WO2009147882A1 - 冷凍サイクル装置 - Google Patents
冷凍サイクル装置 Download PDFInfo
- Publication number
- WO2009147882A1 WO2009147882A1 PCT/JP2009/054874 JP2009054874W WO2009147882A1 WO 2009147882 A1 WO2009147882 A1 WO 2009147882A1 JP 2009054874 W JP2009054874 W JP 2009054874W WO 2009147882 A1 WO2009147882 A1 WO 2009147882A1
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- refrigerant
- pressure
- compressor
- heat exchanger
- expander
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- 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
- F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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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
- F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2400/07—Details of compressors or related parts
- F25B2400/072—Intercoolers therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/14—Power generation using energy from the expansion of the refrigerant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
Definitions
- the present invention relates to a refrigeration cycle apparatus using a supercritical refrigerant, and in particular, a configuration of a refrigeration cycle apparatus that covers a necessary driving force of a second compressor connected in series to a first compressor with a recovery power in an expander. It is about.
- an auxiliary compression mechanism and an expansion mechanism are connected to a single shaft, and a compression mechanism that compresses refrigerant and auxiliary compression that further compresses refrigerant discharged from the compression mechanism A mechanism, a radiator that cools the refrigerant discharged from the auxiliary compression mechanism, an evaporator that heats the refrigerant that has flowed out of the expansion mechanism, a bypass passage that bypasses the expansion mechanism, and a bypass valve provided on the bypass passage And an operation device that controls the operation of the bypass valve, and this operation device changes the opening degree of the bypass valve to adjust the high-pressure side pressure (for example, patent document). 1).
- the density ratio refers to the ratio DE / DC of the density (DE) of the refrigerant flowing into the expansion mechanism and the density (DC) of the refrigerant flowing into the auxiliary compression mechanism.
- An object of the present invention is to solve the above-described problems, and the amount of heat exchange between the high-pressure refrigerant and the reduced-pressure refrigerant is performed in the refrigerant flow path portion where the high-pressure refrigerant flows into the expander.
- the COP An object is to obtain a refrigeration cycle apparatus that is improved and in which the pressure loss of the refrigerant is reduced.
- the refrigeration cycle apparatus includes a first compressor that raises a low-pressure refrigerant that is a low-pressure side refrigerant to an intermediate-pressure refrigerant that is an intermediate-pressure refrigerant, and the intermediate-pressure refrigerant that is connected in series with the first compressor.
- a second compressor that boosts the pressure of the high-pressure refrigerant that is a high-pressure side refrigerant, a first heat source-side heat exchanger that is connected in series to the second compressor and through which the high-pressure refrigerant flows, and the first heat source-side heat exchanger And the high-low pressure heat exchanger connected in series to the high-low pressure heat exchanger, the high-pressure refrigerant is decompressed to the low-pressure refrigerant in series with the high-low pressure heat exchanger, and the second compressor is driven with the recovered power at that time
- An expander and a load-side heat exchanger connected in series to the expander are provided, and in the high-low pressure heat exchanger, the recovered power in the expander and the necessary power of the second compressor are balanced.
- the high-pressure refrigerant and the high-low pressure heat exchanger Varying the amount of heat exchange between the vacuum refrigerant branched at the inlet portion of the pressure refrigerant is depressurized, so as to adjust the density of the refrigerant flowing into the expander.
- the refrigeration cycle apparatus includes a first compressor that boosts a low-pressure refrigerant that is a low-pressure side refrigerant to an intermediate-pressure refrigerant that is an intermediate-pressure refrigerant, and the intermediate compressor connected in series to the first compressor.
- a second compressor that boosts the pressurized refrigerant to a high-pressure refrigerant on the high-pressure side, a first heat source-side heat exchanger connected in series to the second compressor, and the first heat source-side heat exchanger connected in series.
- a high-low pressure heat exchanger an expander connected in series to the high-low pressure heat exchanger to depressurize the high-pressure refrigerant to a low-pressure refrigerant and drive the second compressor with the recovered power at that time, and the expander Is connected to a load-side heat exchanger connected in series to a refrigerant flow path section on the discharge side of the high-pressure refrigerant of the second compressor, and the high-pressure refrigerant from the second compressor is connected to the first heat source side.
- the first four-way valve and the high- and low-pressure heat exchanger are attached to the refrigerant flow path portion on the inflow side of the high-pressure refrigerant, and from the high-pressure refrigerant from the load-side heat exchanger or the first heat source-side heat exchanger, A second four-way valve that operates so that the high-pressure refrigerant flows into the high-low pressure heat exchanger, and in the high-low pressure heat exchanger, the recovered power in the expander and the necessary power of the second compressor are balanced.
- the amount of heat exchange between the high-pressure refrigerant and the reduced-pressure refrigerant branched and depressurized at the inlet of the high-pressure refrigerant of the high-low pressure heat exchanger is changed, and the density of the refrigerant flowing into the expander is changed. It comes to adjust.
- the high-low pressure heat exchanger changes the amount of heat exchange between the high-pressure refrigerant and the reduced-pressure refrigerant, and adjusts the density of the refrigerant flowing into the expander, thereby expanding Since the recovery power in the compressor and the necessary power of the second compressor are balanced, the COP is improved and the pressure loss of the refrigerant is reduced.
- FIG. 1 is a configuration diagram showing a refrigeration cycle apparatus according to Embodiment 1 of the present invention.
- FIG. FIG. 2 is a diagram showing a cooling operation operation on a Ph diagram of the refrigeration cycle apparatus of FIG. 1. It is sectional drawing which shows the expander unit of FIG. It is a flowchart which shows the design procedure of the refrigerating-cycle apparatus of FIG. It is a block diagram which shows the refrigerating-cycle apparatus which concerns on Embodiment 2 of this invention.
- FIG. 6 is a diagram showing a cooling operation on the Ph diagram of the refrigeration cycle apparatus of FIG. 5.
- FIG. 6 is a diagram showing an operation of heating operation on the Ph diagram of the refrigeration cycle apparatus of FIG. 5.
- FIG. 1 is a block diagram showing a refrigeration cycle apparatus according to Embodiment 1 of the present invention.
- the refrigeration cycle apparatus includes an outdoor unit 100 and an indoor unit 200a.
- the outdoor unit 100 includes a first compressor 1 that raises a low-pressure refrigerant that is a low-pressure side refrigerant to an intermediate-pressure refrigerant that is an intermediate-pressure refrigerant, and the first compressor 1 and the refrigerant flow path section in series.
- the connected second heat source side heat exchanger 3b and the second heat source side heat exchanger 3b are connected in series via the refrigerant flow path portion and the intermediate pressure refrigerant is boosted to a high pressure refrigerant which is a high pressure side refrigerant.
- a second compressor 5b and a first heat source side heat exchanger 3a that is connected in series to the second compressor 5b via a refrigerant flow path and through which the high-pressure refrigerant flows are provided. Both ends of a bypass flow path portion 59 that is bypassed are connected to the suction portion and the discharge portion of the second compressor 5b.
- a bypass valve 53 is attached to the bypass flow path portion 59.
- the first heat source side heat exchanger 3a acts as a radiator that releases the heat of the high-pressure refrigerant
- the second heat source side heat exchanger 3b acts as an intermediate cooler that cools the heat of the intermediate pressure refrigerant.
- Wind from a blower (not shown) built in the outdoor unit 100 is sent to the outer surfaces of the first heat source side heat exchanger 3a and the second heat source side heat exchanger 3b.
- the outdoor unit 100 includes a high-low pressure heat exchanger 61 connected in series to the first heat source side heat exchanger 3a via a refrigerant flow path section, and a high-pressure side flow in series with the high-low pressure heat exchanger 61. And an expander 5a that is connected via a passage portion 63 and depressurizes the high-pressure refrigerant into a low-pressure refrigerant and drives the second compressor 5b with the recovered power at that time.
- the expander 5a is connected to the indoor heat exchanger 9a, which is a load-side heat exchanger of the indoor unit 200a, via the refrigerant flow path portion and the liquid pipe 52.
- the low-pressure side flow path portion 64 is branched.
- An electronic expansion valve 62 is attached to the low pressure side flow path portion 64.
- the tip of the low-pressure channel 64 is connected to the refrigerant channel between the second heat source side heat exchanger 3b and the second compressor 5b. Note that the tip of the low-pressure channel 64 may be connected to the refrigerant channel between the second heat source side heat exchanger 3 b and the first compressor 1.
- the opening degree of the electronic expansion valve 62 By adjusting the opening degree of the electronic expansion valve 62, the amount of heat exchange between the high-pressure refrigerant flowing in the high-pressure side flow path portion 63 and the reduced-pressure refrigerant flowing in the low-pressure side flow path portion 64 is changed.
- the temperature of the high-pressure refrigerant flowing into the expander 5a through and adjusting the density of the high-pressure refrigerant By adjusting the temperature of the high-pressure refrigerant flowing into the expander 5a through and adjusting the density of the high-pressure refrigerant, the recovery power of the expander 5a and the necessary power of the second compressor 5b are balanced.
- the indoor unit 200a includes an indoor heat exchanger 9a that is a load-side heat exchanger and a blower (not shown) that forcibly blows indoor air to the outer surface of the indoor heat exchanger 9a.
- a gas pipe 51 that guides the low-pressure refrigerant to the first compressor 1 is connected to one end side of the indoor heat exchanger 9a, and a liquid that guides the low-pressure refrigerant from the expander 5a to the indoor heat exchanger 9a to the other end side.
- a pipe 52 is connected.
- the refrigerant circulating between the outdoor unit 100 and the indoor unit 200a for example, carbon dioxide that is in a supercritical state at a critical temperature (about 31 ° C.) or higher is used.
- FIG. 3 is a longitudinal sectional view showing the expander unit 5, and this expander unit 5 has a scroll-type integrated structure in which the expander 5 a and the second compressor 5 b are both directly connected via a shaft 308.
- the expander 5 a includes an expander fixed scroll 351 and an expander swing scroll 352. The inside of the expander 5a communicates with the expander suction pipe 313 and the expander discharge pipe 315.
- the second compressor 5 b includes a second compressor fixed scroll 361 and a second compressor swing scroll 362. The inside of the second compressor 5b communicates with the second compressor suction pipe 312 and the second compressor discharge pipe 314.
- a shaft 308 supported by the expander bearing portion 351b and the second compressor bearing portion 361b passes through the center of the scrolls 351, 352, 361, 362.
- Balance weights 309a and 309b are attached to both ends of the shaft 308, respectively.
- the back surface of the orbiting scroll 352 of the expander 5a and the back surface of the orbiting scroll 362 of the second compressor 5b are in surface contact.
- the Oldham ring 307, the crank portion 308b, and the like, which are necessary parts, are accommodated in the sealed container 310.
- An oil return pipe 311 for returning the oil stored in the lower part of the sealed container 310 to the refrigerant flow path between the indoor heat exchanger 9a and the expander 5a is attached to the lower part of the sealed container 310.
- this expansion unit 5 When this expansion unit 5 is designed to have a large expansion / compression volume ratio (for example, an expansion / compression volume ratio of 2.3 or more that minimizes the pre-expansion loss and bypass loss), the expander unit 5 is expanded from the second compressor 5b at the same tooth height. Since the thrust load from the expander 5a to the second compressor 5b side becomes smaller than the thrust load toward the 5a side and the thrust load cannot be canceled on both sides, the second compressor 5b and the expander 5a are integrated. The structure of the expanded expander unit 5 becomes difficult in terms of strength. Further, in order to reduce the thrust load on the second compressor 5b side, it is possible to make the second compressor 5b side a spiral having an extremely high tooth height, but this causes a problem in strength.
- a large expansion / compression volume ratio for example, an expansion / compression volume ratio of 2.3 or more that minimizes the pre-expansion loss and bypass loss
- the expansion / compression volume ratio is set to a range of 2.3 or less, so that not only performance but also structure is reliable. High expander unit 5 can be obtained.
- FIG. 1 shows the solid arrows in symbols A to H shown in the refrigerant circuit of FIG. 1 on the Ph diagram.
- the refrigerants in states C, D, E, and F are high-pressure refrigerants on the high-pressure side
- the refrigerants in states G and H are low-pressure refrigerants on the low-pressure side.
- the refrigerant in the states A and B between the high pressure side and the low pressure side is an intermediate pressure refrigerant.
- the necessary decompression function is realized by the expander 5a, and the pre-expansion valve 6 is adjusted so that an appropriate degree of superheat (for example, 5 to 10 ° C.) set in advance at the outlet of the indoor heat exchanger 9a is obtained.
- an appropriate degree of superheat for example, 5 to 10 ° C.
- the high-temperature and intermediate-pressure gas refrigerant (state A) discharged from the first compressor 1 is radiated to some extent by the second heat source side heat exchanger 3b and cooled (state B). 2 flows into the compressor 5b.
- the gas refrigerant that has flowed into the second compressor 5b driven by the expander 5a is compressed by an amount commensurate with the power recovered by the expander 5a (state C).
- the check valve 53 attached to the bypass flow path portion 59 of the second compressor 5b is in an open state at the time of startup where no pressure difference occurs, but the expander 5a operates to drive the second compressor 5b.
- the second compressor 5b is closed due to the difference in pressure between the refrigerant gas inlet side and the outlet side.
- the gas refrigerant discharged from the second compressor 5b dissipates heat to the air that is the medium to be heated in the first heat source side heat exchanger 3a (state D), and then flows into the high-low pressure heat exchanger 61.
- the heat exchange amount of the high / low pressure heat exchanger 61 provided on the refrigerant inlet side of the expander 5a is controlled by the electronic expansion valve 62 attached to the low pressure side flow path section 64, and the expansion machine 5a
- the recovered power is matched with the required power in the second compressor 5b.
- the operation state in which the density ratio becomes larger than the preset (refrigerant inlet density flowing into the expander 5a / refrigerant inlet density flowing into the second compressor 5b) (hereinafter abbreviated as density ratio).
- density ratio refrigerant inlet density flowing into the expander 5a / refrigerant inlet density flowing into the second compressor 5b.
- the opening degree of the electronic expansion valve 62 is reduced, and the flow rate flowing through the low pressure side flow path portion 64 on the low pressure side is reduced.
- the density ratio is smaller than the preset density ratio
- the amount of heat exchange in the high-low pressure heat exchanger 61 is increased, and the inlet temperature of the refrigerant flowing into the expander 5a is decreased. That is, the density of the refrigerant is increased.
- the opening degree of the electronic expansion valve 62 is increased, and the flow rate flowing through the low pressure side flow path portion 64 on the low pressure side is increased.
- FIG. 4 is a flowchart for designing a refrigeration cycle apparatus.
- the change of the environmental conditions in which the refrigeration cycle apparatus is operated is grasped, and the ranges of the outside air temperature humidity and the indoor temperature humidity are set (step S1).
- the volume ratio of the expander 5a is determined (step S2), and the second heat source side heat exchanger 3b, which is an intermediate cooler, can be realized with the given environmental conditions and the volume ratio of the expander 5a.
- step S3 the specifications of the high / low pressure heat exchanger 61 are determined (step S4).
- the refrigerant inlet density of the expander 5a can be controlled to a desired value by changing the heat exchange amount of the high-low pressure heat exchanger 61 designed in this way by the opening degree of the electronic expansion valve 62 (step S5). it can.
- the refrigerant inlet density of the expander 5a is obtained from the refrigerant inlet temperature and the refrigerant inlet pressure of the expander 5a
- the refrigerant inlet density of the second compressor 5b is the refrigerant inlet temperature and the refrigerant inlet of the second compressor 5b.
- the refrigerant inlet pressure of the expander 5a may be detected by a dedicated pressure sensor or the like, but it can be substituted by correcting the pressure loss or the like for a value of a high pressure sensor or the like installed for another purpose.
- the refrigerant inlet pressure of the second compressor 5b may be detected by attaching a pressure sensor to the pipe from the refrigerant outlet of the first compressor 1 to the refrigerant inlet of the second compressor 5b. Alternatively, it may be estimated from the operating state such as the rotation speed of the second compressor 5b.
- the example in which the expander 5a is used in the cooling-only machine has been shown.
- the present invention is not limited to this, and the expander 5a may be used in a heating-only machine such as a water heater. Good. In this case, water is heated by the refrigerant discharged from the second compressor 5b in the first heat source side heat exchanger 3a, which is a radiator.
- the high and low pressure heat exchanger 61 can adjust the refrigerant inlet density of the expander 5a in accordance with the air conditions, so that the COP is high and the efficiency is high.
- a refrigeration cycle apparatus can be obtained.
- a part of the refrigerant is divided in the low-pressure side flow path portion 64, and this divided refrigerant is second compressed through the indoor heat exchanger 9a, the first compressor 1, and the second heat source side heat exchanger 3b, which are evaporators.
- the refrigerant flow rate that flows into the liquid pipe 52 and the gas pipe 51 that are merged with the refrigerant that flows toward the machine 5b, that is, the indoor heat exchanger 9a and the relatively long pipes, is the amount of the divided refrigerant amount that flows into the low-pressure side flow path section 64. Therefore, the pressure loss due to the refrigerant of the refrigeration cycle apparatus can be reduced.
- both the expander 5a and the second compressor 5b have a scroll-type integrated structure, and the second heat source side heat exchanger is provided in the refrigerant flow path portion between the first compressor 1 and the second compressor 5b. Since 3b is provided, the density ratio between the refrigerant inlet density of the expander 5a and the refrigerant inlet density of the second compressor 5b is reduced, and the expander unit 5 that is highly reliable not only in terms of performance but also in terms of structure can do.
- the 2nd heat source side heat exchanger 3b which heat-exchanges between the refrigerant
- the width can be expanded, and the density ratio of the refrigerant can be changed in accordance with a wide range of air conditions.
- the pre-expansion valve 6 is provided on the refrigerant inlet side of the expander 5a, the degree of superheat of the indoor heat exchanger 9a that is an evaporator can be controlled, and the indoor heat exchanger 9a can be used effectively.
- the adiabatic heat drop (the difference between the enthalpy at the time of isoenthalpy expansion and the enthalpy at the time of isentropic expansion) is increased because the high pressure side is in a supercritical state compared to the case of using other refrigerants.
- a refrigeration cycle apparatus having a high performance improvement effect by the expander 5a can be obtained. The same effect can be obtained with R410A and R404A, which exhibit characteristics close to the supercritical state on the high pressure side.
- FIG. FIG. 5 is a block diagram showing a refrigeration cycle apparatus according to Embodiment 2 of the present invention.
- the outdoor unit 100 includes a first four-way valve 2 that enables switching between a cooling operation and a heating operation by the first compressor 1, and a cooling power recovery operation and a heating power recovery operation by the expander 5a.
- a second four-way valve 4 that enables switching is incorporated.
- the first four-way valve 2 is attached to the refrigerant flow path portion on the discharge side of the high-pressure refrigerant of the second compressor 5b.
- the second four-way valve 4 is attached to the refrigerant flow path that guides the high-pressure refrigerant from the first heat source side heat exchanger 3a to the high-low pressure heat exchanger 61 during the cooling operation.
- the outdoor unit 100 is connected to two indoor units 200a and 200b via a gas pipe 51 and a liquid pipe 52.
- the refrigerant flow path in the outdoor unit 100 is an on-off valve so that both the first heat source side heat exchanger 3a and the second heat source side heat exchanger 3b can be used for both the cooling operation and the heating operation.
- Solenoid valves 54, 55, 56, 57, and 58 are attached. Other configurations are the same as those of the first embodiment, and detailed description thereof is omitted.
- the high-temperature and high-pressure gas refrigerant (state A) discharged from the first compressor 1 passes through the electromagnetic valve 57 and flows into the second heat source side heat exchanger 3b.
- the second heat source side heat exchanger 3 b radiates heat to some extent to be cooled and flows into the electromagnetic valve 58.
- the gas refrigerant (state B) that has passed through the electromagnetic valve 58 flows into the second compressor 5b driven by the expander 5a, and is compressed by an amount that matches the power recovered by the expander 5a.
- the gas refrigerant discharged from the second compressor 5b passes through the first port 2a of the first four-way valve 2 through the second port 2b (state C) and is heated in the first heat source side heat exchanger 3a. (State D), and flows into the high-low pressure heat exchanger 61 from the second port 4b of the second four-way valve 4 through the third port 4c.
- the gas passes through the gas pipe 51, returns from the fourth port 2d of the first four-way valve 2 to the suction portion of the first compressor 1 through the third port 2c (state I). Subsequently, the gas refrigerant flows into the first compressor 1 and is discharged from the first compressor 1 as an intermediate pressure refrigerant (state A) that is a high-temperature and intermediate-pressure refrigerant.
- the high-temperature and high-pressure gas refrigerant discharged from the first compressor 1 (state A) passes through the on-off valve 56 (state B) and flows into the second compressor 5b.
- the refrigerant flowing into the second compressor 5b driven by the expander 5a is compressed by an amount commensurate with the power recovered by the expander 5a.
- the refrigerant discharged from the second compressor 5b flows from the first port 2a of the first four-way valve 2 through the fourth port 2d to the indoor heat exchangers 9a and 9b in the indoor units 200a and 200b.
- the refrigerant radiates heat to the air to be heated by the indoor heat exchangers 9a and 9b (state H), and is slightly depressurized by the electronic expansion valves 8a and 8b (state G).
- the refrigerant that has passed through the liquid pipe 52 flows into the high-low pressure heat exchanger 61 from the fourth port 4d of the second four-way valve 4 through the third port 4c.
- the cooled high-pressure refrigerant (state E) flowing through the high-pressure side flow passage portion 63 flows into the pre-expansion valve 6 by heat exchange between the high-pressure refrigerant flowing through the low-pressure side flow passage 64 and the decompression refrigerant flowing through the low-pressure side flow passage portion 64.
- the refrigerant (state F) decompressed by the pre-expansion valve 6 is decompressed by the expander 5a, passes from the first port 4a of the second four-way valve 4 through the second port 4b (state D), and the first and It flows through the second heat source side heat exchangers 3a and 3b in parallel, and evaporates in the respective heat exchangers 3a and 3b (state C). Subsequently, the refrigerant returns from the second port 2b of the first four-way valve 2 through the third port 2c to the suction portion of the first compressor 1 (state I).
- the low-pressure liquid refrigerant is simultaneously flowed in parallel to the first and second heat source side heat exchangers 3a and 3b during the heating operation and used as an evaporator at the same time, but the heating load is small.
- the electromagnetic valves 54 and 55 may be closed, and the low-pressure liquid refrigerant may be flowed only in the first heat source side heat exchanger 3a to be used as an evaporator.
- the first four-way valve 2 and the second four-way valve 4 are provided, so that the expansion can be performed even in the cooling operation and the heating operation.
- the heat exchange amount of the high / low pressure heat exchanger 61 attached to the refrigerant flow path on the refrigerant inlet side of the machine 5a with the electronic expansion valve 62, the recovery power in the expander 5a can be recovered by the second compressor 5b. Therefore, the refrigeration cycle apparatus having a high COP and high efficiency can be obtained.
- the second heat source side heat exchanger 3b acts as an intermediate cooler together with the high and low pressure heat exchanger 61 that cools the refrigerant for the adjustment of the inlet density of the refrigerant flowing into the expander 5a during the cooling operation, Since it acts as an evaporator during the heating operation, the first and second heat source side heat exchangers 3a and 3b can be used for both the cooling operation and the heating operation, and a highly efficient refrigeration cycle can be configured.
- FIG. FIG. 8 is a block diagram showing a refrigeration cycle apparatus according to Embodiment 3 of the present invention.
- the tip of the low pressure side flow path portion 64 to which the electronic expansion valve 62 is attached is connected to the suction portion of the first compressor 1, and the decompressed refrigerant that has flowed out of the high and low pressure heat exchanger 61. Is guided to the suction portion of the first compressor 1 and flows into the first compressor 1.
- Other configurations are the same as those of the refrigeration cycle apparatus of the second embodiment, and detailed description thereof is omitted.
- the tip of the low pressure side flow path portion 64 is connected to the suction portion of the first compressor 1, so the low pressure side flow path portion 64 is equal to the suction pressure of the first compressor 1. Accordingly, the saturation temperature of the refrigerant flowing through the low pressure side flow path portion 64 of the high and low pressure heat exchanger 61 is lowered, and the temperature of the refrigerant flowing through the low pressure side flow path portion 64 and the temperature of the refrigerant flowing through the high pressure side flow path portion 63 are The amount of heat exchange of the high / low pressure heat exchanger 61 can be increased by widening the difference. Therefore, the change width of the refrigerant inlet density of the expander 5a can be expanded, and the density ratio can be changed in accordance with a wide range of air conditions.
- the expander unit 5 of the scroll type in which both the expander 5a and the second compressor 5b are directly connected via the shaft 308 is used, but of course, the present invention is not limited to this.
- at least one of the expander and the second compressor may have a rotary configuration.
Abstract
Description
ここで、密度比は、上記膨張機構に流入する冷媒の密度(DE)と上記補助圧縮機構に流入する冷媒の密度(DC)との比、DE/DCをいう。
また、バイパス流路に流れる流量分も蒸発器を通過するため、蒸発器での冷媒の圧力損失が大きくなるという問題点もあった。
実施の形態1.
図1はこの発明の実施の形態1に係る冷凍サイクル装置を示す構成図である。
図において、この実施の形態に係る冷凍サイクル装置は、室外ユニット100と、室内ユニット200aとを備えている。
上記室外ユニット100は、低圧側の冷媒である低圧冷媒を中間圧の冷媒である中間圧冷媒に昇圧させる第1圧縮機1と、この第1圧縮機1と冷媒流路部を介して直列に接続された第2熱源側熱交換器3bと、この第2熱源側熱交換器3bと冷媒流路部を介して直列に接続され前記中間圧冷媒を高圧側の冷媒である高圧冷媒に昇圧させる第2圧縮機5bと、この第2圧縮機5bに冷媒流路部を介して直列に接続されているともに前記高圧冷媒が流れる第1熱源側熱交換器3aとを備えている。
第2圧縮機5bの吸入部及び吐出部には、迂回したバイパス流路部59の両端部がそれぞれ接続されている。バイパス流路部59には、バイパス弁53が取り付けられている。
第1熱源側熱交換器3aは、高圧冷媒の熱を放出する放熱器として作用し、第2熱源側熱交換器3bは、中間圧冷媒の熱を冷却する中間冷却器として作用をしている。第1熱源側熱交換器3a、第2熱源側熱交換器3bの外表面には、室外ユニット100に内蔵された送風機(図示せず)からの風が送られる。
膨張機5aは、冷媒流路部、液配管52を介して室内ユニット200aの負荷側熱交換器である室内熱交換器9aと接続されている。
なお、低圧側流路部64の先端部は、第2熱源側熱交換器3bと第1圧縮機1との間の冷媒流路部に接続してもよい。
この電子膨張弁62の開度調整により、高圧側流路部63に流れる高圧冷媒と、低圧側流路部64に流れる減圧冷媒との間での熱交換量を変化させ、高圧側流路部を通じて膨張機5aに流入する高圧冷媒の温度を調節し、高圧冷媒の密度を調整することで、膨張機5aの回収動力と第2圧縮機5bの必要動力とは釣り合うようになっている。
なお、室外ユニット100と室内ユニット200aとの間で循環する冷媒は、例えば臨界温度(約31℃)以上で超臨界状態となる二酸化炭素が用いられる。
膨張機5aは、膨張機用固定スクロール351と膨張機用揺動スクロール352とを備えている。膨張機5aの内部は、膨張機吸入管313及び膨張機吐出管315と連通している。第2圧縮機5bは、第2圧縮機用固定スクロール361と第2圧縮機用揺動スクロール362とを備えている。第2圧縮機5bの内部は、第2圧縮機吸入管312及び第2圧縮機吐出管314と連通している。
これらのスクロール351,352,361,362の中心部には、膨張機用軸受け部351b、第2圧縮機用軸受け部361bで支持された軸308が貫通している。軸308の両端部には、バランスウェイト309a,309bがそれぞれ取り付けられている。膨張機5aの揺動スクロール352の背面と第2圧縮機5bの揺動スクロール362の背面とは面接触している。その他、必要部品であるオルダムリング307、クランク部308b等が密閉容器310内に収納されている。密閉容器310の下部には、密閉容器310の下部に貯留した油を室内熱交換器9aと膨張機5aとの間の冷媒流路部に戻す油戻し管311が取り付けられている。
また、第2圧縮機5b側のスラスト荷重を減らすために第2圧縮機5b側を極端に歯高の高い渦巻とすることもできるが、強度的な問題が発生する。
従って、膨張機5a、第2圧縮機5bともにスクロール構造を有する膨張機ユニット5では、膨張圧縮容積比を2.3以下の範囲に設定することで、性能面だけでなく、構造面でも信頼性の高い膨張機ユニット5を得ることができる。
図1において、実線矢印は冷房運転ときの冷媒の流れ方向を示し、図2は、図1の冷媒回路中に示した記号A~Hにおける各冷媒状態をP-h線図上で示したもので、状態C,D,E,Fの冷媒は、高圧側の高圧冷媒であり、状態G,Hの冷媒は、低圧側の低圧冷媒である。また、高圧側と低圧側の間の状態A,Bの冷媒は、中間圧冷媒である。
必要な減圧機能は膨張機5aで実現し、室内熱交換器9aの出口部に予め設定された適切な過熱度(例えば、5~10℃)が得られるように、予膨張弁6が調節される。
このとき、第2圧縮機5bのバイパス流路部59に取り付けた逆止弁53は、圧力差の生じない起動時には開放状態となるが、膨張機5aが動作して第2圧縮機5bが駆動すると、第2圧縮機5bの冷媒ガスの入口側と出口側との高低圧力差により閉止される。第2圧縮機5bから吐出されたガス冷媒は、第1熱源側熱交換器3aで被加熱媒体である空気に放熱し(状態D)、引き続き高低圧熱交換器61に流入する。
高低圧熱交換器61では、高圧側流路部63を流れる高圧冷媒と、低圧側流路部64に取り付けられた電子膨張弁62で減圧された低圧側流路部64を流れる減圧冷媒との間での熱交換により、高圧側流路部63を流れる冷却された高圧冷媒(状態E)は、予膨張弁6へ流入する。予膨張弁6で膨張により膨張機5aの入口における密度が調節された高圧冷媒(状態F)は、膨張機5aで減圧され、冷媒流路部、液配管52を通過する(状態G)。その後、液冷媒は、室内熱交換器9aで空調対象空間の熱負荷を処理した後、ガス配管51に流入し、引き続きガス冷媒は、第1圧縮機1に流入し(状態H)、第1圧縮機1から高温、中間圧のガス冷媒(状態A)として吐出される。
この実施の形態では、膨張機5aの冷媒の入口側に設けた高低圧熱交換器61の熱交換量を低圧側流路部64に取り付けた電子膨張弁62で制御し、膨張機5aでの回収動力を、第2圧縮機5bでの必要動力と一致させる。
高低圧熱交換器61の熱交換量を小さくするためには、電子膨張弁62の開度を小さくし、低圧側の低圧側流路部64に流れる流量を低下させる。
一方、予め設定された上記密度比に対し、密度比が小さくなる運転状態では、高低圧熱交換器61での熱交換量を大きくし、膨張機5aに流入する冷媒の入口温度を低くする、即ち冷媒の密度を大きくする。高低圧熱交換器61の熱交換量を大きくするためには、電子膨張弁62の開度を大きくし、低圧側の低圧側流路部64に流れる流量を増加させる。
まず、冷凍サイクル装置が運転される環境条件の変化を把握し、外気温湿度及び室内温湿度の範囲を設定する(ステップS1)。
次に、膨張機5aの容積比を決定し(ステップS2)、与えられた環境条件と膨張機5aの容積比で運転が実現できるように、中間冷却器である第2熱源側熱交換器3bの仕様を決定し(ステップS3)、また高低圧熱交換器61の仕様を決定する(ステップS4)。このように設計された高低圧熱交換器61の熱交換量を電子膨張弁62の開度で可変することで(ステップS5)、膨張機5aの冷媒入口密度を所望の値に制御することができる。
また、空気条件、冷媒温度、第2圧縮機5bの回転数などの運転状態から推定するようにしてもよい。
また、第2圧縮機5bの冷媒入口圧力は、第1圧縮機1の冷媒出口から第2圧縮機5bの冷媒入口までの配管に圧力センサーを取り付けて検知すればよく、また空気条件、冷媒温度、第2圧縮機5bの回転数などの運転状態から推定するようにしてもよい。
なお、この実施の形態では冷房専用機で膨張機5aを利用する例を示したが、これに限るものではなく、給湯機のような暖房専用機にも膨張機5aを利用するようにしてもよい。この場合には、放熱器である第1熱源側熱交換器3aで、第2圧縮機5bから吐出された冷媒により水が加熱される。
図5は、この発明の実施の形態2に係る冷凍サイクル装置を示す構成図である。
この実施の形態では、室外ユニット100は、第1圧縮機1による冷房運転と暖房運転との切り換えを可能にする第1四方弁2、膨張機5aによる冷房動力回収運転と暖房動力回収運転との切り換えを可能にする第2四方弁4を内蔵している。
第1四方弁2は、第2圧縮機5bの高圧冷媒の吐出側の冷媒流路部に取り付けられている。第2四方弁4は、冷房運転のときに第1熱源側熱交換器3aからの高圧冷媒を高低圧熱交換器61に導く冷媒流路部に取り付けられている。
室外ユニット100は、ガス配管51及び液配管52を介して2台の室内ユニット200a、200bと接続されている。室外ユニット100内の冷媒流路には、第1熱源側熱交換器3a、第2熱源側熱交換器3bの両方でそれぞれ冷房運転及び暖房運転の両運転に活用できるように、開閉弁である電磁弁54,55,56,57,58が取り付けられている。
その他の構成は実施の形態1と同様であり、詳細な説明は省略する。
先ず、冷房運転時の動作について図5及び図6に基づいて説明する。
この冷房運転時には、図5の実線で示すように、第1四方弁2は、第1口2aと第2口2bとが連通し、第3口2cと第4口2dとが連通している。また、第2四方弁4は、第1口4aと第4口4dとが連通し、第2口4bと第3口4cとが連通している。このとき、電磁弁54,55,56は、閉止され、電磁弁57,58は、開放されている。
第1圧縮機1から吐出された高温高圧のガス冷媒(状態A)は、電磁弁57を通過し、第2熱源側熱交換器3bへ流入する。第2熱源側熱交換器3bである程度放熱して冷却され、電磁弁58に流入する。電磁弁58を通過したガス冷媒(状態B)は、膨張機5aで駆動される第2圧縮機5bに流入し、膨張機5aで回収された動力に釣合う分だけ圧縮される。
この暖房運転時には、図5の点線で示すように、第1四方弁2は、第1口2aと第4口2dとが連通し、第2口2bと第3口2cとが連通している。また、第2四方弁4は、第3口4cと第4口4dとが連通し、第1口4aと第2口4bとが連通している。このとき、電磁弁54,55,56は、開放されており、電磁弁57,58は、閉止されている。
第1圧縮機1から吐出された高温高圧のガス冷媒(状態A)は、開閉弁56を通過し(状態B)、第2圧縮機5bに流入する。膨張機5aで駆動される第2圧縮機5bに流入した冷媒は、膨張機5aで回収された動力に釣合う分だけ圧縮される。第2圧縮機5bから吐出された冷媒は、第1四方弁2の第1口2aから第4口2dを通って室内ユニット200a,200b内の室内熱交換器9a,9bに流入する。
図8は、この発明の実施の形態3に係る冷凍サイクル装置を示す構成図である。
この実施の形態では、電子膨張弁62が取り付けられた低圧側流路部64の先端部は、第1圧縮機1の吸入部に接続されており、高低圧熱交換器61から流出した減圧冷媒は、第1圧縮機1の吸入部に導かれ、第1圧縮機1に流入するようになっている。
その他の構成は実施の形態2の冷凍サイクル装置と同様であり、詳細な説明は省略する。
従って、膨張機5aの冷媒入口密度の変化幅を拡大することができ、広範囲な空気条件に合わせて密度比を変化させることができる。
Claims (8)
- 低圧側の冷媒である低圧冷媒を中間圧の冷媒である中間圧冷媒に昇圧させる第1圧縮機と、
この第1圧縮機と直列に接続され前記中間圧冷媒を高圧側の冷媒である高圧冷媒に昇圧させる第2圧縮機と、
この第2圧縮機に直列に接続され前記高圧冷媒が流れる第1熱源側熱交換器と、
この第1熱源側熱交換器に直列に接続されている高低圧熱交換器と、
この高低圧熱交換器に直列に接続され前記高圧冷媒を前記低圧冷媒に減圧させるとともにそのときの回収動力で前記第2圧縮機を駆動させる膨張機と、
この膨張機に直列に接続された負荷側熱交換器とを備え、
前記高低圧熱交換器では、前記膨張機での前記回収動力と前記第2圧縮機の必要動力とが釣り合うように、前記高圧冷媒と、高低圧熱交換器の高圧冷媒の入口部で分岐され減圧された減圧冷媒との間での熱交換量を変化させ、前記膨張機に流入する前記冷媒の密度を調節するようになっていることを特徴とする冷凍サイクル装置。 - 低圧側の冷媒である低圧冷媒を中間圧の冷媒である中間圧冷媒に昇圧させる第1圧縮機と、
この第1圧縮機と直列に接続され前記中間圧冷媒を高圧側の高圧冷媒に昇圧させる第2圧縮機と、
この第2圧縮機に直列に接続された第1熱源側熱交換器と、
この第1熱源側熱交換器に直列に接続された高低圧熱交換器と、
この高低圧熱交換器に直列に接続され前記高圧冷媒を低圧冷媒に減圧させるとともにそのときの回収動力で前記第2圧縮機を駆動させる膨張機と、
この膨張機に直列に接続された負荷側熱交換器と、
前記第2圧縮機の前記高圧冷媒の吐出側の冷媒流路部に取り付けられ、前記第2圧縮機からの前記高圧冷媒が前記第1熱源側熱交換器または前記負荷側熱交換器に流れるように作動する第1四方弁と、
前記高低圧熱交換器の前記高圧冷媒の流入側の冷媒流路部に取り付けられ、前記負荷側熱交換器からの前記高圧冷媒または前記第1熱源側熱交換器から前記高圧冷媒を高低圧熱交換器に流れるように作動する第2四方弁とを備え、
前記高低圧熱交換器では、前記膨張機での前記回収動力と前記第2圧縮機の必要動力とが釣り合うように、前記高圧冷媒と、高低圧熱交換器の高圧冷媒の入口部で分岐され減圧された減圧冷媒との間での熱交換量を変化させ、前記膨張機に流入する前記冷媒の密度を調節するようになっていることを特徴とする冷凍サイクル装置。 - 前記高低圧熱交換器から流出した前記減圧冷媒は、前記第1圧縮機と前記第2圧縮機との間の冷媒流路部に導かれ、第2圧縮機に流入するようになっていることを特徴とする請求項1または2に記載の冷凍サイクル装置。
- 前記高低圧熱交換器から流出した前記減圧冷媒は、前記第1圧縮機の吸入側の冷媒流路部に導かれ、第1圧縮機に流入するようになっていることを特徴とする請求項1または2に記載の冷凍サイクル装置。
- 前記第1圧縮機と前記第2圧縮機との間の冷媒流路部に、冷媒流路部に流れる冷媒と外気との間で熱交換する第2熱源側熱交換器が取り付けられていることを特徴とする請求項1~4の何れか1項に記載の冷凍サイクル装置。
- 前記膨張機の前記高圧冷媒の入口部に、予膨張弁が設けられていることを特徴とする請求項1~5の何れか1項に記載の冷凍サイクル装置。
- 前記膨張機及び前記第2圧縮機は、ともに軸を介して直結したスクロール型の一体構成であることを特徴とする請求項1~6の何れか1項に記載の冷凍サイクル装置。
- 前記冷媒は二酸化炭素であることを特徴とする請求項1~7の何れか1項に記載の冷凍サイクル装置。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN2009801199132A CN102047048B (zh) | 2008-06-05 | 2009-03-13 | 冷冻循环装置 |
US12/989,126 US8769983B2 (en) | 2008-06-05 | 2009-03-13 | Refrigeration cycle apparatus |
JP2010515795A JP4906963B2 (ja) | 2008-06-05 | 2009-03-13 | 冷凍サイクル装置 |
EP09758149.0A EP2312238B1 (en) | 2008-06-05 | 2009-03-13 | Refrigeration cycle apparatus |
HK11106317.0A HK1152373A1 (en) | 2008-06-05 | 2011-06-21 | Refrigeration cycle apparatus |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2008-148004 | 2008-06-05 | ||
JP2008148004 | 2008-06-05 |
Publications (1)
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WO2009147882A1 true WO2009147882A1 (ja) | 2009-12-10 |
Family
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Application Number | Title | Priority Date | Filing Date |
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PCT/JP2009/054874 WO2009147882A1 (ja) | 2008-06-05 | 2009-03-13 | 冷凍サイクル装置 |
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Country | Link |
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US (1) | US8769983B2 (ja) |
EP (1) | EP2312238B1 (ja) |
JP (1) | JP4906963B2 (ja) |
CN (1) | CN102047048B (ja) |
HK (1) | HK1152373A1 (ja) |
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2011139425A2 (en) | 2010-04-29 | 2011-11-10 | Carrier Corporation | Refrigerant vapor compression system with intercooler |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
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MX2013003730A (es) | 2010-09-29 | 2013-08-29 | Rbc Horizon Inc | Aparato de recuperacion de energia para un sistema de refrigeracion. |
JP5575191B2 (ja) * | 2012-08-06 | 2014-08-20 | 三菱電機株式会社 | 二元冷凍装置 |
US9537442B2 (en) | 2013-03-14 | 2017-01-03 | Regal Beloit America, Inc. | Methods and systems for controlling power to an electric motor |
EP2889558B1 (en) * | 2013-12-30 | 2019-05-08 | Rolls-Royce Corporation | Cooling system with expander and ejector |
US9562705B2 (en) | 2014-02-13 | 2017-02-07 | Regal Beloit America, Inc. | Energy recovery apparatus for use in a refrigeration system |
JP7193706B2 (ja) * | 2018-10-02 | 2022-12-21 | ダイキン工業株式会社 | 冷凍サイクル装置 |
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JPH1194379A (ja) * | 1997-09-22 | 1999-04-09 | Sanden Corp | 冷凍空調装置 |
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-
2009
- 2009-03-13 CN CN2009801199132A patent/CN102047048B/zh not_active Expired - Fee Related
- 2009-03-13 EP EP09758149.0A patent/EP2312238B1/en active Active
- 2009-03-13 WO PCT/JP2009/054874 patent/WO2009147882A1/ja active Application Filing
- 2009-03-13 JP JP2010515795A patent/JP4906963B2/ja active Active
- 2009-03-13 US US12/989,126 patent/US8769983B2/en not_active Expired - Fee Related
-
2011
- 2011-06-21 HK HK11106317.0A patent/HK1152373A1/xx not_active IP Right Cessation
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JPH1194379A (ja) * | 1997-09-22 | 1999-04-09 | Sanden Corp | 冷凍空調装置 |
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WO2011139425A2 (en) | 2010-04-29 | 2011-11-10 | Carrier Corporation | Refrigerant vapor compression system with intercooler |
WO2011139425A3 (en) * | 2010-04-29 | 2013-02-21 | Carrier Corporation | Refrigerant vapor compression system with intercooler |
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US9989279B2 (en) | 2010-04-29 | 2018-06-05 | Carrier Corporation | Refrigerant vapor compression system with intercooler |
Also Published As
Publication number | Publication date |
---|---|
US20110036118A1 (en) | 2011-02-17 |
EP2312238A4 (en) | 2017-04-19 |
CN102047048A (zh) | 2011-05-04 |
CN102047048B (zh) | 2012-11-28 |
US8769983B2 (en) | 2014-07-08 |
HK1152373A1 (en) | 2012-02-24 |
JPWO2009147882A1 (ja) | 2011-10-27 |
JP4906963B2 (ja) | 2012-03-28 |
EP2312238B1 (en) | 2018-09-12 |
EP2312238A1 (en) | 2011-04-20 |
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