CN105683681A - Refrigeration cycle device - Google Patents
Refrigeration cycle device Download PDFInfo
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- CN105683681A CN105683681A CN201380080566.3A CN201380080566A CN105683681A CN 105683681 A CN105683681 A CN 105683681A CN 201380080566 A CN201380080566 A CN 201380080566A CN 105683681 A CN105683681 A CN 105683681A
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- Prior art keywords
- refrigeration agent
- communicating pipe
- heat exchanger
- pressure
- reliever
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 210
- 238000001816 cooling Methods 0.000 claims abstract description 50
- 230000008016 vaporization Effects 0.000 claims abstract description 23
- 238000009834 vaporization Methods 0.000 claims abstract description 22
- 239000003795 chemical substances by application Substances 0.000 claims description 200
- 239000007788 liquid Substances 0.000 claims description 31
- 239000003507 refrigerant Substances 0.000 claims description 20
- 230000006837 decompression Effects 0.000 claims description 6
- 239000002826 coolant Substances 0.000 abstract 8
- 239000006200 vaporizer Substances 0.000 description 54
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 22
- 229910052742 iron Inorganic materials 0.000 description 11
- 238000001704 evaporation Methods 0.000 description 6
- 239000007789 gas Substances 0.000 description 6
- 238000001514 detection method Methods 0.000 description 4
- MWUXSHHQAYIFBG-UHFFFAOYSA-N Nitric oxide Chemical compound O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 description 3
- 230000008020 evaporation Effects 0.000 description 3
- 238000005452 bending Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- RBIIKVXVYVANCQ-CUWPLCDZSA-N (2s,4s,5s)-5-amino-n-(3-amino-2,2-dimethyl-3-oxopropyl)-6-[4-(2-chlorophenyl)-2,2-dimethyl-5-oxopiperazin-1-yl]-4-hydroxy-2-propan-2-ylhexanamide Chemical compound C1C(C)(C)N(C[C@H](N)[C@@H](O)C[C@@H](C(C)C)C(=O)NCC(C)(C)C(N)=O)CC(=O)N1C1=CC=CC=C1Cl RBIIKVXVYVANCQ-CUWPLCDZSA-N 0.000 description 1
- OTMSDBZUPAUEDD-UHFFFAOYSA-N Ethane Chemical compound CC OTMSDBZUPAUEDD-UHFFFAOYSA-N 0.000 description 1
- VGGSQFUCUMXWEO-UHFFFAOYSA-N Ethene Chemical compound C=C VGGSQFUCUMXWEO-UHFFFAOYSA-N 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000002401 inhibitory effect Effects 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000004064 recycling Methods 0.000 description 1
- 239000011555 saturated liquid Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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
- F25B40/00—Subcoolers, desuperheaters or superheaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/26—Refrigerant piping
- F24F1/32—Refrigerant piping for connecting the separate outdoor units to indoor units
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
-
- 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
-
- 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
- F25B2400/16—Receivers
Abstract
This refrigeration cycle device has a heat-source unit, a cooling unit, a first connecting tube, and a second connecting tube. The heat-source unit has a compressor for compressing coolant, a high-pressure-side heat exchanger for cooling the coolant from the compressor, and a principal depressurization device for depressurizing the coolant from the condenser. The cooling unit has a low-pressure-side heat exchanger for vaporizing the coolant. The first connecting tube guides the coolant conveyed from the principal depressurization device to the low-pressure-side heat exchanger to the interval between the heat-source unit and the cooling unit. The second connecting tube guides the coolant conveyed from the low-pressure-side heat exchanger to the compressor to the interval between the heat-source unit and the cooling unit. The first connecting tube creates a coolant pressure loss in a range in which the saturation temperature of the coolant in the low-pressure-side heat exchanger does not fall below the use vaporization temperature of the low-pressure-side heat exchanger.
Description
Technical field
The present invention relates to such as freezing, the refrigerating circulatory device of the purposes such as refrigeration.
Background technology
In the past, it is known that by multiple connection join pipe by have compressor and condenser heat source unit and have expansion valve and vaporizer cooling unit connect, and make refrigeration agent by be connected join pipe circulate between heat source unit and cooling unit as refrigerator. In such conventional refrigerator, attempt the CO being used as high-pressure refrigerant2。
Employ in the conventional refrigerator of high-pressure refrigerant such, due to operating pressure height, so, not only it is connected the wall thickness joining pipe and becomes thick, it is connected the cost joining pipe itself to increase, be connected join pipe bending machining, connect processing and also become difficult, the labour arranging operation of pipe is joined in on-the-spot connection and the time becomes big. In addition, when the display stands arranged to the such as shop such as convenience store, supermarket etc. uses described such conventional refrigerator, because the situation that cooling unit is arranged on the place of stow away from heat unit is many, so, such as, the situation being connected the length joining pipe elongated (being connected the total length joining pipe is about 100m) is many. If it is elongated to be connected the length joining pipe, then increase for carrying out being connected the material cost of the construction joining pipe at scene. Due to such situation, increase for setting activity duration, the construction cost of refrigerator.
In the past, in order to seek to be connected the thin-walled property joining pipe, propose following refrigerator, this refrigerator configures the main mechanism of decompressor at heat source unit, the refrigeration agent reduced pressure by the main mechanism of decompressor is joined in pipe in connection flow, such as, the pressure making connection join in pipe reduces (see patent documentation 1).
At first technical literature
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Publication 2003-139422 publication
Summary of the invention
Invent problem to be solved
But, in the conventional refrigerator shown in patent documentation 1, if the pressure-losses being connected the refrigeration agent joining in pipe becomes big, the pressure of the refrigeration agent then reduced pressure by the main mechanism of decompressor can further much slower, therefore, the temperature of saturation of the refrigeration agent in vaporizer is easily lower than the vaporization temperature utilized in vaporizer, it is difficult to guarantee the appropriate running of refrigerator.
The present invention is the invention made for solving described such problem, its objective is to obtain a kind of labour arranging operation and the time that can seek to alleviate scene, and can avoid the refrigerating circulatory device reducing appropriate operating range.
For solving the means of problem
Refrigerating circulatory device based on the present invention possesses heat source unit, cooling unit, 1st communicating pipe and the 2nd communicating pipe, described heat source unit has the compressor of compressed refrigerant, cooling carrys out the high-tension side heat exchanger of the refrigeration agent of compressor, by the main reliever that the refrigeration agent from high-tension side heat exchanger reduces pressure, described cooling unit has the low-tension side heat exchanger that refrigeration agent is evaporated, the refrigeration agent that described 1st communicating pipe, conducting was carried from main reliever to low-tension side heat exchanger between heat source unit and cooling unit, the refrigeration agent that described 2nd communicating pipe, conducting was carried from low-tension side heat exchanger to compressor between heat source unit and cooling unit, 1st communicating pipe was that the scope of vaporization temperature that utilizes that the temperature of saturation of the refrigeration agent in low-tension side heat exchanger is not less than low-tension side heat exchanger produces communicating pipe of the pressure-losses of refrigeration agent.
Invention effect
According to the refrigerating circulatory device based on the present invention, because can be reduced pressure by refrigeration agent by main reliever, the pressure of the refrigeration agent in the 1st communicating pipe is made to become low, so, the thin-walled property of the 1st communicating pipe can be sought, it is possible to alleviate the labour that operation is set and the time of on-the-spot refrigerating circulatory device. In addition, because the temperature of saturation that the pressure-losses of the refrigeration agent in the 1st communicating pipe is suppressed in the refrigeration agent of low-tension side heat exchanger is not less than the scope utilizing vaporization temperature of low-tension side heat exchanger, so, it is possible to avoid the appropriate operating range reducing refrigerating circulatory device.
Accompanying drawing explanation
Fig. 1 is the structure iron representing the refrigerating circulatory device based on embodiments of the present invention 1.
Fig. 2 is the structure iron representing the existing refrigerating circulatory device using R410A refrigeration agent.
Fig. 3 is the pressure-losses of the refrigeration agent in the 1st communicating pipe representing Fig. 1 and the chart of the relation of the internal diameter of the 1st communicating pipe.
Fig. 4 is the pressure-losses of the refrigeration agent in the 1st communicating pipe representing Fig. 1 and the chart of the relation of the length of the 1st communicating pipe.
Fig. 5 is the structure iron representing the refrigerating circulatory device based on embodiments of the present invention 2.
Fig. 6 is the structure iron representing the refrigerating circulatory device based on embodiments of the present invention 3.
Fig. 7 is the structure iron representing the refrigerating circulatory device based on embodiments of the present invention 4.
Fig. 8 is the structure iron representing the refrigerating circulatory device based on embodiments of the present invention 5.
Fig. 9 is the chart of the pressure-losses of refrigeration agent in the 1st communicating pipe representing the design pressure applied in the refrigerating circulatory device using R404A refrigeration agent and the relation of the internal diameter of the 1st communicating pipe.
Figure 10 is the chart of the pressure-losses of refrigeration agent in the 1st communicating pipe representing the design pressure applied in the refrigerating circulatory device using R404A refrigeration agent and the relation of the length of the 1st communicating pipe.
Embodiment
Below, with reference to accompanying drawing, being preferred embodiment described the present invention.
Enforcement mode 1.
Fig. 1 is the structure iron representing the refrigerating circulatory device based on embodiments of the present invention 1. In the drawings, refrigerating circulatory device there is heat source unit 1, the cooling unit 2 that leaves heat source unit 1 and be configured and be connected between heat source unit 1 and cooling unit 2 respectively and the 1st communicating pipe 3 that refrigeration agent is circulated between heat source unit 1 and cooling unit 2 and the 2nd communicating pipe 4. In this embodiment, the CO of high-pressure refrigerant it is used as the refrigeration agent of refrigerating circulatory device2, the on high-tension side pressure of refrigeration cycle is below the emergent pressure of refrigeration agent.
Heat source unit 1 has compressor 11, condenser (high-tension side heat exchanger) 12 and main reliever (expansion valve) 13.At heat source unit 1, be linked in sequence the 2nd communicating pipe 4, compressor 11, condenser 12, main reliever 13 and multiple pipe connectings of the 1st communicating pipe 3 are set. On the other hand, cooling unit 2 has vaporizer (low-tension side heat exchanger) 14. At cooling unit 2, be linked in sequence the 1st communicating pipe 3, vaporizer 14 and multiple pipe connectings of the 2nd communicating pipe 4 are set.
Accordingly, in refrigerating circulatory device, if compressor 11 is driven, then refrigeration agent is transferred according to compressor 11, condenser 12, main reliever 13, the 1st communicating pipe 3, vaporizer 14, the order of the 2nd communicating pipe 4, and returns compressor 11.
The refrigeration agent of compressor 11 pressurized gas shape. The refrigeration agent that have compressed by compressor 11 is carried to condenser 12.
Condenser 12 cools the refrigeration agent of the gas shape of compressor 11, makes it to become liquid refrigeration agent. Such as, condenser 12 is by cooling from the refrigeration agent of gas shape to cooling material (air or water etc.) rejected heat and condensating refrigerant. Refrigeration agent by condenser 12 condensation is carried to main reliever 13.
Main reliever 13 makes the liquid refrigeration agent of condenser 12 expand and reduce pressure. In this embodiment, main reliever 13 is the electric expansion valve of the flow of adjustable refrigeration agent. Main reliever 13 is controlled by not shown control portion.
The refrigeration agent that 1st communicating pipe 3, conducting was carried from main reliever 13 to vaporizer 14 between heat source unit 1 and cooling unit 2.
Vaporizer 14 makes the refrigeration agent from the 1st communicating pipe 3 evaporate. Such as, vaporizer 14 is arranged on the cooling container (cooling display stands etc.) being such as located at the shop such as convenience store, supermarket. Cooling container is cooled by making refrigeration agent evaporation by vaporizer 14.
The refrigeration agent that 2nd communicating pipe 4, conducting was carried from vaporizer 14 to compressor 11 between heat source unit 1 and cooling unit 2. Within the 2nd communicating pipe 4, the refrigeration agent of gas shape is switched on.
It is arranged on the downstream compared with main reliever 13, upstream compared with compressor 11 1st and the 2nd communicating pipe 3,4. Therefore, the low-tension side that the 1st and the 2nd communicating pipe 3,4 was arranged in refrigeration cycle.
Main reliever 13 refrigeration agent is reduced pressure to the 1st and the 2nd communicating pipe 3,4 design pressure below pressure. In this embodiment, the design pressure of the 1st and the 2nd communicating pipe 3,4 is 4.15MPa, and refrigeration agent is reduced pressure below 4.15MPa by main reliever 13.
Such as, in the existing refrigerating circulatory device employing R410A refrigeration agent, as shown in Figure 2, main reliever 13 is not be arranged on heat source unit 1, but it being arranged on cooling unit 2, the refrigeration agent carrying out condenser 12, after the 1st communicating pipe 3, is carried to main reliever 13. That is, in the existing refrigerating circulatory device employing R410A refrigeration agent, the high-tension side that the 1st communicating pipe 3 was arranged in refrigeration cycle. The design pressure of the 1st communicating pipe 3 employing the existing refrigerating circulatory device shown in Fig. 2 of R410A refrigeration agent is 4.15MPa.
Employing high-pressure refrigerant (CO2) the refrigerating circulatory device based on present embodiment in, because main reliever 13 is arranged on heat source unit 1, so, by making refrigeration agent reduce pressure by main reliever 13, can make the pressure of the refrigeration agent in the 1st and the 2nd communicating pipe 3,4 below the design pressure of the 1st communicating pipe 3 of existing refrigerating circulatory device (that is, below 4.15MPa).Accordingly, it may be possible to using the 1st and the 2nd communicating pipe 3,4 of the existing refrigerating circulatory device using R410A refrigeration agent as using high-pressure refrigerant (CO2) the recycling the 1st and the 3rd communicating pipe 3,4 of the refrigerating circulatory device based on present embodiment.
In addition, when from main reliever 13 refrigeration agent out through the 1st communicating pipe 3, the pressure-losses of refrigeration agent is produced. The length of the 1st communicating pipe 3 is more long, and the pressure-losses of the refrigeration agent in the 1st communicating pipe 3 is more big, and the internal diameter of the 1st communicating pipe 3 is more little, and the pressure-losses of the refrigeration agent in the 1st communicating pipe 3 is more big. The pressure-losses of the refrigeration agent in the 1st communicating pipe 3 is big, owing to refrigeration agent passed in the 1st communicating pipe 3, make the pressure much slower of refrigeration agent, the temperature of saturation that there is the refrigeration agent in vaporizer 14 is lower than the worry (that is, can not carry out the worry of the appropriate running of refrigerating circulatory device) of vaporization temperature (the utilizing vaporization temperature of vaporizer 14) of user for utilizing at vaporizer 14.
In order to prevent this kind of situation, based on, in the refrigerating circulatory device of present embodiment, the temperature of saturation of the refrigeration agent in vaporizer 14 is not less than the scope utilizing vaporization temperature of vaporizer 14, setting the size of the pressure-losses of the refrigeration agent in the 1st communicating pipe 3. That is, the scope of vaporization temperature that utilizes that the temperature of saturation becoming the refrigeration agent in vaporizer 14 the 1st communicating pipe 3 is not less than vaporizer 14 produces communicating pipe of the pressure-losses of refrigeration agent. The size of the pressure-losses of the refrigeration agent in the 1st communicating pipe 3 is set by the length and internal diameter adjusting for the 1st communicating pipe 3.
Usually, the vaporization temperature utilized at vaporizer 14 is-40 DEG C～0 DEG C. Therefore, if the temperature of saturation that the pressure of the refrigeration agent in vaporizer 14 remains the refrigeration agent in vaporizer 14 is not less than-40 DEG C (utilizing vaporization temperature), then the appropriate running of refrigerating circulatory device can be carried out.
Fig. 3 is the pressure-losses of the refrigeration agent in the 1st communicating pipe 3 representing Fig. 1 and the chart of the relation of the internal diameter of the 1st communicating pipe 3. If imagination is such as arranged on the refrigerating circulatory device in the shops such as supermarket, then the maximum length of the 1st communicating pipe 3 is about 100m. In figure 3, each in the inlet pressure of the 1st communicating pipe 3 of the length of the 1st communicating pipe 3 when being 100m and top hole pressure is represented.
As shown in Figure 3, recognizing that the internal diameter of the 1st communicating pipe 3 is more little, the inlet pressure of the 1st communicating pipe 3 and the difference of top hole pressure are more big, and the pressure-losses of the refrigeration agent in the 1st communicating pipe 3 is more big. Based in the refrigerating circulatory device of present embodiment, if imagination such as by main reliever 13 by the pressure of refrigeration agent to 4.15MPa (design pressure of the 1st communicating pipe 3), then according to Fig. 3, the internal diameter of the 1st communicating pipe 3 remaining on more than 0.90MPa (being equivalent to the pressure of the refrigeration agent of vapour temperature-40 DEG C) for the top hole pressure of the 1st communicating pipe 3 by length being 100m is more than 10.3mm.
Fig. 4 is the pressure-losses of the refrigeration agent in the 1st communicating pipe 3 representing Fig. 1 and the chart of the relation of the length of the 1st communicating pipe 3. Such as, if imagination is arranged on the refrigerating circulatory device as shown in Figure 2 in the shops such as supermarket, then the internal diameter of the 1st communicating pipe 3 is 12.7mm. In the diagram, each in the inlet pressure of the 1st communicating pipe 3 of the internal diameter of the 1st communicating pipe 3 when being 12.7mm and top hole pressure is represented.
As shown in Figure 4, recognizing that the length of the 1st communicating pipe 3 is more long, the inlet pressure of the 1st communicating pipe 3 and the difference of top hole pressure are more big, and the pressure-losses of the refrigeration agent in the 1st communicating pipe 3 is more big.Based in the refrigerating circulatory device of present embodiment, such as, if imagination by main reliever 13 by the pressure of refrigeration agent to 4.15MPa (design pressure of the 1st communicating pipe 3), then according to Fig. 4, the length of the 1st communicating pipe 3 remaining on more than 0.90MPa (being equivalent to the pressure of the refrigeration agent of vaporization temperature-40 DEG C) for the top hole pressure of the 1st communicating pipe 3 by internal diameter being 12.7mm is below 142m.
Based on, in the refrigerating circulatory device of present embodiment, the internal diameter of the 1st communicating pipe 3 is the length of more than 10.3mm or the 1st communicating pipe 3 is below 142m. Accordingly, suppress the pressure-losses of the refrigeration agent in the 1st communicating pipe 3, the appropriate running of refrigerating circulatory device can be carried out. The length of the 1st communicating pipe 3 owing to inhibiting the pressure-losses of refrigeration agent, so, as long as at more than 0m. In addition, the upper limit of the internal diameter of the 1st communicating pipe 3 is the size being received into and joining pipe installation space, or reaches the size of the refrigerant flow rates of the degree that non-compatible refrigerator oil can flow.
In addition, based in the refrigerating circulatory device of present embodiment, because the refrigeration agent reduced pressure by main reliever 13 passed in the 1st communicating pipe 3, so, the refrigeration agent in the 1st communicating pipe 3 becomes gas-liquid two-phase state. In the 1st communicating pipe 3, owing to the mass dryness fraction of gas-liquid two-phase refrigeration agent is more low, refrigeration agent is more single-phase close to liquid, so, the pressure-losses of refrigeration agent diminishes. On the other hand, in the 1st communicating pipe 3, the pressure of gas-liquid two-phase refrigeration agent more reduces, and the mass dryness fraction of refrigeration agent more increases. Due to such situation, in this embodiment, in order to make the pressure-losses of the refrigeration agent in the 1st communicating pipe 3 little, the decompression amplitude of refrigeration agent is adjusted by main reliever 13, so that the scope below the design pressure of the 1st communicating pipe 3, make the pressure height of the refrigeration agent in the 1st communicating pipe 3 as far as possible. In this embodiment, that is, by main reliever 13, refrigeration agent is reduced pressure, so that the inlet pressure of the 1st communicating pipe 3 becomes the design pressure of the 1st communicating pipe 3.
In such refrigerating circulatory device, because by main reliever 13 to the decompression of refrigeration agent, it is possible to make the pressure of the refrigeration agent in the 1st communicating pipe 3 become low, so, it is possible to the withstand voltage properties of the 1st communicating pipe 3 is designed low. Such as, such as, it is thus possible to the communicating pipe of the refrigerating circulatory device of common refrigeration agent (R410A etc.) will be used as use high-pressure refrigerant (CO2Deng) the applying the 1st communicating pipe 3 of refrigerating circulatory device. Such as, when when being revised as the refrigerating circulatory device using high-pressure refrigerant communicating pipe of the existing refrigerating circulatory device by using common refrigeration agent, can again utilize the communicating pipe of existing refrigerating circulatory device without change, it is possible to seek to alleviate labour and the time of refrigerating circulatory device amendment engineering. In addition, even if when being newly set using the refrigerating circulatory device of high-pressure refrigerant, because by the reduction of the pressure in the 1st communicating pipe 3, the wall thickness of the 1st communicating pipe 3 can be made thinning, so, the bending machining of the 1st communicating pipe 3 can be made and connect operation to become easy, it is possible to alleviate the labour arranging operation and the time of on-the-spot refrigerating circulatory device.
In addition, because the temperature of saturation of the refrigeration agent in vaporizer 14 is not less than in the scope utilizing vaporization temperature of vaporizer 14, inhibit the pressure-losses of the refrigeration agent in the 1st communicating pipe 3, so, can prevent the vaporization temperature that utilizes at vaporizer 14 from there is no the situation appropriately carrying out the evaporation of refrigeration agent, it is possible to avoid the reducing of appropriate operating range of refrigerating circulatory device.
That is, based in the refrigerating circulatory device of present embodiment, it is possible to meet and alleviate the labour and the time that arrange operation or amendment operation and avoid reducing of appropriate operating range simultaneously.
In addition because the internal diameter of the 1st communicating pipe 3 in more than 10.3mm or the length of the 1st communicating pipe 3 at below 142m, so, it is possible to easily suppress the pressure-losses of the refrigeration agent in the 1st communicating pipe 3 with simple structure.
In addition, in the example, the on high-tension side pressure of refrigeration cycle is below the emergent pressure of refrigeration agent, but can also operate in the overcritical region that the emergent pressure of the on high-tension side pressure ratio refrigeration agent of refrigeration cycle is high.
Enforcement mode 2.
Implementing in mode 1, without change the refrigeration agent from the 1st communicating pipe 3 is carried to vaporizer 14, but, flow control portion 21 can also be set between the 1st communicating pipe 3 and vaporizer 14, have adjusted after the flow of the refrigeration agent of the 1st communicating pipe 3 by flow control portion 21, refrigeration agent is carried to vaporizer 14, accordingly, controls the superheating temperature from the outlet of vaporizer 14 refrigeration agent out.
That is, Fig. 5 is the structure iron representing the refrigerating circulatory device based on embodiments of the present invention 2. Cooling unit 2 also has flow control portion (cooling unit side reliever) 21. Flow control portion 21 is arranged at the pipe connecting connecting the 1st communicating pipe 3 and vaporizer 14. In addition, the refrigeration agent from the 1st communicating pipe 3 is reduced pressure by flow control portion 21, and carries to vaporizer 14. In this embodiment, flow control portion 21 is the electric expansion valve of the flow of adjustable refrigeration agent. Flow control portion 21 is controlled by not shown control portion. Vaporizer 14 makes the refrigeration agent evaporation reduced pressure by flow control portion 21.
By the adjustment of the flow of refrigeration agent being controlled by flow control portion 21 superheating temperature of the refrigeration agent of the outlet of vaporizer 14. Such as, reduce pressure by main reliever 13 at refrigeration agent, after the pressure of the refrigeration agent in the 1st communicating pipe 3 becomes 4.15MPa (design pressure of the 1st communicating pipe 3), adjust the flow of refrigeration agent by flow control portion 21, it is 5 DEG C～10 DEG C from the superheating temperature of the outlet of vaporizer 14 refrigeration agent out. Other structure is identical with enforcement mode 1.
In such refrigerating circulatory device, because making cooling unit 2 comprise the flow control portion 21 reduced pressure by the refrigeration agent from the 1st communicating pipe 3 and carry to vaporizer 14, so, it is possible to control each in the vaporization temperature in the pressure of the refrigeration agent in the 1st communicating pipe 3 and vaporizer 14 more reliably. It is thus possible to one side suppresses the increase of the pressure-losses of the refrigeration agent in the 1st communicating pipe 3 more reliably, one side makes refrigeration agent fully evaporate in vaporizer 14, it is possible to seek the cooling performance improved in vaporizer 14. Accordingly, it may be possible to carry out returning from vaporizer 14 gas of the refrigeration agent of compressor 11 more reliably, it is possible to avoid because liquid refrigeration agent returns the fault etc. of the compressor 11 that compressor 11 causes.
Here, by the flow control portion 21 of cooling unit 2 to the decompression adjusting range of refrigeration agent at about below 0.3MPa. Accordingly, it may be possible to the maximum value making the pressure of the refrigeration agent in the 1st communicating pipe 3 becomes the pressure of 0.3MPa higher than evaporating pressure. Accordingly, it may be possible to improve the pressure of the refrigeration agent in the 1st communicating pipe 3 in the scope of design pressure, it is possible to one side seeks the thin-walled property of the 1st communicating pipe 3, one side suppresses the increase of the pressure-losses of the 1st communicating pipe 3. In addition, if the upper limit of the pressure of the refrigeration agent in the 1st communicating pipe 3 is design pressure 4.15MPa, then the upper limit of evaporating pressure becomes 3.85MPa, and the vaporization temperature corresponding with the evaporating pressure of 3.85MPa becomes 5 DEG C.Usually, because the vaporization temperature of refrigerating circulatory device is-40 DEG C～0 DEG C, so, it is possible to guarantee utilizing more than vaporization temperature by the temperature of saturation of the refrigeration agent in vaporizer 14, it is possible to avoid the reducing of appropriate operating range of refrigerating circulatory device.
In addition, implementing in mode 2, it is also possible to be connected in parallel multiple cooling unit 2 in the 1st shared communicating pipe 3, from the 1st shared communicating pipe 3 to each cooling unit 2 refrigerant conveying. In this case, carry out the main decompression of refrigeration agent by the main reliever 13 of heat source unit 1, make the pressure of the refrigeration agent in the 1st communicating pipe 3 become design pressure (4.15MPa) below. In addition, in this case, the distribution to each vaporizer 14 of refrigerant flow and the refrigeration capacity of each cooling unit 2 are correspondingly undertaken by each flow control portion 21. That is, the adjustment of the flow of each vaporizer of the whereabouts of refrigeration agent 14 is undertaken by each flow control portion 21, to make the vaporization temperature in each vaporizer 14 become utilize temperature. So, it is possible to one side suppresses the increase of the pressure-losses of the refrigeration agent in the 1st communicating pipe 3 more reliably, and one side, in each cooling unit 2, makes refrigeration agent fully evaporate, it is possible to seek the cooling performance improved in each cooling unit.
Enforcement mode 3.
Fig. 6 is the structure iron representing the refrigerating circulatory device based on embodiments of the present invention 3. Heat source unit 1 also has inner heat exchanger 31. Inner heat exchanger 31 carries out heat exchange at the refrigeration agent carried from the 2nd communicating pipe 4 to compressor 11 with from condenser 12 between the refrigeration agent that main reliever 13 is carried. That is, heat exchange is carried out between the refrigeration agent of inner heat exchanger 31 at the gas shape sucked to compressor 11 and the outlet from condenser 12 liquid refrigeration agent out. In inner heat exchanger 31, by the refrigeration agent carried from condenser 12 to main reliever 13 to the refrigeration agent rejected heat carried from the 2nd communicating pipe 4 to compressor 11. Other structure is identical with enforcement mode 2.
In such refrigerating circulatory device, because heat source unit 1 is included in the refrigeration agent carried from the 2nd communicating pipe 4 to compressor 11 and carries out the inner heat exchanger 31 of heat exchange from condenser 12 between the refrigeration agent that main reliever 13 is carried, so, the degree of subcooling entering the liquid refrigeration agent of main reliever 13 can be made to increase, it is possible to the mass dryness fraction of the refrigeration agent in the 1st communicating pipe 3 is reduced. It is thus possible to suppress the pressure-losses of the refrigeration agent in the 1st communicating pipe 3, it is possible to guarantee the top hole pressure of the 1st communicating pipe 3 so that the temperature of saturation of the refrigeration agent in vaporizer 14 be not less than vaporizer 14 utilize vaporization temperature. It is thus possible to carry out the appropriate running of refrigerating circulatory device more reliably.
In addition, implementing in mode 3, inner heat exchanger 31 is applied to the heat source unit 1 of enforcement mode 2, however, it may also be possible to inner heat exchanger 31 is applied to the heat source unit 1 of enforcement mode 1.
Enforcement mode 4.
Fig. 7 is the structure iron representing the refrigerating circulatory device based on embodiments of the present invention 4. Heat source unit 1 also has bypass loop 41 and bypass heat exchanger 42.
Bypass loop 41 has bypass pipe 44 that bypass reliever 43 and the refrigeration agent that reduced pressure by bypass reliever 43 of the part decompression of the refrigeration agent from the main reliever 13 of condenser 12 whereabouts are carried to the suction port of compressor 11. In this embodiment, bypass reliever 43 is the electric expansion valve of the flow of adjustable refrigeration agent.
Bypass heat exchanger 42 carries out heat exchange between the refrigeration agent carried to main reliever 13 from condenser 12 and the refrigeration agent reduced pressure by bypass reliever 43. That is, bypass heat exchanger 42 carries out heat exchange at the liquid refrigeration agent out of the outlet from condenser 12 with between the refrigeration agent of bypass reliever 43 gas-liquid two-phase state out. In bypass heat exchanger 42, by the refrigeration agent carried from condenser 12 to main reliever 13 to the refrigeration agent rejected heat reduced pressure by bypass reliever 43. Other structure is identical with enforcement mode 2.
In such refrigerating circulatory device, because heat source unit 1 is included in the bypass heat exchanger 42 carrying out heat exchange between refrigeration agent and the refrigeration agent reduced pressure by bypass reliever 43 carried from condenser 12 to main reliever 13, so, the degree of subcooling entering the liquid refrigeration agent of main reliever 13 can be made to increase, it is possible to the mass dryness fraction of the refrigeration agent in the 1st communicating pipe 3 is reduced. Accordingly, same with enforcement mode 3, it is possible to suppress the pressure-losses of the refrigeration agent in the 1st communicating pipe 3. In addition, because by the part from condenser 12 refrigeration agent out being carried to compressor 11 by bypass loop 41, the flow-reduction of the refrigeration agent in the 1st communicating pipe 3, so, it is possible to suppress the pressure-losses of the refrigeration agent in the 1st communicating pipe 3 further. Accordingly, it may be possible to carry out the appropriate running of refrigerating circulatory device more reliably.
In addition, implementing in mode 4, bypass loop 41 and bypass heat exchanger 42 are applied to the heat source unit 1 of enforcement mode 2, however, it may also be possible to bypass loop 41 and bypass heat exchanger 42 are applied to the heat source unit 1 of enforcement mode 1.
In addition, it is also possible to the inner heat exchanger 31 based on enforcement mode 3 is applied to the heat source unit 1 based on enforcement mode 4. Namely, it is possible to the inner heat exchanger 31 based on enforcement mode 3 and the bypass loop 41 based on enforcement mode 4 and bypass heat exchanger 42 are all applied to the heat source unit 1 based on enforcement mode 1 or 2.
Enforcement mode 5.
Fig. 8 is the structure iron representing the refrigerating circulatory device based on embodiments of the present invention 5. Heat source unit 1 also has by liquid device 51. Store from condenser 12 liquid refrigeration agent out by liquid device 51. Accordingly, the saturated liquid state of refrigeration agent is become by the outlet of liquid device 51. It is stored in the liquid refrigeration agent by liquid device 51 to the conveying of main reliever 13. Other structure is identical with enforcement mode 2.
In such refrigerating circulatory device, because being stored in by liquid device 51 from condenser 12 liquid refrigeration agent out, it is stored in the liquid refrigeration agent by liquid device 51 to carry to main reliever 13, so, it is possible to prevent the refrigeration agent to the conveying of main reliever 13 from becoming gas-liquid two-phase state. It is thus possible to the mass dryness fraction making the refrigeration agent in the 1st communicating pipe 3 reduces, it is possible to suppress the increase of the pressure-losses of the refrigeration agent in the 1st communicating pipe 3. It is thus possible to guarantee the top hole pressure of the 1st communicating pipe 3 so that the temperature of saturation of the refrigeration agent in vaporizer 14 be not less than vaporizer 14 utilize vaporization temperature, it is possible to carry out the appropriate running of refrigerating circulatory device more reliably.
In addition, such as, when arranging multiple cooling unit 2, produce big load variation because of the switching of operating number of each cooling unit 2. Now, if not by liquid device 51, the then lack of refrigerant of condenser 12, the refrigeration agent of the outlet of condenser 12 becomes gas-liquid two-phase state, and the running efficiency of refrigerating circulatory device can reduce.Implementing in mode 5, because being stored in by liquid device 51 from condenser 12 liquid refrigeration agent out, so, it is possible to avoid the lack of refrigerant of condenser 12, it is possible to avoid the reduction of the running efficiency of refrigerating circulatory device.
Above, the concrete enforcement mode of the present invention is illustrated, but, the present invention is not limited to each described enforcement mode, it is possible to carries out various change within the scope of the invention and implements. Such as, design pressure as the 1st communicating pipe 3 is not limited to 4.15MPa, it is also possible to will employ the design pressure of on high-tension side design pressure (that is, 2.94MPa) as the 1st communicating pipe 3 of the refrigerating circulatory device of R404A refrigeration agent. In this case, as shown in Fig. 9 and Figure 10, by making the internal diameter of the 1st communicating pipe 3 at below 11.0mm or make the length of the 1st communicating pipe 3 at below 275m, the temperature of saturation of the refrigeration agent in vaporizer 14 is not less than the scope utilizing vaporization temperature of vaporizer 14, the size of the pressure-losses of the refrigeration agent in the 1st communicating pipe 3 of setting.
In addition, in each described enforcement mode, 1st detector of the detection temperature of refrigeration agent or pressure can also being arranged on the 1st communicating pipe 3 or vaporizer 14, the pressure of the refrigeration agent in the 1st communicating pipe 3 obtained according to the detected result from the 1st detector by control portion, controls main reliever 13. In this case, such as, the pressure transmitter (the 1st detector) of the pressure of detection refrigeration agent can be arranged on for the 1st communicating pipe 3, according to the information from pressure transmitter, obtain the pressure of the refrigeration agent in the 1st communicating pipe 3, maybe the temperature sensor (the 1st detector) detecting the temperature of refrigeration agent is arranged on vaporizer 14, from the temperature information based on temperature sensor of vaporizer 14, obtains the pressure of the refrigeration agent in the 1st communicating pipe 3. In addition, such as, additionally it is possible to the temperature sensor (the 1st detector) of the temperature of detection refrigeration agent was arranged on for the 1st communicating pipe 3, from the temperature information based on temperature sensor of the 1st communicating pipe 3, obtains the pressure of the refrigeration agent in the 1st communicating pipe 3. So, it is possible to more correctly carry out the adjustment of the pressure of the refrigeration agent in the 1st communicating pipe 3.
In addition, implementing in mode 2～5,2nd detector (pressure transmitter or temperature sensor) of the temperature of detection refrigeration agent or pressure can also be arranged on vaporizer 14, the pressure of the refrigeration agent in the exit of the vaporizer 14 obtained according to the detected result from the 2nd detector, controls flow control portion 21 by control portion. So, it is possible to more correctly carry out the adjustment of the superheating temperature of the refrigeration agent in the exit of vaporizer 14.
In addition, in each described enforcement mode, the quantity of cooling unit 2 is not limited to 1, it is possible to so that the quantity of cooling unit 2 is multiple. Have again, it is possible to so that the quantity of heat source unit 1 is multiple. When being multiple when making the quantity of heat source unit 1, from the refrigeration agent of each of main reliever 13 of each heat source unit 1 by the 1st communicating pipe 3 conducting shared, carry to cooling unit 2.
In addition, in each described enforcement mode, as the refrigeration agent of refrigerating circulatory device, it may also be useful to as the CO of high-pressure refrigerant2, however, it may also be possible to the CO that the high-tension side of refrigeration cycle is operated in overcritical region2Refrigeration agent in addition (such as, the freon refrigerant of R32 etc., containing CO2And any one the mix refrigerant of R32, ethene, ethane, nitrogen oxide etc.) use as the refrigeration agent of refrigerating circulatory device.
In addition, based on the refrigerating circulatory device of each described enforcement mode except being applied to the cooling display stands being arranged on shop, it is possible to be applied to various refrigerating unit, refrigerating installation etc.
Claims (7)
1. a refrigerating circulatory device, it is characterised in that, possess heat source unit, cooling unit, the 1st communicating pipe and the 2nd communicating pipe,
Described heat source unit has the compressor of compressed refrigerant, the high-tension side heat exchanger cooling the refrigeration agent from described compressor and the main reliever reduced pressure by the refrigeration agent from described high-tension side heat exchanger,
Described cooling unit has the low-tension side heat exchanger that refrigeration agent is evaporated,
The refrigeration agent that described 1st communicating pipe, conducting was carried from described main reliever to described low-tension side heat exchanger between described heat source unit and described cooling unit,
The refrigeration agent that described 2nd communicating pipe, conducting was carried from described low-tension side heat exchanger to described compressor between described heat source unit and described cooling unit,
Described 1st communicating pipe is that the scope of vaporization temperature that utilizes that the temperature of saturation of the refrigeration agent in described low-tension side heat exchanger is not less than described low-tension side heat exchanger produces communicating pipe of the pressure-losses of refrigeration agent.
2. refrigerating circulatory device as claimed in claim 1, it is characterised in that, described cooling unit has the cooling unit side reliever reduced pressure by the refrigeration agent from described 1st communicating pipe and carry to described low-tension side heat exchanger.
3. refrigerating circulatory device as claimed in claim 1 or 2, it is characterized in that, described heat source unit has at the refrigeration agent carried to described compressor from described 2nd communicating pipe and the inner heat exchanger carrying out heat exchange from described high-tension side heat exchanger between the refrigeration agent that described main reliever is carried.
4. refrigerating circulatory device as described in the arbitrary item in claims 1 to 3, it is characterized in that, described heat source unit has bypass loop and bypass heat exchanger, described bypass loop comprises the bypass reliever of the part decompression of the refrigeration agent from main reliever described in the heat exchanger whereabouts of described high-tension side, and the refrigeration agent reduced pressure by described bypass reliever is carried to described compressor, described bypass heat exchanger carries out heat exchange at the refrigeration agent reduced pressure by described bypass reliever with from described high-tension side heat exchanger between the refrigeration agent that described main reliever is carried.
5. refrigerating circulatory device as described in the arbitrary item in Claims 1-4, it is characterised in that, have store from described high-tension side heat exchanger liquid refrigeration agent out by liquid device,
It is stored in the described liquid refrigeration agent by liquid device to the conveying of described main reliever.
6. refrigerating circulatory device as described in the arbitrary item in claim 1 to 5, it is characterised in that, the internal diameter of described 1st communicating pipe is for being more than or equal to 10.3mm, or the length of described 1st communicating pipe is for being less than or equal to 142m.
7. refrigerating circulatory device as described in the arbitrary item in claim 1 to 6, it is characterised in that, refrigeration agent is CO2, R32 or comprise CO2And the mix refrigerant of any one of R32.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2013/079147 WO2015063838A1 (en) | 2013-10-28 | 2013-10-28 | Refrigeration cycle device |
Publications (1)
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|---|---|
| CN105683681A true CN105683681A (en) | 2016-06-15 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201380080566.3A Pending CN105683681A (en) | 2013-10-28 | 2013-10-28 | Refrigeration cycle device |
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| Country | Link |
|---|---|
| JP (1) | JPWO2015063838A1 (en) |
| CN (1) | CN105683681A (en) |
| GB (1) | GB2534510B (en) |
| WO (1) | WO2015063838A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111527177A (en) * | 2017-12-12 | 2020-08-11 | 大金工业株式会社 | Refrigerant containing fluorocarbon and carbon dioxide, use thereof, refrigerator having the refrigerant, and method for operating the refrigerator |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
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| JP2017145975A (en) * | 2016-02-15 | 2017-08-24 | 三菱電機株式会社 | Refrigeration cycle device, process of manufacture of refrigeration cycle device, drop-in method for refrigeration cycle device, and replace method for refrigeration cycle device |
| JP6833065B2 (en) * | 2017-11-29 | 2021-02-24 | 三菱電機株式会社 | Refrigeration equipment and outdoor unit |
| JP7150148B2 (en) * | 2019-04-10 | 2022-10-07 | 三菱電機株式会社 | Outdoor unit, refrigeration cycle device and refrigerator |
| JP7282258B2 (en) * | 2020-03-27 | 2023-05-26 | 三菱電機株式会社 | Outdoor unit and refrigeration cycle equipment |
| JP2023062750A (en) * | 2021-10-22 | 2023-05-09 | パナソニックＩｐマネジメント株式会社 | air conditioner |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05332630A (en) * | 1992-05-29 | 1993-12-14 | Hitachi Ltd | Air conditioner |
| JPH0875290A (en) * | 1994-09-06 | 1996-03-19 | Hitachi Ltd | Heat pump type air conditioner |
| JPH10160268A (en) * | 1996-11-25 | 1998-06-19 | Hitachi Ltd | Air conditioner |
| JP2005226950A (en) * | 2004-02-16 | 2005-08-25 | Mitsubishi Electric Corp | Refrigerating air conditioner |
| CN101124436A (en) * | 2004-08-11 | 2008-02-13 | L·卡特斯 | Method and apparatus for monitoring refrigerant-cycle systems |
| CN102734969A (en) * | 2011-04-07 | 2012-10-17 | 松下电器产业株式会社 | Refrigeration cycle apparatus and hydronic heater including the refrigeration cycle apparatus |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007232244A (en) * | 2006-02-28 | 2007-09-13 | Mitsubishi Electric Corp | Replacement kit for cleaning piping, its use method, and refrigerating cycle device |
| JP5424705B2 (en) * | 2009-05-01 | 2014-02-26 | 三菱電機株式会社 | Refrigeration air conditioner |
| JP5627417B2 (en) * | 2010-11-26 | 2014-11-19 | 三菱電機株式会社 | Dual refrigeration equipment |
-
2013
- 2013-10-28 WO PCT/JP2013/079147 patent/WO2015063838A1/en active Application Filing
- 2013-10-28 GB GB1606526.0A patent/GB2534510B/en active Active
- 2013-10-28 JP JP2015544640A patent/JPWO2015063838A1/en active Pending
- 2013-10-28 CN CN201380080566.3A patent/CN105683681A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05332630A (en) * | 1992-05-29 | 1993-12-14 | Hitachi Ltd | Air conditioner |
| JPH0875290A (en) * | 1994-09-06 | 1996-03-19 | Hitachi Ltd | Heat pump type air conditioner |
| JPH10160268A (en) * | 1996-11-25 | 1998-06-19 | Hitachi Ltd | Air conditioner |
| JP2005226950A (en) * | 2004-02-16 | 2005-08-25 | Mitsubishi Electric Corp | Refrigerating air conditioner |
| CN101124436A (en) * | 2004-08-11 | 2008-02-13 | L·卡特斯 | Method and apparatus for monitoring refrigerant-cycle systems |
| CN102734969A (en) * | 2011-04-07 | 2012-10-17 | 松下电器产业株式会社 | Refrigeration cycle apparatus and hydronic heater including the refrigeration cycle apparatus |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111527177A (en) * | 2017-12-12 | 2020-08-11 | 大金工业株式会社 | Refrigerant containing fluorocarbon and carbon dioxide, use thereof, refrigerator having the refrigerant, and method for operating the refrigerator |
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| Publication number | Publication date |
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| WO2015063838A1 (en) | 2015-05-07 |
| JPWO2015063838A1 (en) | 2017-03-09 |
| GB2534510B (en) | 2020-03-11 |
| GB2534510A (en) | 2016-07-27 |
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