquid phase in reservoir, the R134a of higher boiling composition becomes the high concentration state.Therefore the high cold-producing medium of R32 concentration is inhaled into compressor and circulates in refrigerant loop, may make aircondition integral body can't obtain the original performance of R407C.
At this problem, aircondition in the past is to utilize bypass pipe to connect reservoir and the refrigerant piping that flows for high pressure liquid refrigerant, change with the composition that suppresses cold-producing medium, or the composition of detection cold-producing medium, to carry out only operation control (with reference to patent documentation 1,2,3,4 to forming to change.)。In addition, also having a kind of aircondition is that residual refrigerant is stored in the reservoir that is connected with the refrigerant piping that flows for high pressure liquid refrigerant, to suppress the following cold-producing medium of evaporation process to form variation (for example with reference to patent documentation 5).
Patent documentation 1: the spy opens flat 8-35725 communique
Patent documentation 2: the spy opens flat 10-220880 communique
Patent documentation 3: the spy opens flat 10-332211 communique
Patent documentation 4: the spy opens flat 11-173698 communique
Patent documentation 5: the spy opens the 2001-183020 communique
Preceding a kind of aircondition of above-mentioned use R407C is when utilizing bypass pipe to connect reservoir with the refrigerant piping that flows for high pressure liquid refrigerant, and the formation of refrigerant loop and operation control can be complicated.
On the other hand, back a kind of aircondition of above-mentioned use R407C is when using the mobile refrigerant piping of receiver replacement reservoir and voltage supply liquid refrigerant to be connected, with preceding a kind of comparing, the formation of refrigerant loop and operation control are uncomplicated, and this is its advantage.
Yet, nearest field at the aircondition that is used for the skyscraper air conditioning, for the raising and the machine miniaturization of heat pump performance, also develop and produce the product of a kind of cold-producing medium that uses saturation pressure to be higher than R407C (for example R410A or HC series coolant).Yet, when using saturation pressure to be higher than the cold-producing medium of R407C, compare during with use R407C, because the working pressure maximum of the cold-producing medium that flows in refrigerant loop (is higher than the about 1MPa of standard working pressure mostly, hereinafter referred to as maximum working (operation) pressure (MWP)) raise, therefore must increase the compressive resistance of the parts that constitute refrigerant loop.Especially, compare with more small-sized airconditions such as domestic air conditionings, the part dimension that constitutes refrigerant loop in the employed aircondition of skyscraper is bigger, therefore the maximum working (operation) pressure (MWP) for the mobile refrigerant circuit part of high-pressure refrigerant (hereinafter referred to as high-voltage section) also raises, therefore have to increase the compressive resistance of the parts that constitute refrigerant loop, the tendency that increases cost is arranged.Therefore, have in the aircondition of above-mentioned the sort of reservoir as one of high-voltage section component parts, for the compressive resistance that makes reservoir increases, must increase wall thickness, thereby cost is increased.
Summary of the invention
The objective of the invention is to: even raise because of the cold-producing medium that uses saturation pressure to be higher than R407C causes the maximum working (operation) pressure (MWP) of refrigerant loop in having a plurality of airconditions that utilize the unit, the cost that also can suppress to constitute the parts of refrigerant loop increases.
The aircondition of technical scheme 1 has a plurality of unit that utilize, and has steam compression type cryogen circuit and reservoir.Steam compression type refrigeration agent loop comprises: being connected with and can allowing maximum working (operation) pressure (MWP) is that the high-voltage section that constitutes of parts that 3.3Mpa or bigger high-pressure refrigerant flow through and being connected with only allows to be lower than the low voltage section that parts that the low pressure refrigerant of maximum working (operation) pressure (MWP) 3.3MPa flows through constitute.Reservoir is one of parts that constitute described low voltage section, the cold-producing medium that circulates in described refrigerant loop can be stored as liquid refrigerant.Be simulation azeotropic refrigerant, azeotropic refrigerant or unitary system cryogen in low voltage section and the mobile cold-producing medium of high-voltage section.
Under the situation of using R407C as aircondition running cold-producing medium, the standard working pressure of high-voltage section is about 2.0MPa.Therefore, in the aircondition that uses R407C as the running cold-producing medium, the maximum working (operation) pressure (MWP) of high-voltage section mostly is the 3.0～3.3MPa that exceeds about the about 1MPa of standard working pressure 2.0MPa greatly.Therefore, use in the aircondition of R407C as the running cold-producing medium, the parts that constitute high-voltage section only need have the compressive resistance that can bear 3.3MPa.
On the other hand, if use saturation pressure to be higher than the cold-producing medium of R407C,, so have and bear the compressive resistance of 3.3MPa with upward pressure with regard to the parts that require to constitute high-voltage section because the maximum working (operation) pressure (MWP) of high-voltage section can surpass 3.3MPa.Especially container and pipe arrangement, be not to process after producing material, process and normally from specification product such as JIS, select material with the wall thickness that satisfies the maximum working (operation) pressure (MWP) condition with the optimum wall thickness of calculating according to the high-voltage section maximum working (operation) pressure (MWP).Therefore, the cold-producing medium that uses saturation pressure to be higher than R407C can significantly increase wall thickness, the cost that constitutes refrigerant loop is increased surpass necessary scope.
Aircondition of the present invention is in order to prevent the as above increase of unnecessary cost, adopt simulation azeotropic refrigerant, azeotropic refrigerant or unitary system cryogen to be higher than the cold-producing medium of R407C as saturation pressure, while can be stored the reservoir of following a plurality of residual refrigerant of utilizing the change of unit operating load and increasing and decreasing in the low voltage section setting that maximum working (operation) pressure (MWP) is lower than 3.3MPa, therefore high-voltage section need not to be provided with receiver, and is provided with need not when using mixed non-azeotropic refrigerant and prevents that cold-producing medium from forming the parts such as bypass pipe that change.
So, even raise because of the cold-producing medium that uses saturation pressure to be higher than R407C causes the maximum working (operation) pressure (MWP) of refrigerant loop, the cost that also can prevent to constitute the parts of refrigerant loop increases.
Technical scheme 2 is in the aircondition of technical scheme 1, comprises R32 in low voltage section and the mobile cold-producing medium of high-voltage section.
The aircondition of technical scheme 4 has: with the low-pressure refrigerant gas compression, to discharge the compressor of high-pressure gas refrigerant; Can be used as the heat source side heat exchanger of evaporimeter and condensed device work; Connect, can be used as a plurality of side heat exchangers that utilize of condensed device and evaporator operation mutually side by side; Be connected in the described expansion mechanism that utilizes between side heat exchanger and the described heat source side heat exchanger; The switching mechanism that can between following state, switch: promptly, the gas side of described heat source side heat exchanger is connected with the discharge side of described compressor and with the suction side of described compressor with describedly utilize the gas side of side heat exchanger to be connected, low-pressure refrigerant gas being sucked the state of compressor, and the gas side of described heat source side heat exchanger is connected with the suction side of described compressor and the discharge side of described compressor is connected so that high-pressure gas refrigerant flows into the described state that utilizes the side heat exchanger with the described gas side of side heat exchanger that utilizes; Be connected between the suction side of described switching mechanism and described compressor, the reservoir that the cold-producing medium of low pressure can be stored as liquid refrigerant, comprise described reservoir, and flow through with the low pressure refrigerant that the low voltage section that constitutes after the suction side of described compressor is connected only allows to be lower than maximum working (operation) pressure (MWP) 3.3MPa by described switching mechanism, as the part beyond the described low voltage section, by described compressor, described heat source side heat exchanger, described a plurality of high-voltage section of utilizing side heat exchanger and described switching mechanism to connect the back formation can flow through maximum working (operation) pressure (MWP) and be 3.3Mpa or bigger high-pressure refrigerant, and the cold-producing medium that is flowing in described low voltage section and described high-voltage section is the simulation azeotropic refrigerant with the saturation pressure characteristic that is higher than R407C, azeotropic refrigerant or unitary system cryogen.
Under the situation of using R407C as aircondition running cold-producing medium, the standard working pressure of high-voltage section is about 2.0MPa.Therefore, use in the aircondition of R407C as the running cold-producing medium, the maximum working (operation) pressure (MWP) of high-voltage section mostly is the 3.0～3.3MPa that exceeds about the about 1MPa of standard working pressure 2.0MPa greatly.Therefore, use in the aircondition of R407C as the running cold-producing medium, the parts that constitute high-voltage section only need have the compressive resistance that can bear 3.3MPa.
On the other hand, if use saturation pressure to be higher than the cold-producing medium of R407C,, so have and bear the compressive resistance of 3.3MPa with upward pressure with regard to the parts that require to constitute high-voltage section because the maximum working (operation) pressure (MWP) of high-voltage section can surpass 3.3MPa.Especially container and pipe arrangement, be not to process after producing material, process and normally from specification product such as JIS, select material with the wall thickness that satisfies the maximum working (operation) pressure (MWP) condition with the optimum wall thickness of calculating according to the high-voltage section maximum working (operation) pressure (MWP).Therefore, the cold-producing medium that uses saturation pressure to be higher than R407C can significantly increase wall thickness, the cost that constitutes refrigerant loop is increased surpass necessary scope.
Aircondition of the present invention is in order to prevent the as above increase of unnecessary cost, adopt simulation azeotropic refrigerant, azeotropic refrigerant or unitary system cryogen to be higher than the cold-producing medium of R407C as saturation pressure, while can be stored the reservoir of following a plurality of residual refrigerant of utilizing the change of unit operating load and increasing and decreasing in the low voltage section setting that maximum working (operation) pressure (MWP) is lower than 3.3MPa, therefore high-voltage section need not to be provided with receiver, and is provided with need not when using mixed non-azeotropic refrigerant and prevents that cold-producing medium from forming the parts such as bypass pipe that change.
So, even raise because of the cold-producing medium that uses saturation pressure to be higher than R407C causes the maximum working (operation) pressure (MWP) of refrigerant loop, the cost that also can prevent to constitute the parts of refrigerant loop increases.
When this aircondition is worked the heat source side heat exchanger as refrigerating operaton the time as condensed device, by making condensing cold-producing medium become the supercooling state of regulation, can follow operating load to change and the residual refrigerant of increase and decrease is stored in the reservoir reliably.In addition,, become the supercooling state of regulation, can follow operating load to change and the residual refrigerant of increase and decrease is stored in the reservoir reliably by making condensing cold-producing medium even will utilize the side heat exchanger to work as heating operation the time time as condensed device.
Technical scheme 6 is in arbitrary aircondition in technical scheme 4～5, and the cold-producing medium that flows in low voltage section and high-voltage section comprises R32.
Therefore this aircondition can improve the air-conditioning ability because use comprises the high R32 cold-producing medium of hot conveyance ability.
Technical scheme 7 is the arbitrary airconditions in technical scheme 4～5, is R410A in low voltage section and the mobile cold-producing medium of high-voltage section.
This aircondition can be than the further raising air-conditioning of R407C ability owing to using R410A.
Description of drawings
Fig. 1 is the summary refrigerant loop figure of the aircondition of the embodiment of the invention 1.
Fig. 2 be explanation aircondition freeze cycle not in sad line chart.
Fig. 3 is to use the graph of a relation of pressure and wall thickness.
The specific embodiment
(1) integral body of aircondition constitutes
Fig. 1 is the summary refrigerant loop figure of the aircondition of the embodiment of the invention 1.Aircondition 1 is the cold device that heats that can be used for skyscraper etc., and this aircondition has: heat source unit 2, utilize unit 5 with its many of being connected side by side (in the present embodiment being 2), connect heat source unit 2 and the liquid refrigerant pipe arrangement 6 and the gas refrigerant pipe arrangement 7 that utilize unit 5 usefulness.
Aircondition 1 uses saturation pressure to be higher than the simulation azeotropic refrigerant R410A (R32:50wt%, R125:50wt%) of R407C as the running cold-producing medium in present embodiment is relevant.Among the R410A, the content of the R32 that hot transporting capacity is higher is higher than R407C, therefore can improve the air-conditioning ability of aircondition 1.
(2) utilize the formation of unit
Utilize unit 5 mainly to be constituted by the pipe arrangement that utilizes side expansion valve 51, utilizes side heat exchanger 52 and connect them.
Utilizing side expansion valve 51 in the present embodiment, is the electric expansion valve that is used to regulate refrigerant pressure and refrigerant flow etc., and it is connected with the hydraulic fluid side that utilizes side heat exchanger 52.
Utilize side heat exchanger 52 in the present embodiment, when refrigerating operaton, room air is cooled off, when heating operation, room air is heated as the cold-producing medium condensed device as refrigerant evaporator.In addition, utilize side heat exchanger 52 to be provided with to be used to detect refrigerant temperature utilize side Temperature Detector 53.In the present embodiment, utilizing side Temperature Detector 53 is to be configured in the thermistor that utilizes side heat exchanger 52 hydraulic fluid sides.
(3) formation of heat source unit
Heat source unit 2 mainly by compressor 21, No. four transfer valves 22, heat source side heat exchanger 23, heat source side expansion valve 24, reservoir 25, hydraulic fluid side isolating valve 26, gas side isolating valve 27 and connect they pipe arrangement constitute.
No. four transfer valves 22 are used in the flow direction of making to switch when refrigerating operaton and heating operation switch cold-producing medium, when refrigerating operaton, the discharge side of compressor 21 is connected with the gas side of heat source side heat exchanger 23, suction side (being exactly reservoir 25 particularly) with compressor 21 is connected (with reference to the solid line of No. four transfer valves 22 among Fig. 1) with gas refrigerant connecting pipings 7 sides simultaneously, when carrying out heating operation, No. four transfer valves 22 are connected the discharge side of compressor 21 with gas refrigerant connecting pipings 7 sides, the suction side with compressor 21 is connected (with reference to the dotted line of No. four transfer valves 22 among Fig. 1) with the gas side of heat source side heat exchanger 23 simultaneously.
Heat source side heat exchanger 23 in the present embodiment, during refrigerating operaton as with outdoor air or water condensed device as the cold-producing medium of thermal source, during heating operation then as with outdoor air or water evaporimeter as the cold-producing medium of thermal source.In addition, on heat source side heat exchanger 23, be provided with the heat source side Temperature Detector 29 that is used to detect refrigerant temperature.In the present embodiment, heat source side Temperature Detector 29 is the thermistors that are configured in the hydraulic fluid side of heat source side heat exchanger 23.
Heat source side expansion valve 24 is connected with the hydraulic fluid side of heat source side heat exchanger 23, in the present embodiment, is the electric expansion valve that is used to regulate heat source side heat exchanger 23 and utilizes the refrigerant flow between the side heat exchanger 52.
Reservoir 25 is connected between No. four transfer valves 22 and the compressor 21, is to be used to store the low pressure refrigerant that is inhaled into compressor 21 and the container of residual refrigerant.
Hydraulic fluid side isolating valve 26 and gas side isolating valve 27 are connected with liquid refrigerant connecting pipings 6 and gas refrigerant connecting pipings 7 respectively.Be connected between the hydraulic fluid side that utilizes side heat exchanger 52 that liquid refrigerant connecting pipings 6 will utilize unit 5 and the hydraulic fluid side of the heat source side heat exchanger 23 of heat source unit 2.Be connected between the gas side that utilizes side heat exchanger 52 that gas refrigerant connecting pipings 7 will utilize unit 5 and No. four transfer valves 22 of heat source unit 2.
The refrigerant loop that above-mentionedly utilize side expansion valve 51, utilize side heat exchanger 52, compressor 21, No. four transfer valves 22, heat source side heat exchanger 23, heat source side expansion valve 24, reservoir 25, hydraulic fluid side isolating valve 26 and gas side isolating valve 27 is connected in sequence is as the refrigerant loop 10 of aircondition 1.
(3) running of aircondition
Below utilize Fig. 1 and Fig. 2 that the running operation of aircondition 1 under normal service conditions is described.Wherein Fig. 2 be explanation aircondition freeze cycle not in sad line chart.
During＜refrigerating operaton 〉
During refrigerating operaton, the state of No. four transfer valves 22 is shown in the solid line among Fig. 1, that is, the discharge side of compressor 21 is connected with the gas side of heat source side heat exchanger 23, and the suction side of compressor 21 is connected with the gas side that utilizes side heat exchanger 52.In addition, hydraulic fluid side isolating valve 26, gas side isolating valve 27 are opened, and utilize side expansion valve 51 to be in full-gear.Heat source side expansion valve 24 is in the supercooling control that can utilize 29 of high-pressure detector 28 and heat source side Temperature Detectors and carries out the state that aperture is regulated.Say more more specifically, according to the temperature difference between high-pressure detector 28 pairing saturation temperatures of detected high-pressure gas refrigerant force value and the heat source side heat exchanger 29 detected high pressure liquid refrigerant temperature values, calculate the supercooling degree of high pressure liquid refrigerant, and the aperture of regulating heat source side expansion valve 24, so that the supercooling degree becomes setting.
Under the such state of refrigerant loop 10, if starting compressor 21, low-pressure refrigerant gas (about 15 ℃ of the about 0.9MPa of pressure P s=, temperature T s=) just are inhaled into and are collapsed into high-pressure gas refrigerant (about 70 ℃ of the about 3.0MPa of pressure P d=, temperature T d=) (with reference to some A among Fig. 2 and some B) in the compressor 21.After this, high-pressure gas refrigerant is admitted to heat source side heat exchanger 23 via No. four transfer valves 22, carry out heat exchange with outdoor air that becomes thermal source or water and, make the lower slightly temperature T c (about 45 ℃) (with reference to the some C among Fig. 2) of saturation temperature Tsat (about 50 ℃ of temperature) under its cooling raio pressure P d by condensing.At this, the supercooling degree Δ Tc (being Tsat-Tc) of the high pressure liquid refrigerant under the some C state utilizes the supercooling of heat source side expansion valve 24 to control remain unchanged (at this, about 5 ℃ of Δ Tc=).
And, the aperture of the corresponding heat source side expansion valve 24 of liquid refrigerant after this is condensing and be depressurized into the gas-liquid two-phase system cryogen (about 3 ℃ of the about 0.9MPa of pressure P s=, temperature T D=) (with reference to the some D among Fig. 2) of low pressure, and be sent to via hydraulic fluid side isolating valve 26 and liquid refrigerant connecting pipings 6 and utilize unit 5.
Be sent to utilize unit 5 gas-liquid two-phase system cryogen via after utilizing side expansion valve 51, in utilizing side heat exchanger 52, carry out heat exchange and be evaporated, become low-pressure refrigerant gas (about 15 ℃ of the about 0.9MPa of pressure P s=, temperature T s=) (with reference to the some A among Fig. 2) once more with room air.This low-pressure refrigerant gas flows into reservoir 25 via gas refrigerant connecting pipings 7, gas side isolating valve 27 and No. four transfer valves 22.The low-pressure refrigerant gas that flows into reservoir 25 is inhaled into compressor 21 once more.
As mentioned above, utilize the supercooling control of heat source side expansion valve 24 that the supercooling degree Δ Tc of the high pressure liquid refrigerant under the C state is remained unchanged, even therefore utilize the operating load change of unit 5, circulating mass of refrigerant to change, also can guarantee the state variation that freeze cycle shown in Figure 2 is such, and residual refrigerant is stored in the reservoir 25.
In addition, when low pressure liquid refrigerant flows into reservoir 25 with low-pressure refrigerant gas from utilizing side heat exchanger 52, or residual refrigerant is when being stored in the reservoir 25, in the gas-liquid separation that reservoir 25 carries out between low-pressure refrigerant gas and low pressure liquid refrigerant, have only low-pressure refrigerant gas to be inhaled into compressor 21.At this moment, present embodiment is owing to use the R410A that simulates one of azeotropic refrigerant as the running cold-producing medium, so can the cold-producing medium composition of the low-pressure refrigerant gas that is inhaled into compressor 21 and the cold-producing medium composition that is stored in the liquid refrigerant in the reservoir 25 be remained unchanged by the gas-liquid separation in the reservoir 25.
During＜heating operation 〉
During heating operation, the state of No. four transfer valves 22 is shown in the dotted line among Fig. 1, and promptly the discharge side of compressor 21 is connected with the gas side that utilizes side heat exchanger 52, and the suction side of compressor 21 is connected with the gas side of heat source side heat exchanger 23.In addition, hydraulic fluid side isolating valve 26, gas side isolating valve 27 are opened, and heat source side expansion valve 24 is in full-gear.Utilize side expansion valve 51 to be in and to utilize high-pressure detector 28 and the supercooling control that utilizes side Temperature Detector 53 to carry out the state that aperture is regulated.Say more more specifically, according to the high-pressure detector 28 pairing saturation temperatures of detected high-pressure gas refrigerant force value and utilize temperature difference between the side heat exchanger 53 detected high pressure liquid refrigerant temperature values, calculate the supercooling degree of high pressure liquid refrigerant, and regulate the aperture of utilizing side expansion valve 51, so that the supercooling degree becomes setting.
Under the such state of refrigerant loop 10, if starting compressor 21, low-pressure refrigerant gas just is inhaled in the compressor 21 and is collapsed into high-pressure gas refrigerant, is admitted to via No. four transfer valves 22, gas side isolating valve 27 and gas refrigerant connecting pipings 7 then and utilizes unit 5.And, be admitted to the high-pressure gas refrigerant that utilizes unit 5 and in utilizing side heat exchanger 52, carry out heat exchange and, be cooled to the temperature more lower slightly than the saturation temperature of high-pressure gas refrigerant by condensing with room air.At this, the supercooling degree of the high pressure liquid refrigerant under the some C state is owing to the supercooling control that utilizes side expansion valve 51 remains unchanged.Liquid refrigerant correspondence after condensing utilizes the aperture of side expansion valve 51 to be depressurized becomes the gas-liquid of low pressure two-phase system cryogen, is sent to heat source unit 2 via liquid refrigerant connecting pipings 6 and hydraulic fluid side isolating valve 26.The gas-liquid two-phase system cryogen that is sent to heat source unit 2 via heat source side expansion valve 24 after, in heat source side heat exchanger 23 with become the outdoor air of thermal source or water and carry out heat exchange and be evaporated, become low-pressure refrigerant gas once more, and flow into reservoir 25 via No. four transfer valves 22.And the low-pressure refrigerant gas that flows into reservoir 25 is inhaled into compressor 21 once more.
As mentioned above, when heating operation, the flow direction of cold-producing medium is opposite during with refrigerating operaton, and by utilizing side expansion valve 51 to carry out supercooling control, except these 2 differences, the state variation of cold-producing medium is identical with the state variation of freeze cycle shown in Figure 2.
(4) design pressure of the parts of formation refrigerant loop
During from above-mentioned aircondition 1 refrigerating operaton and the operation explanation during heating operation as can be known, refrigerant loop 10 by the refrigerant loop part that flows for high-pressure refrigerant, be high-voltage section 10a and have only refrigerant loop part that low pressure refrigerant flows through, be that low voltage section 10b constitutes.Particularly, low voltage section 10b is the part that No. four transfer valves 22 that will comprise reservoir 25 are connected with compressor 21 suction sides, and high-voltage section 10a is the part of removing in the refrigerant loop 10 beyond the low voltage section 10b.
At this, to constituting parts (be exactly compressor 21, No. four transfer valves 22, heat source side heat exchanger 23, heat source side expansion valve 24, hydraulic fluid side isolating valve 26, gas side isolating valve 27 particularly, utilize side expansion valve 51 and utilize side heat exchanger 52) and the pipe arrangement of high-voltage section 10a, at the standard working pressure (about 3.0MPa) of above-mentioned high-pressure refrigerant and leave the leeway of about 1MPa, so that make the high-pressure refrigerant of maximum working (operation) pressure (MWP) (about 4MPa) can flow through above-mentioned parts and pipe arrangement.In addition, to constituting parts (being exactly reservoir 25 particularly) and the pipe arrangement of low voltage section 10b, at the standard working pressure (about 0.9MPa) of above-mentioned low pressure refrigerant and leave the leeway of about 1MPa, so that the low pressure refrigerant of maximum working (operation) pressure (MWP) (about 2MPa) can flow through above-mentioned parts and pipe arrangement.
(5) feature of aircondition
The aircondition 1 of present embodiment has following feature.
(A) aircondition 1 of present embodiment is owing to use saturation pressure to be higher than the R410A of R407C as cold-producing medium, simultaneously the low voltage section 10b that is lower than 3.3MPa at maximum working (operation) pressure (MWP) is provided with and can stores the change of following a plurality of operating loads that utilize unit 5 and the reservoir 25 of the residual refrigerant that increases and decreases, so high-voltage section 10a need not to be provided with receiver.
Therefore, even aircondition 1 raises because of the cold-producing medium that uses saturation pressure to be higher than R407C causes the maximum working (operation) pressure (MWP) of refrigerant loop, also can suppress to constitute the cost increase of refrigerant loop parts.
About suppressing the effect that cost increases, below situation when using R410A to cause the maximum working (operation) pressure (MWP) of refrigerant loop to raise as cold-producing medium, at low voltage section 10b the situation of reservoir 25 being set and doing relatively present embodiment with the situation that at high-voltage section 10a receiver (not having diagram) is set in the past.
For example, use JIS specification product STPG370E (pressure pipe arrangement carbon steel steel pipe) to be material, when cylindric reservoir 25 that the processing and manufacturing nominal diameter is 10 inches and receiver, consider to select specification (schedule) 20 (wall thickness 6.4mm) or specification 30 (wall thickness 7.8mm).And, shown in the working pressure and wall thickness graph of a relation of Fig. 3, the highest use of material of specification 30 to 4.3MPa.
At this, because the maximum working (operation) pressure (MWP) of reservoir 25 is about 2.0MPa (maximum working (operation) pressure (MWP) of low voltage section 10b), therefore promptly use the material of specification 20, also have enough compressive resistances, can select for use.On the other hand, because the maximum working (operation) pressure (MWP) of receiver is about 4.0MPa (maximum working (operation) pressure (MWP) of high-voltage section 10a), therefore can not use the material of specification 20, and, from calculating,, must select the material of specification 30 though the wall thickness of about 7.4mm is enough.
When using R407C like this as aircondition running cold-producing medium, because the maximum working (operation) pressure (MWP) of high-voltage section is between 3.0～3.3MPa, therefore can use the material of specification 20, yet when saturation pressures such as using R410A as present embodiment is higher than the cold-producing medium of R407C, if use the container of receiver as the storage residual refrigerant, wall thickness can be significantly increased, the unnecessary cost of the parts that constitute refrigerant loop can be increased.In other words, as mentioned above, when saturation pressures such as using R410A is higher than the cold-producing medium of R407C, adopt reservoir to replace receiver can prevent that as the container of storage residual refrigerant cost from increasing.
(B) in addition, because R410A is the simulation azeotropic refrigerant, even so adopt the container of reservoir 25 as the storage residual refrigerant, be provided with also need not be when using mixed non-azeotropic refrigerant such as R407C and prevent that cold-producing medium from forming the parts such as bypass pipe that change, thereby can prevent to constitute the increase of refrigerant loop component costs.
(C) aircondition 1 is when refrigerating operaton, can be according to the temperature difference between the temperature value of the force value of high-pressure detector 28 detected high-pressure gas refrigerants and heat source side heat exchanger 29 detected high pressure liquid refrigerants, calculate the supercooling degree of high pressure liquid refrigerant, and the aperture of regulating heat source side expansion valve 24, therefore so that the supercooling degree becomes setting, can follow operating load to change and the residual refrigerant of increase and decrease is stored in the reservoir 25 reliably.In addition, when heating operation, can and utilize temperature difference between the temperature value of side heat exchanger 53 detected high pressure liquid refrigerants according to the force value of high-pressure detector 28 detected high-pressure gas refrigerants, calculate the supercooling degree of high pressure liquid refrigerant, and adjusting utilizes the aperture of side expansion valve 51, therefore so that the supercooling degree becomes setting, can follow operating load to change and the residual refrigerant of increase and decrease is stored in the reservoir 25 reliably.
(6) other embodiment
The embodiment of the invention below has been described with reference to the accompanying drawings, yet concrete formation is not limited to the foregoing description, can change in the scope that does not depart from inventive concept.
(A) aircondition in the previous embodiment has and can freeze and the refrigerant loop of heating operation, yet is not limited to this, has the refrigeration of not establishing No. four transfer valves aircondition special-purpose or that heat special-purpose refrigerant loop and is applicable to the present invention too.
(B) in the aforementioned embodiment, the R410A that adopts one of simulation azeotropic refrigerant is as the running cold-producing medium, yet be not limited to this, also can adopt R410B R32:R125 ratio of components such as (R32:45wt%, R125:55wt%) to be different from unitary system cryogens such as the simulation azeotropic refrigerant of R410A or R32, other simulation azeotropic refrigerant or azeotropic refrigerants.
The possibility of utilizing on the industry
If use the present invention is in having the aircondition of a plurality of range sites, even because using saturation pressure Be higher than the cold-producing medium of R407C and cause the maximum working (operation) pressure (MWP) of refrigerant loop to raise, also can prevent from consisting of system The increase of refrigerant circuit component costs.
Claims (7)
1. an aircondition (1) has a plurality of unit (5) that utilize,
It is characterized in that having steam compression type refrigeration agent loop (10) and reservoir (25),
Steam compression type refrigeration agent loop (10) comprises: being connected with and can allowing maximum working (operation) pressure (MWP) is that the high-voltage section (10a) that constitutes of parts that 3.3Mpa or bigger high-pressure refrigerant flow through and being connected with only allows to be lower than the low voltage section (10b) that parts that the low pressure refrigerant of maximum working (operation) pressure (MWP) 3.3MPa flows through constitute
Reservoir (25) is one of parts that constitute described low voltage section, the cold-producing medium that circulates in described refrigerant loop can be stored as liquid refrigerant,
In described low voltage section and the mobile cold-producing medium of described high-voltage section is simulation azeotropic refrigerant, azeotropic refrigerant or the unitary system cryogen with the saturation pressure characteristic that is higher than R407C.
2. aircondition as claimed in claim 1 (1) is characterized in that, comprises R32 in described low voltage section (10b) and the mobile cold-producing medium of described high-voltage section (10a).
3. aircondition (1) according to claim 1 is characterized in that, is R410A in described low voltage section (10b) and the mobile cold-producing medium of described high-voltage section (10a).
4. an aircondition (1) has:
With the low-pressure refrigerant gas compression, to discharge the compressor (21) of high-pressure gas refrigerant;
Can be used as the heat source side heat exchanger (23) of evaporimeter and condensed device work;
Connect, can be used as a plurality of side heat exchangers (52) that utilize of condensed device and evaporator operation mutually side by side;
Be connected in the described expansion mechanism (24,51) that utilizes between side heat exchanger and the described heat source side heat exchanger;
The switching mechanism (22) that can between following state, switch: promptly, the gas side of described heat source side heat exchanger is connected with the discharge side of described compressor, and the suction side of described compressor is connected with the described gas side of side heat exchanger that utilizes, low-pressure refrigerant gas being sucked the state of compressor, and the gas side of described heat source side heat exchanger is connected with the suction side of described compressor, and the discharge side of described compressor is connected with the described gas side of side heat exchanger that utilizes, so that high-pressure gas refrigerant flows into the described state that utilizes the side heat exchanger;
Be connected between the suction side of described switching mechanism and described compressor, can be with the cold-producing medium of low pressure reservoir (25) as the liquid refrigerant storage,
Comprise described reservoir and flow through with the low pressure refrigerant that the low voltage section (10b) that constitutes after the suction side of described compressor is connected only allows to be lower than maximum working (operation) pressure (MWP) 3.3MPa by described switching mechanism,
As the part beyond the described low voltage section, can flow through maximum working (operation) pressure (MWP) by described compressor, described heat source side heat exchanger, described a plurality of high-voltage section (10a) that constitute after utilizing side heat exchanger and described switching mechanism to connect is 3.3Mpa or bigger high-pressure refrigerant
The cold-producing medium that is flowing in described low voltage section and described high-voltage section is simulation azeotropic refrigerant, azeotropic refrigerant or the unitary system cryogen with the saturation pressure characteristic that is higher than R407C.
5. aircondition as claimed in claim 4 (1), it is characterized in that, also have: detect the hydraulic fluid side refrigerant temperature of described heat source side heat exchanger (23) heat source side Temperature Detector (29), detect utilizing side Temperature Detector (53), detecting the high-pressure detector (28) of the discharge side refrigerant pressure of described compressor (21) of the described hydraulic fluid side refrigerant temperature of respectively utilizing side heat exchanger (52)
According to described heat source side Temperature Detector, described side Temperature Detector and detected refrigerant temperature of described high-pressure detector and the refrigerant pressure value utilized, regulate the aperture of described expansion mechanism (24), when described heat source side heat exchanger is worked as condensed device, to make the liquid refrigerant of described heat source side heat exchanger hydraulic fluid side become predetermined supercooling state, and regulate the aperture of described expansion mechanism (51), to make the described liquid refrigerant of side heat exchanger hydraulic fluid side that utilizes become predetermined supercooling state when utilizing the side heat exchanger to work as condensed device described.
6. as claim 4 or 5 described airconditions (1), it is characterized in that, comprise R32 in described low voltage section (10b) and the mobile cold-producing medium of described high-voltage section (10a).
7. as aircondition (1) as described in claim 4 or 5, it is characterized in that, is R410A in described low voltage section (10b) and the mobile cold-producing medium of described high-voltage section (10a).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003161934A JP2004361036A (en) | 2003-06-06 | 2003-06-06 | Air conditioning system |
| JP161934/2003 | 2003-06-06 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1723373A CN1723373A (en) | 2006-01-18 |
| CN100419344C true CN100419344C (en) | 2008-09-17 |
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ID=33508651
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB200480001832XA Expired - Lifetime CN100419344C (en) | 2003-06-06 | 2004-05-31 | Air conditioner |
Country Status (9)
| Country | Link |
|---|---|
| US (1) | US20060000224A1 (en) |
| EP (1) | EP1632732B1 (en) |
| JP (1) | JP2004361036A (en) |
| KR (1) | KR100605797B1 (en) |
| CN (1) | CN100419344C (en) |
| AT (1) | ATE541167T1 (en) |
| AU (1) | AU2004245797B2 (en) |
| ES (1) | ES2380331T3 (en) |
| WO (1) | WO2004109199A1 (en) |
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| JP4187020B2 (en) * | 2006-08-08 | 2008-11-26 | ダイキン工業株式会社 | Air conditioner and cleaning method thereof |
| JP5138292B2 (en) * | 2007-07-04 | 2013-02-06 | 三菱重工業株式会社 | Air conditioner |
| JP5213372B2 (en) * | 2007-07-09 | 2013-06-19 | 三菱電機株式会社 | Air conditioner |
| US20170080773A1 (en) * | 2008-11-03 | 2017-03-23 | Arkema France | Vehicle Heating and/or Air Conditioning Method |
| JP5315990B2 (en) * | 2008-12-29 | 2013-10-16 | ダイキン工業株式会社 | Air conditioning apparatus and control method thereof |
| WO2012042573A1 (en) * | 2010-09-30 | 2012-04-05 | 三菱電機株式会社 | Air conditioning device |
| KR20120136854A (en) * | 2011-06-10 | 2012-12-20 | 삼성전자주식회사 | Water supply apparatus |
| ES2796384T3 (en) | 2011-10-04 | 2020-11-26 | Mitsubishi Electric Corp | Refrigeration cycle device |
| JP6064412B2 (en) * | 2012-07-30 | 2017-01-25 | 株式会社富士通ゼネラル | Air conditioner |
| JP2016102631A (en) * | 2014-11-28 | 2016-06-02 | パナソニックＩｐマネジメント株式会社 | Air conditioning device |
| US11906207B2 (en) | 2017-12-18 | 2024-02-20 | Daikin Industries, Ltd. | Refrigeration apparatus |
| US11365335B2 (en) | 2017-12-18 | 2022-06-21 | Daikin Industries, Ltd. | Composition comprising refrigerant, use thereof, refrigerating machine having same, and method for operating said refrigerating machine |
| US11441802B2 (en) | 2017-12-18 | 2022-09-13 | Daikin Industries, Ltd. | Air conditioning apparatus |
| EP3730569A4 (en) | 2017-12-18 | 2021-12-22 | Daikin Industries, Ltd. | Refrigeration cycle device |
| US11549041B2 (en) | 2017-12-18 | 2023-01-10 | Daikin Industries, Ltd. | Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator |
| US11549695B2 (en) | 2017-12-18 | 2023-01-10 | Daikin Industries, Ltd. | Heat exchange unit |
| WO2019123897A1 (en) * | 2017-12-18 | 2019-06-27 | ダイキン工業株式会社 | Refrigeration cycle device |
| US11493244B2 (en) | 2017-12-18 | 2022-11-08 | Daikin Industries, Ltd. | Air-conditioning unit |
| US11435118B2 (en) | 2017-12-18 | 2022-09-06 | Daikin Industries, Ltd. | Heat source unit and refrigeration cycle apparatus |
| CN111479894B (en) | 2017-12-18 | 2021-09-17 | 大金工业株式会社 | Composition containing refrigerant, use thereof, refrigerator having same, and method for operating refrigerator |
| US11820933B2 (en) | 2017-12-18 | 2023-11-21 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
| US11506425B2 (en) | 2017-12-18 | 2022-11-22 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
| US11441819B2 (en) | 2017-12-18 | 2022-09-13 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
| CN110953779B (en) * | 2019-12-20 | 2021-06-22 | 潍柴动力股份有限公司 | Method and device for controlling pressure of liquid storage tank of Rankine cycle system |
| KR20230168821A (en) | 2022-06-08 | 2023-12-15 | 임종봉 | R410A gas insulated transformer |
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- 2004-05-31 CN CNB200480001832XA patent/CN100419344C/en not_active Expired - Lifetime
- 2004-05-31 KR KR1020057004897A patent/KR100605797B1/en active IP Right Grant
- 2004-05-31 ES ES04745455T patent/ES2380331T3/en not_active Expired - Lifetime
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Also Published As
| Publication number | Publication date |
|---|---|
| AU2004245797A1 (en) | 2004-12-16 |
| US20060000224A1 (en) | 2006-01-05 |
| ATE541167T1 (en) | 2012-01-15 |
| CN1723373A (en) | 2006-01-18 |
| WO2004109199A1 (en) | 2004-12-16 |
| EP1632732B1 (en) | 2012-01-11 |
| EP1632732A4 (en) | 2006-07-26 |
| JP2004361036A (en) | 2004-12-24 |
| KR20050044931A (en) | 2005-05-13 |
| EP1632732A1 (en) | 2006-03-08 |
| KR100605797B1 (en) | 2006-08-01 |
| AU2004245797B2 (en) | 2006-06-29 |
| ES2380331T3 (en) | 2012-05-10 |
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