US20100242529A1 - Refrigeration apparatus - Google Patents
Refrigeration apparatus Download PDFInfo
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- US20100242529A1 US20100242529A1 US12/744,249 US74424908A US2010242529A1 US 20100242529 A1 US20100242529 A1 US 20100242529A1 US 74424908 A US74424908 A US 74424908A US 2010242529 A1 US2010242529 A1 US 2010242529A1
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- refrigerant
- compression
- tube
- heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- 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
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
- F25B31/004—Lubrication oil recirculating arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- 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
- 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
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
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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
- F25B2400/23—Separators
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressor (AREA)
Abstract
A refrigeration apparatus uses a refrigerant that operates in a supercritical range, and includes a compression mechanism, a heat source-side heat exchanger, an expansion mechanism, a usage-side heat exchanger, an intercooler and an intermediate oil separation mechanism. The compression mechanism has a plurality of compression elements, and is configured and arranged so that refrigerant discharged from a first-stage compression element is sequentially compressed by a second-stage compression element. The intercooler is configured and arranged to cool refrigerant flowing through an intermediate refrigerant tube that draws refrigerant discharged from the first-stage compression element into the second-stage compression element. The intermediate oil separation mechanism is configured and arranged to separate a refrigeration oil from the refrigerant discharged from the first-stage compression element. The intermediate oil separation mechanism is arranged at a section of the intermediate refrigerant tube between the first-stage compression element and an inlet of the intercooler.
Description
- The present invention relates to a refrigeration apparatus, and particularly relates to a refrigeration apparatus which performs a multistage compression refrigeration cycle by using a refrigerant that operates in a supercritical range.
- As one conventional example of a refrigeration apparatus which performs a multistage compression refrigeration cycle by using a refrigerant that operates in a supercritical range,
Patent Document 1 discloses an air-conditioning apparatus performs a two-stage compression refrigeration cycle by using carbon dioxide as a refrigerant. This air-conditioning apparatus has primarily a compressor having two compression elements connected in series, an outdoor heat exchanger as a heat source-side heat exchanger, an expansion valve, and an indoor heat exchanger. - <
Patent Document 1> - Japanese Laid-open Patent Application No. 2007-232263
- A refrigeration apparatus according to a first aspect of the present invention is a refrigeration apparatus which a refrigerant that operates in a supercritical range is used, comprising a compression mechanism, a heat source-side heat exchanger, an expansion mechanism for depressurizing the refrigerant, a usage-side heat exchanger, an intercooler, and an intermediate oil separation mechanism. The compression mechanism has a plurality of compression elements and is configured so that the refrigerant discharged from the first-stage compression element, which is one of a plurality of compression elements, is sequentially compressed by the second-stage compression element. The term “compression mechanism” herein means a compressor in which a plurality of compression elements are integrally incorporated, or a configuration including a compressor in which a single compression element is incorporated and/or a plurality of connected compressors in which a plurality of compression elements are incorporated in each. The phrase “the refrigerant discharged from a first-stage compression element, which is one of the plurality of compression elements, is sequentially compressed by a second-stage compression element” does not mean merely that two compression elements connected in series are included, namely, the “first-stage compression element” and the “second-stage compression element;” but means that a plurality of compression elements are connected in series and the relationship between the compression elements is the same as the relationship between the aforementioned “first-stage compression element” and “second-stage compression element.” The intercooler is provided to an intermediate refrigerant tube for drawing refrigerant discharged from the first-stage compression element into the second-stage compression element, and functions as a cooler of the refrigerant discharged from the first-stage compression element and drawn into the second-stage compression element. The intermediate oil separation mechanism is provided to a section of the intermediate refrigerant tube between the first-stage compression element and an inlet of the intercooler, and is a mechanism for separating from the refrigerant a refrigeration oil that accompanies the refrigerant discharged from the first-stage compression element and for returning the refrigeration oil to the intake side of the compression mechanism.
- In cases in which a heat exchanger that uses air as a heat source is used as the outdoor heat exchanger in a conventional air-conditioning apparatus, the critical temperature (about 31° C.) of carbon dioxide used as the refrigerant is about the same as the temperature of water or air as the cooling source of an outdoor heat exchanger or indoor heat exchanger functioning as a cooler of the refrigerant, which is low compared to R22, R410A, and other refrigerants, and the apparatus therefore operates in a state in which the high pressure of the refrigeration cycle is higher than the critical pressure of the refrigerant so that the refrigerant can be cooled by the air in the outdoor heat exchanger during an air-cooling operation as the cooling operation. As a result, since the refrigerant discharged from the second-stage compression element of the compressor has a high temperature, there is a large difference in temperature between the refrigerant and the air as a heat source in the outdoor heat exchanger functioning as a refrigerant cooler, and the outdoor heat exchanger has much heat radiation loss, which poses a problem in making it difficult to achieve a high operating efficiency.
- As a countermeasure to this problem, in this refrigeration apparatus, the intercooler which functions as a cooler of the refrigerant discharged from the first-stage compression element and drawn into the second-stage compression element is provided to the intermediate refrigerant tube for drawing refrigerant discharged from the first-stage compression element into the second-stage compression element, thereby lowering the temperature of the refrigerant drawn into the second-stage compression element. As a result, the temperature of the refrigerant discharged from the second-stage compression element of the compressor is reduced, and heat radiation loss in the outdoor heat exchanger is reduced.
- Since the refrigeration oil in the compressor herein accompanies the refrigerant discharged from the first-stage compression element of the compressor, the refrigeration oil in the compressor is moved out of the compressor by the intermediate refrigerant tube. There is a danger of a shortage of oil to the compressor because merely providing an intercooler as described above causes refrigeration oil to accumulate in the intercooler and to cease returning to the compressor.
- However, in this refrigeration apparatus, since the intermediate oil separation mechanism is provided and the refrigeration oil accompanying the refrigerant discharged from the first-stage compression element can be suppressed from flowing into the intercooler, the accumulation of refrigeration oil in the intercooler can be prevented, and oil shortages to the compression mechanism can be prevented. It is also possible to prevent loss of heat transfer performance and increases in pressure drop in the intercooler due to accumulation of refrigeration oil in the intercooler, and the performance of the refrigeration apparatus can be improved.
- Particularly in cases in which the compression mechanism includes a high-pressure dome-type compressor in which a plurality of compression elements connected in series are housed within the same casing, since the refrigerant discharged from the second-stage compression element is discharged out of the casing after being discharged into the space in the casing where refrigeration oil accumulates, there is not a large amount of refrigeration oil accompanying this refrigerant. Meanwhile, since the refrigerant discharged from the first-stage compression element is discharged directly out of the casing, there is a large amount of refrigeration oil accompanying this refrigerant and there is a high danger that a large amount of refrigeration oil will accumulate in the intercooler. Therefore, it is extremely beneficial to provide the intermediate oil separation mechanism according to the present invention.
- A refrigeration apparatus according to a second aspect of the present invention is the refrigeration apparatus according to the first aspect of the present invention, wherein the intermediate oil separation mechanism has an intermediate oil separator for separating from the refrigerant the refrigeration oil that accompanies the refrigerant discharged from the first-stage compression element, and an intermediate oil return tube for returning the refrigeration oil separated from the refrigerant to the compression mechanism, the intermediate oil return tube being connected to the intermediate oil separator.
- In this refrigeration apparatus, since providing the intermediate oil separator in the vicinity of the first-stage compression element makes it possible to separate refrigeration oil from the refrigerant in the vicinity of the first-stage compression element, the accumulation of refrigeration oil can be prevented not only in the intercooler but in the intermediate refrigerant tube as well.
- The refrigeration apparatus according to a third aspect of the present invention is the refrigeration apparatus according to the first aspect of the present invention, wherein the intermediate oil separation mechanism has a header provided to the inlet of the intercooler, and an intermediate oil return tube for connecting a lower end of the header with the compression mechanism.
- In this refrigeration apparatus, the increase in the number of components can be minimized because the header provided to the inlet of the intercooler functions as an oil separator.
- A refrigeration apparatus according to a fourth aspect of the present invention is the refrigeration apparatus according to any of the first through third aspects of the present invention, wherein the refrigerant that operates in the supercritical range is carbon dioxide.
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FIG. 1 is a schematic structural diagram of an air-conditioning apparatus as an embodiment of the refrigeration apparatus according to the present invention. -
FIG. 2 is a pressure-enthalpy graph representing the refrigeration cycle during the air-cooling operation. -
FIG. 3 is a temperature-entropy graph representing the refrigeration cycle during the air-cooling operation. -
FIG. 4 is a schematic structural drawing of an intercooler and an intermediate oil separation mechanism in an air-conditioning apparatus according toModification 1. -
FIG. 5 is a schematic structural drawing of an air-conditioning apparatus according toModification 2. -
FIG. 6 is a schematic structural drawing of an air-conditioning apparatus according toModification 3. -
FIG. 7 is a schematic structural drawing of an air-conditioning apparatus according toModification 3. -
FIG. 8 is a schematic structural drawing of an air-conditioning apparatus according toModification 3. -
FIG. 9 is a pressure-enthalpy graph representing the refrigeration cycle during the air-cooling operation in the air-conditioning apparatus according toModification 3. -
FIG. 10 is a temperature-entropy graph representing the refrigeration cycle during the air-cooling operation in the air-conditioning apparatus according toModification 3. -
FIG. 11 is a schematic structural drawing of an air-conditioning apparatus according toModification 4. -
FIG. 12 is a schematic structural drawing of an air-conditioning apparatus according toModification 5. -
FIG. 13 is a schematic structural drawing of an air-conditioning apparatus according toModification 5. -
FIG. 14 is a schematic structural drawing of an air-conditioning apparatus according toModification 6. -
FIG. 15 is a pressure-enthalpy graph representing the refrigeration cycle during the air-cooling operation in the air-conditioning apparatus according toModification 6. -
FIG. 16 is a temperature-entropy graph representing the refrigeration cycle during the air-cooling operation in the air-conditioning apparatus according toModification 6. -
FIG. 17 is a pressure-enthalpy graph representing the refrigeration cycle during the air-warming operation in the air-conditioning apparatus according toModification 6. -
FIG. 18 is a temperature-entropy graph representing the refrigeration cycle during the air-warming operation in the air-conditioning apparatus according toModification 6. -
FIG. 19 is a schematic structural drawing of an air-conditioning apparatus according toModification 6. -
FIG. 20 is a schematic structural drawing of an air-conditioning apparatus according toModification 7. -
FIG. 21 is a schematic structural drawing of an air-conditioning apparatus according toModification 7. -
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- 1 Air-conditioning apparatus (refrigeration apparatus)
- 2, 102, 202 Compression mechanisms
- 4 Heat source-side heat exchanger
- 5 Expansion mechanism
- 6 Usage-side heat exchanger
- 7 Intercooler
- 8 Intermediate refrigerant tube
- 16 Intermediate oil separation mechanism
- 16 a Intermediate oil separator
- 16 b Intermediate oil return tube
- 16 d Header
- Embodiments of the refrigeration apparatus according to the present invention are described hereinbelow with reference to the drawings.
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FIG. 1 is a schematic structural diagram of an air-conditioning apparatus 1 as an embodiment of the refrigeration apparatus according to the present invention. The air-conditioning apparatus 1 has arefrigerant circuit 10 configured so as to be capable of an air-cooling operation, and the apparatus performs a two-stage compression refrigeration cycle by using a refrigerant (carbon dioxide in this case) for operating in a supercritical range. - The
refrigerant circuit 10 of the air-conditioning apparatus 1 has primarily acompression mechanism 2, a heat source-side heat exchanger 4, anexpansion mechanism 5, a usage-side heat exchanger 6, and anintercooler 7. - In the present embodiment, the
compression mechanism 2 is configured from acompressor 21 which uses two compression elements to subject a refrigerant to two-stage compression. Thecompressor 21 has a hermetic structure in which acompressor drive motor 21 b, adrive shaft 21 c, andcompression elements casing 21 a. Thecompressor drive motor 21 b is linked to thedrive shaft 21 c. Thedrive shaft 21 c is linked to the twocompression elements compressor 21 has a so-called single-shaft two-stage compression structure in which the twocompression elements single drive shaft 21 c and the twocompression elements compressor drive motor 21 b. In the present embodiment, thecompression elements compressor 21 is configured so as to admit refrigerant through anintake tube 2 a, to discharge this refrigerant to an intermediaterefrigerant tube 8 after the refrigerant has been compressed by thecompression element 2 c, to admit the refrigerant discharged to the intermediaterefrigerant tube 8 into thecompression element 2 d, and to discharge the refrigerant to adischarge tube 2 b after the refrigerant has been further compressed. The intermediaterefrigerant tube 8 is a refrigerant tube for taking refrigerant into thecompression element 2 d connected to the second-stage side of thecompression element 2 c after the refrigerant has been discharged from thecompression element 2 c connected to the first-stage side of thecompression element 2 c. - The
discharge tube 2 b is a refrigerant tube for feeding refrigerant discharged from thecompression mechanism 2 to the heat source-side heat exchanger 4, and thedischarge tube 2 b is provided with anoil separation mechanism 41 and anon-return mechanism 42. Theoil separation mechanism 41 is a mechanism for separating refrigerator oil accompanying the refrigerant from the refrigerant discharged from thecompression mechanism 2 and returning the oil to the intake side of thecompression mechanism 2, and theoil separation mechanism 41 has primarily anoil separator 41 a for separating refrigerator oil accompanying the refrigerant from the refrigerant discharged from thecompression mechanism 2, and anoil return tube 41 b connected to theoil separator 41 a for returning the refrigerator oil separated from the refrigerant to theintake tube 2 a of thecompression mechanism 2. Theoil return tube 41 b is provided with adecompression mechanism 41 c for depressurizing the refrigerator oil flowing through theoil return tube 41 b. A capillary tube is used for thedecompression mechanism 41 c in the present embodiment. Thenon-return mechanism 42 is a mechanism for allowing the flow of refrigerant from the discharge side of thecompression mechanism 2 to theswitching mechanism 3 and for blocking the flow of refrigerant from theswitching mechanism 3 to the discharge side of thecompression mechanism 2, and a non-return valve is used in the present embodiment. - Thus, in the present embodiment, the
compression mechanism 2 has twocompression elements compression elements - The heat source-
side heat exchanger 4 is a heat exchanger that functions as a refrigerant cooler. One end of the heat source-side heat exchanger 4 is connected to thecompression mechanism 2, and the other end is connected to theexpansion mechanism 5. Though not shown in the drawings, the heat source-side heat exchanger 4 is supplied with water or air as a cooling source for conducting heat exchange with the refrigerant flowing through the heat source-side heat exchanger 4. - The
expansion mechanism 5 is a mechanism for depressurizing the refrigerant, and an electric expansion valve is used in the present embodiment. One end of theexpansion mechanism 5 is connected to the heat source-side heat exchanger 4, and the other end is connected to the usage-side heat exchanger 6. In the present embodiment, theexpansion mechanism 5 depressurizes the high-pressure refrigerant cooled in the heat source-side heat exchanger 4 before feeding the refrigerant to the usage-side heat exchanger 6. - The usage-
side heat exchanger 6 is a heat exchanger that functions as a heater of refrigerant. One end of the usage-side heat exchanger 6 is connected to theexpansion mechanism 5, and the other end is connected to thecompression mechanism 2. Though not shown in the drawings, the usage-side heat exchanger 6 is supplied with water or air as a heat source for conducting heat exchange with the refrigerant flowing through the usage-side heat exchanger 6. - The
intercooler 7 is provided to the intermediaterefrigerant tube 8, and is a heat exchanger which functions as a cooler of refrigerant discharged from thecompression element 2 c on the first-stage side and drawn into thecompression element 2 d. Though not illustrated herein, theintercooler 7 is supplied with water or air as a cooling source for conducting heat exchange with the refrigerant flowing through theintercooler 7. Thus, it is acceptable to say that theintercooler 7 is a cooler that uses the external heat source, meaning that the intercooler does not use the refrigerant that circulates through therefrigerant circuit 10. - An intermediate
oil separation mechanism 16 is provided in a section of the intermediaterefrigerant tube 8 between the first-stage compression element 2 c and the inlet of theintercooler 7. The intermediateoil separation mechanism 16 is a mechanism for separating from the refrigerant the refrigeration oil that accompanies the refrigerant discharged from the first-stage compression element 2 c and for returning the refrigeration oil to thecompression mechanism 2. The intermediateoil separation mechanism 16 has primarily anintermediate oil separator 16 a for separating from the refrigerant the refrigeration oil that accompanies the refrigerant discharged from the first-stage compression element 2 c, and an intermediateoil return tube 16 b for returning the refrigeration oil separated from the refrigerant to thecompression mechanism 2, the intermediate oil return tube being connected to theintermediate oil separator 16 a. In the present embodiment, the intermediateoil return tube 16 b is connected between an oil outlet of theintermediate oil separator 16 a and the intake side of the compression mechanism 2 (theintake tube 2 a in this case), and is provided with adepressurizing mechanism 16 c for depressurizing the refrigeration oil flowing through the intermediateoil return tube 16 b. A capillary tube is used as thedepressurizing mechanism 16 c in the present embodiment. - Furthermore, though not illustrated herein, the air-
conditioning apparatus 1 has a controller for controlling the actions of thecompression mechanism 2, theexpansion mechanism 5, and the other components constituting the air-conditioning apparatus 1. - Next, the action of the air-
conditioning apparatus 1 of the present embodiment will be described usingFIGS. 1 through 3 .FIG. 2 is a pressure-enthalpy graph representing the refrigeration cycle during the air-cooling operation, andFIG. 3 is a temperature-entropy graph representing the refrigeration cycle during the air-cooling operation. Operation controls during the following air-cooling operation are performed by the aforementioned controller (not shown). In the following description, the term “high pressure” means a high pressure in the refrigeration cycle (specifically, the pressure at points D, D′, and E inFIGS. 2 and 3 ), the term “low pressure” means a low pressure in the refrigeration cycle (specifically, the pressure at points A and F inFIGS. 2 and 3 ), and the term “intermediate pressure” means an intermediate pressure in the refrigeration cycle (specifically, the pressure at points B1 and C1 inFIGS. 2 and 3 ). - When the
compression mechanism 2 is driven while therefrigerant circuit 310 is in this state, low-pressure refrigerant (refer to point A inFIGS. 1 through 3 ) is drawn into thecompression mechanism 2 through theintake tube 2 a, and after the refrigerant is first compressed to an intermediate pressure by thecompression element 2 c, the refrigerant is discharged to the intermediate refrigerant tube 8 (refer to point B1 inFIGS. 1 through 3 ). As in the embodiment described above, the intermediate-pressure discharged from the first-stage compression element 2 c flows into theintermediate oil separator 16 a constituting the intermediateoil separation mechanism 16, and after the accompanying refrigeration oil is separated, the refrigerant is fed to theintercooler 7. The refrigeration oil separated from the intermediate-pressure refrigerant in theintermediate oil separator 16 a flows into the intermediateoil return tube 16 b constituting the intermediateoil separation mechanism 16, and after being depressurized by thedepressurizing mechanism 16 c provided to the intermediateoil return tube 16 b, the refrigerant is returned to the compression mechanism 2 (theintake tube 2 a in this case) and led back into thecompression mechanism 2. After the refrigeration oil has been separated in the intermediateoil separation mechanism 16, the intermediate-pressure refrigerant is then cooled in theintercooler 7 by undergoing heat exchange with water or air as a cooling source (refer to point C1 inFIGS. 1 through 3 ). The refrigerant cooled in theintercooler 7 is then led to and further compressed in thecompression element 2 d connected to the second-stage side of thecompression element 2 c, and the refrigerant is then discharged from thecompression mechanism 2 to thedischarge tube 2 b (refer to point D inFIGS. 1 through 3 ). The high-pressure refrigerant discharged from thecompression mechanism 2 is compressed to a pressure exceeding a critical pressure (i.e., the critical pressure Pcp at the critical point CP shown inFIG. 2 ) by the two-stage compression action of thecompression elements compression mechanism 2 flows into theoil separator 41 a constituting theoil separation mechanism 41, and the accompanying refrigeration oil is separated. The refrigeration oil separated from the high-pressure refrigerant in theoil separator 41 a flows into theoil return tube 41 b constituting theoil separation mechanism 41 wherein it is depressurized by thedepressurization mechanism 41 c provided to theoil return tube 41 b, and the oil is then returned to theintake tube 2 a of thecompression mechanism 2 and led back into thecompression mechanism 2. Next, having been separated from the refrigeration oil in theoil separation mechanism 41, the high-pressure refrigerant is passed through thenon-return mechanism 42 and is fed to the heat source-side heat exchanger 4 functioning as a refrigerant cooler. The high-pressure refrigerant fed to the heat source-side heat exchanger 4 is cooled in the heat source-side heat exchanger 4 by heat exchange with water or air as a cooling source (refer to point E inFIGS. 1 through 3 ). The high-pressure refrigerant cooled in the heat source-side heat exchanger 4 is then depressurized by theexpansion mechanism 5 to become a low-pressure gas-liquid two-phase refrigerant, which is fed to the usage-side heat exchanger 6 functioning as a refrigerant heater (refer to point F inFIGS. 1 through 3 ). The low-pressure gas-liquid two-phase refrigerant fed to the usage-side heat exchanger 6 is heated by heat exchange with water or air as a heating source, and the refrigerant evaporates as a result (refer to point A inFIGS. 1 through 3 ). The low-pressure refrigerant heated in the usage-side heat exchanger 6 is then led back into thecompression mechanism 2. In this manner the air-cooling operation is performed. - Thus, in the air-
conditioning apparatus 1, theintercooler 7 is provided to the intermediaterefrigerant tube 8 for letting refrigerant discharged from thecompression element 2 c into thecompression element 2 d. Therefore, the refrigerant drawn into thecompression element 2 d on the second-stage side of thecompression element 2 c decreases in temperature (refer to points B1 and C1 inFIG. 3 ) and the refrigerant discharged from thecompression element 2 d also decreases in temperature (refer to points D and D′ inFIG. 3 ), in comparison with cases in which nointercooler 7 is provided (in this case, the refrigeration cycle is performed in the sequence inFIGS. 2 and 3 : point A→point B1→point D′→point E→point F). Therefore, in the heat source-side heat exchanger 4 functioning as a cooler of high-pressure refrigerant in this air-conditioning apparatus 1, operating efficiency can be improved over cases in which nointercooler 7 is provided, because the temperature difference between the refrigerant and water or air as the cooling source can be reduced, and heat radiation loss can be reduced by an amount equivalent to the area enclosed by connecting points B1, D′, D, and C1 inFIG. 3 . - In the air-
conditioning apparatus 1, since the section of the intermediaterefrigerant tube 8 between the first-stage compression element 2 c and the inlet of theintercooler 7 is provided with the intermediateoil separation mechanism 16 for separating from the refrigerant the refrigeration oil that accompanies the refrigerant discharged from the first-stage compression element 2 c and returning the refrigerant to thecompression mechanism 2, the refrigeration oil that accompanies the refrigerant discharged from the first-stage compression element 2 c can be suppressed from flowing into theintercooler 7, the accumulation of refrigeration oil in theintercooler 7 can be prevented, and oil shortages to thecompression mechanism 2 can be prevented, in comparison with cases in which no intermediateoil separation mechanism 16 is provided. - In cases in which no intermediate
oil separation mechanism 16 is provided, since the heat transfer performance of theintercooler 7 decreases and the amount of heat exchanged in the intercooler 7 (i.e. the enthalpy difference between points B1 and C1 inFIG. 2 ) decreases due to the accumulation of refrigeration oil in theintercooler 7, it may not be possible to reduce the heat radiation loss in the heat source-side heat exchanger 4. The accumulation of refrigeration oil in theintercooler 7 may also cause greater pressure drop in theintercooler 7, a pressure drop (specifically, point C1 inFIG. 2 ) in the refrigerant drawn into the second-stage compression element 2 d, and an increase in power consumption in the second-stage compression element 2 d. However, since the intermediateoil separation mechanism 16 is provided, it is possible to prevent the loss of heat transfer performance and the increase in pressure drop in theintercooler 7 as caused by the accumulation of refrigeration oil in theintercooler 7, and the performance of the air-conditioning apparatus 1 can be improved. - Furthermore, since the intermediate
oil separation mechanism 16 in the present embodiment has theintermediate oil separator 16 a for separating from the refrigerant the refrigeration oil that accompanies the refrigerant discharged from the first-stage compression element 2 c, and the intermediateoil return tube 16 b connected to theintermediate oil separator 16 a for returning the refrigeration oil separated from the refrigerant to thecompression mechanism 2; providing theintermediate oil separator 16 a in the vicinity of the first-stage compression element 2 c makes it possible to separate the refrigeration oil from the refrigerant in the vicinity of the first-stage compression element 2 c, whereby the accumulation of refrigeration oil can be prevented not only in theintercooler 7 but in the intermediaterefrigerant tube 8 as well. - In any case where the
compressor 21 constituting thecompression mechanism 2 is a low-pressure dome-type compressor in which the refrigerant drawn into the first-stage compression element 2 c fills the space in thecasing 21 a where refrigeration oil accumulates, an intermediate-pressure dome-type compressor in which the refrigerant discharged from the first-stage compression element 2 c fills the space in thecasing 21 a where refrigeration oil accumulates, or a high-pressure dome-type compressor in which the refrigerant discharged from the second-stage compression element 2 d fills the space in thecasing 21 a where refrigeration oil accumulates; the effect of preventing oil shortages to thecompression mechanism 2 as well as other effects can be achieved by providing the intermediateoil separation mechanism 16. Particularly in cases in which a high-pressure dome-type compressor is used as thecompressor 21 constituting thecompression mechanism 2, the refrigerant discharged from the second-stage compression element 2 d is discharged out of thecasing 21 a after being first discharged into the space in thecasing 21 a where refrigeration oil accumulates and the amount of refrigeration oil accompanying this refrigerant is therefore not large, whereas since the refrigerant discharged from the first-stage compression element 2 c is discharged directly out of thecasing 21 a, a large amount of refrigeration oil accompanies this refrigerant and there is a danger of a large amount of refrigeration oil accumulating in theintercooler 7. It is therefore extremely beneficial to provide the intermediateoil separation mechanism 16. - In the embodiment described above, the intermediate
oil separation mechanism 16 is configured from theintermediate oil separator 16 a and the intermediateoil return tube 16 b, but the intermediateoil separation mechanism 16 may also be configured such that the intermediateoil return tube 16 b is connected to a lower end of aheader 16 d provided to the inlet of theintercooler 7, as shown inFIG. 4 . In the case that theintercooler 7 is structured having a plurality of heat transfer channels, theheader 16 d is a tube member located between the intermediaterefrigerant tube 8 and a branching tube for branching off to the heat transfer channels. Aside from being connected to the lower end of theheader 16 d rather than to the oil outlet of theintermediate oil separator 16 a, the intermediateoil return tube 16 b has the same configuration as the intermediateoil return tube 16 b in the embodiment described above. - In the configuration of
Modification 1, since theheader 16 d provided to the inlet of theintercooler 7 functions as an oil separator, the increase in the number of components can be minimized in comparison with the embodiment described above. - In the modifications described hereinafter, examples are described in which the intermediate
oil separation mechanism 16 has theintermediate oil separator 16 a and the intermediateoil return tube 16 b, but a configuration may also be used in which the intermediateoil return tube 16 b is connected to the lower end of theheader 16 d provided in the inlet of theintercooler 7, as is the case in the present modification. - In the above-described embodiment and modifications thereof, the
compression mechanism 2 was a two-stage compression-type compression mechanism 2 configured from asingle compressor 21 having a single-shaft two-stage compression structure, wherein twocompression elements compression mechanism 2 having a two-stage compression structure by connecting two compressors in series, each of which compressors having a single-stage compression structure in which one compression element is rotatably driven by one compressor drive motor. - For example, in the embodiment described above, the
compression mechanism 2 can be configured by connecting two compressors in series, one being acompressor 22 housing thecompression element 2 c and the other being acompressor 23 housing thecompression element 2 d as shown inFIG. 5 , and the configuration can have an intermediateoil separation mechanism 16 identical to that of the previous embodiment (i.e. an intermediateoil separation mechanism 16 having anintermediate oil separator 16 a and an intermediateoil return tube 16 b) provided to the section of the intermediaterefrigerant tube 8 between the first-stage compression element 2 c (i.e. the compressor 22) and the inlet of theintercooler 7. Thecompression mechanism 2 has acompressor 22 and acompressor 23. Thecompressor 22 has a hermetic structure in which a casing 22 a houses acompressor drive motor 22 b, adrive shaft 22 c, and acompression element 2 c. Thecompressor drive motor 22 b is coupled with thedrive shaft 22 c, and thedrive shaft 22 c is coupled with thecompression element 2 c. Thecompressor 23 has a hermetic structure in which acasing 23 a houses acompressor drive motor 23 b, adrive shaft 23 c, and acompression element 2 d. Thecompressor drive motor 23 b is coupled with thedrive shaft 23 c, and thedrive shaft 23 c is coupled with thecompression element 2 d. As in the above-described embodiment and modifications thereof, thecompression mechanism 2 is configured so as to admit refrigerant through anintake tube 2 a, discharge the drawn-in refrigerant to an intermediaterefrigerant tube 8 after the refrigerant has been compressed by thecompression element 2 c, and discharge the refrigerant discharged to adischarge tube 2 b after the refrigerant has been drawn into thecompression element 2 d and further compressed. - Since it is possible in the configuration of
Modification 2 as well to suppress the refrigeration oil accompanying the refrigerant discharged from the first-stage compression element 2 c housed in thecompressor 22 from flowing into theintercooler 7, the accumulation of refrigeration oil in theintercooler 7 can be prevented, and oil shortages to thecompression mechanism 2 can be prevented. It is also possible to prevent loss of heat transfer performance and the increase of pressure drop in theintercooler 7 caused by the accumulation of refrigeration oil in theintercooler 7, and the performance of the air-conditioning apparatus 1 can be improved. - In the above-described embodiment and the modifications thereof, the two-stage compression-
type compression mechanism 2 was used in which refrigerant discharged from the first-stage compression element of twocompression elements type compression mechanism 102 in which refrigerant discharged from the first-stage compression element of three compression elements is sequentially compressed by the second-stage compression elements. - For example, in the embodiment described above, the
compression mechanism 102 can be configured by connecting two compressors in series, one being acompressor 24 housing acompression element 102 c and the other being acompressor 25housing compression elements FIG. 6 , wherein an intermediateoil separation mechanism 16 identical to that of the previous embodiment (i.e. the intermediateoil separation mechanism 16 having theintermediate oil separator 16 a and the intermediateoil return tube 16 b) is provided in the section of an intermediate refrigerant tube 8 (the one connecting thecompression element 102 c and thecompression element 102 d) between the first-stage compression element 102 c and the inlet of theintercooler 7, and another intermediateoil separation mechanism 16 is provided in the section of another intermediate refrigerant tube 8 (the one connecting thecompression element 102 d and thecompression element 102 e) between the first-stage compression element 102 d and the inlet of theintercooler 7. Thecompression mechanism 102 herein is configured by establishing a serial connection between thecompressor 24 which compresses refrigerant in one stage with a single compression element, and thecompressor 25 which compresses refrigerant in two stages with two compression elements. Thecompressor 24 has a hermetic structure in which acasing 24 a houses acompressor drive motor 24 b, adrive shaft 24 c, and thecompression element 102 c, similar to thecompressors Modification 3 described above. Thecompressor drive motor 24 b is coupled with thedrive shaft 24 c, and thedrive shaft 24 c is coupled with thecompression element 102 c. Thecompressor 25 also has a hermetic structure in which acasing 25 a houses acompressor drive motor 25 b, adrive shaft 25 c, and thecompression elements compressor 21 having a two-stage compression structure in the embodiment described above. Thecompressor drive motor 25 b is coupled with thedrive shaft 25 c, and thedrive shaft 25 c is coupled with the twocompression elements compressor 24 is configured so that refrigerant is drawn in through anintake tube 102 a, compressed by thecompression element 102 c, and then discharged to an intermediaterefrigerant tube 8 for taking refrigerant into thecompression element 102 d connected to the second-stage side of thecompression element 102 c. Thecompressor 25 is configured so that refrigerant discharged to this intermediaterefrigerant tube 8 is drawn into thecompression element 102 d and further compressed, after which the refrigerant is discharged to the intermediaterefrigerant tube 8 for taking refrigerant into thecompression element 102 e connected to the second-stage side of thecompression element 102 d, the refrigerant discharged to this intermediaterefrigerant tube 8 is drawn into thecompression element 102 e and further compressed, and the refrigerant is then discharged to adischarge tube 102 b. - Instead of the configuration shown in
FIG. 6 (specifically, a configuration in which the single-stage compression-type compressor 24 and the two-stage compression-type compressor 25 are connected in series), another possible option is a configuration in which a two-stage compression-type compressor 26 and a single-stage compression-type compressor 27 are connected in series as shown inFIG. 7 . In this case, thecompressor 26 hascompression elements compressor 27 has acompression element 102 e, and a configuration is therefore obtained in which threecompression elements FIG. 6 . Since thecompressor 26 has the same configuration as thecompressor 21 in the previous embodiment and thecompressor 27 has the same configuration as thecompressors Modification 3 described above, the symbols indicating components other than thecompression elements numbers - Furthermore, instead of the configuration shown in
FIG. 6 (specifically, a configuration in which a single-stage compression-type compressor 24 and a two-stage compression-type compressor 25 are connected in series), another possible option is a configuration in which three single-stage compression-type compressors FIG. 8 . In this case, thecompressor 26 has acompression element 102 c, thecompressor 28 has acompression element 102 d, and thecompressor 27 has acompression element 102 e, and a configuration is therefore obtained in which threecompression elements FIGS. 6 and 7 . Since thecompressors compressors Modification 3 described above, the symbols indicating components other than thecompression elements numbers - Thus, in the present modification, the
compression mechanism 102 has threecompression elements compression elements refrigerant circuit 110 in the present modification is configured from acompression mechanism 102,intermediate refrigerant tubes 8,intercoolers 7, intermediateoil separation mechanisms 16, and other components. - Next, the action of the air-
conditioning apparatus 1 of the present modification will be described usingFIGS. 6 through 10 .FIG. 9 is a pressure-enthalpy graph representing the refrigeration cycle during the air-cooling operation inModification 3, andFIG. 10 is a temperature-entropy graph representing the refrigeration cycle during the air-cooling operation inModification 3. Operation control in the following air-cooling operation is performed by the aforementioned controller (not shown). In the following description, the term “high pressure” means a high pressure in the refrigeration cycle (specifically, the pressure at points D, D′, and E inFIGS. 9 and 10 ), the term “low pressure” means a low pressure in the refrigeration cycle (specifically, the pressure at points A and F inFIGS. 9 and 10 ), and the term “intermediate pressure” means an intermediate pressure in the refrigeration cycle (specifically, the pressure at points B1, B2, B2′, C1, C2, and C2′ inFIGS. 9 and 10 ). - When the
compression mechanism 102 is driven, low-pressure refrigerant (refer to point A inFIGS. 6 through 10 ) is drawn into thecompression mechanism 102 through theintake tube 102 a, and after being first compressed to an intermediate pressure by thecompression element 102 c, the refrigerant is discharged to the intermediaterefrigerant tube 8 for drawing refrigerant discharged from the first-stage compression element 102 c into the second-stage compression element 102 d (refer to point B1 inFIGS. 6 through 10 ). The intermediate-pressure refrigerant discharged from the first-stage compression element 102 c flows into theintermediate oil separator 16 a constituting the intermediateoil separation mechanism 16 provided to a section of the intermediaterefrigerant tube 8 between the first-stage compression element 102 c and an inlet of anintercooler 7, and after the accompanying refrigeration oil is separated, the refrigerant is fed to theintercooler 7. The refrigeration oil separated from the intermediate-pressure refrigerant in theintermediate oil separator 16 a flows into the intermediateoil return tube 16 b constituting the intermediateoil separation mechanism 16, and after being depressurized by adepressurizing mechanism 16 c provided to the intermediateoil return tube 16 b, the refrigeration oil is returned to the compression mechanism 102 (theintake tube 102 a in this case) and drawn back into thecompression mechanism 102. Next, the intermediate-pressure refrigerant separated from the refrigeration oil in the intermediateoil separation mechanism 16 is cooled in theintercooler 7 by heat exchange with water or air as a cooling source (refer to point C1 inFIGS. 6 through 10 ). The refrigerant cooled in theintercooler 7 is drawn into thecompression element 102 d connected to the second-stage side of thecompression element 102 c and further compressed to a higher intermediate pressure, and is then discharged to the intermediaterefrigerant tube 8 for drawing refrigerant discharged from the first-stage compression element 102 d into the second-stage compression element 102 e (refer to point B2 inFIGS. 6 through 10 ). The intermediate-pressure refrigerant discharged from the first-stage compression element 102 d flows into theintermediate oil separator 16 a constituting the intermediateoil separation mechanism 16 provided in the section of the intermediaterefrigerant tube 8 between the first-stage compression element 102 d and the inlet of theintercooler 7, and after the accompanying refrigeration oil is separated, the refrigerant is fed to theintercooler 7. The refrigeration oil separated from the intermediate-pressure refrigerant in theintermediate oil separator 16 a flows into the intermediateoil return tube 16 b constituting the intermediateoil separation mechanism 16, and after being depressurized by thedepressurizing mechanism 16 c provided to the intermediateoil return tube 16 b, the refrigeration oil is returned to theintake tube 102 a of thecompression mechanism 102 and drawn back into thecompression mechanism 102. Next, the intermediate-pressure refrigerant separated from the refrigeration oil in the intermediateoil separation mechanism 16 is cooled in theintercooler 7 by heat exchange with water or air as a cooling source (refer to point C2 inFIGS. 6 through 10 ). The refrigerant cooled in theintercooler 7 is drawn into thecompression element 102 e connected to the second-stage side of thecompression element 102 d and further compressed, and is then discharged from thecompression mechanism 102 to thedischarge tube 102 b (refer to point D inFIGS. 6 through 10 ). The high-pressure refrigerant discharged from thecompression mechanism 102 is herein compressed to a pressure exceeding a critical pressure (i.e. the critical pressure Pcp at the critical point CP shown inFIG. 9 ) by the three-stage compression action of thecompression elements compression mechanism 102 flows into theoil separator 41 a constituting theoil separation mechanism 41 and the accompanying refrigeration oil is separated. The refrigeration oil separated from the high-pressure refrigerant in theoil separator 41 a flows into theoil return tube 41 b constituting theoil separation mechanism 41 where it is depressurized by thedepressurizing mechanism 41 c provided to theoil return tube 41 b, after which the refrigeration oil is returned to the compression mechanism 102 (theintake tube 102 a in this case) and drawn back into thecompression mechanism 102. Next, having been separated from the refrigeration oil in theoil separation mechanism 41, the high-pressure refrigerant is passed through thenon-return mechanism 42 and fed to the heat source-side heat exchanger 4 functioning as a refrigerant cooler. The high-pressure refrigerant fed to the heat source-side heat exchanger 4 is cooled by heat exchange with water or air as a cooling source (refer to point E inFIGS. 6 through 10 ). The high-pressure refrigerant cooled in the heat source-side heat exchanger 4 is depressurized by theexpansion mechanism 5 to become a low-pressure gas-liquid two-phase refrigerant, which is fed to the usage-side heat exchanger 6 functioning as a refrigerant heater (refer to point F inFIGS. 6 through 10 ). The low-pressure gas-liquid two-phase refrigerant fed to the usage-side heat exchanger 6 is heated in the usage-side heat exchanger 6 by heat exchange with water or air as a heating source, and the refrigerant evaporates as a result (refer to point A inFIGS. 6 through 10 ). The low-pressure refrigerant heated in the usage-side heat exchanger 6 is drawn back into thecompression mechanism 102. In this manner the air-cooling operation is performed. - Thus, in the configuration of the present modification, since the
intercooler 7 is provided to the intermediaterefrigerant tube 8 for drawing refrigerant discharged from thecompression element 102 c into thecompression element 102 d and theintercooler 7 is also provided to the intermediaterefrigerant tube 8 for drawing refrigerant discharged from thecompression element 102 d into thecompression element 102 e, the temperature of the refrigerant drawn into thecompression element 102 d on the second-stage side of thecompression element 102 c and the temperature of the refrigerant drawn into thecompression element 102 e on the second-stage side of thecompression element 102 d are both reduced (refer to points B1, C1, B2, and C2 inFIG. 10 ), and the temperature of the refrigerant discharged from thecompression element 102 e is also reduced (refer to points D and D′ inFIG. 10 ), in comparison with cases in which nointercoolers 7 are provided (in this case, the refrigeration cycle is performed in the sequence inFIGS. 9 and 10 : point A→point B1→point B2′ (C2′)→point D′→point E→point F). Therefore, in the configuration of the present modification, it is possible to reduce the temperature difference between the refrigerant and the water or air as a cooling source in the heat source-side heat exchanger 4 functioning as a cooler of high-pressure refrigerant in comparison with cases in which nointercoolers 7 are provided, the heat radiation loss can be reduced in proportion to the area enclosed by points B1, B2′ (C2′), D′, D, C2, B2, and C1 inFIG. 10 , and operating efficiency can therefore be improved. Moreover, since this area is greater than the area in a two-stage compression refrigeration cycle such as those of the above-described embodiment and the modifications thereof, the operating efficiency can be further improved over the above-described embodiment and the modifications thereof. - In the configuration of the present modification, oil shortages to the
compression mechanism 102 can be prevented as in the above-described embodiment and the modifications thereof, because the intermediateoil separation mechanism 16 for separating from the refrigerant the refrigeration oil accompanying the refrigerant discharged from the first-stage compression element 102 c and returning the refrigeration oil to the intake side of thecompression mechanism 102 is provided to the section in the intermediaterefrigerant tube 8 between the first-stage compression element 102 c and the inlet of theintercooler 7, and another intermediateoil separation mechanism 16 for separating from the refrigerant the refrigeration oil accompanying the refrigerant discharged from the first-stage compression element 102 d and returning the refrigeration oil to the intake side of thecompression mechanism 102 is provided to the section of the other intermediaterefrigerant tube 8 between the first-stage compression element 102 d and the inlet of theintercooler 7. - In cases in which no intermediate
oil separation mechanisms 16 are provided, theintercoolers 7 suffer a loss of heat transfer performance and the amount of heat exchanged in the intercoolers 7 (i.e. the enthalpy difference between points B1 and C1 and the enthalpy difference between points B2 and C2 inFIG. 9 ) decreases due to the accumulation of refrigeration oil in theintercoolers 7. Therefore, it may no longer be possible to reduce heat radiation loss in the heat source-side heat exchanger 4, and the accumulation of refrigeration oil in theintercoolers 7 may cause greater pressure drop in theintercoolers 7, lower pressure in the refrigerant (i.e. points C1 and C2 inFIG. 9 ) drawn into the second-stage compression element 102 d andcompression element 102 e, and increased power consumption in the second-stage compression element 102 d andcompression element 102 e. However, since the intermediateoil separation mechanisms 16 are provided, the performance of the air-conditioning apparatus 1 can be improved as with the above-described embodiment and the modifications thereof. - In any case where the two-stage compression-type compressor 25 (see
FIG. 6 ) constituting thecompression mechanism 102 is a low-pressure dome-type compressor in which the refrigerant drawn into the first-stage compression element 102 d fills the space in thecasing 25 a where refrigeration oil accumulates, an intermediate-pressure dome-type compressor in which the refrigerant discharged from the first-stage compression element 102 d fills the space in thecasing 25 a where refrigeration oil accumulates, or a high-pressure dome-type compressor in which the refrigerant discharged from the second-stage compression element 102 e fills the space in thecasing 25 a where refrigeration oil accumulates; the effect of preventing oil shortages to thecompression mechanism 102 as well as other effects can be achieved by providing the intermediateoil separation mechanisms 16. Particularly in cases in which a high-pressure dome-type compressor is used as thecompressor 25 constituting thecompression mechanism 102, the refrigerant discharged from the second-stage compression element 102 e is discharged out of thecasing 25 a after being first discharged into the space in thecasing 25 a where refrigeration oil accumulates and the amount of refrigeration oil accompanying this refrigerant is therefore not large, whereas since the refrigerant discharged from the first-stage compression element 102 d is discharged directly out of thecasing 25 a, a large amount of refrigeration oil accompanies this refrigerant and there is a danger of a large amount of refrigeration oil accumulating in theintercooler 7. It is therefore extremely beneficial to provide the intermediateoil separation mechanism 16. As with thecompressor 25, it is also extremely beneficial to provide the intermediateoil separation mechanism 16 in cases in which a high-pressure dome-type compressor is used as the two-stage compression-type compressor 26 (seeFIG. 7 ) constituting thecompression mechanism 102. - Though not described in detail herein, another possible option instead of the three-stage compression-
type compression mechanism 102 is to use a compression mechanism having more stages than a three-stage compression system, such as a four-stage compression system, and the same effects as the present modification can be achieved in this case as well. - In the above-described embodiment and the modifications thereof, the configuration had the multistage compression-
type compression mechanism 2 orcompression mechanism 102 in which compression was performed sequentially by a plurality of compression elements, but another possible option for cases in which a high-capacity usage-side heat exchanger 6 is connected or a plurality of usage-side heat exchangers 6 are connected, for example, is to use a parallel multistage compression-type compression mechanism in which a plurality of multistage compression-type compression mechanisms 2 orcompression mechanisms 102 are connected in parallel. - For example, a
refrigerant circuit 210 can be used, which uses acompression mechanism 202 having a configuration wherein a parallel connection is established between a two-stage compression-typefirst compression mechanism 203 havingcompression elements second compression mechanism 204 havingcompression elements FIG. 11 . - In the present modification, the
first compression mechanism 203 is configured using acompressor 29 for subjecting the refrigerant to two-stage compression through twocompression elements intake branch tube 203 a which branches off from anintake header tube 202 a of thecompression mechanism 202, and also to a firstdischarge branch tube 203 b whose flow merges with adischarge header tube 202 b of thecompression mechanism 202. In the present modification, thesecond compression mechanism 204 is configured using acompressor 30 for subjecting the refrigerant to two-stage compression through twocompression elements intake branch tube 204 a which branches off from theintake header tube 202 a of thecompression mechanism 202, and also to a seconddischarge branch tube 204 b whose flow merges with thedischarge header tube 202 b of thecompression mechanism 202. Since thecompressors compressor 21 in the embodiment described above, symbols indicating components other than thecompression elements compressor 29 is configured so that refrigerant is drawn in through the firstintake branch tube 203 a, the drawn-in refrigerant is compressed by thecompression element 203 c and then discharged to a first inlet-sideintermediate branch tube 81 constituting the intermediaterefrigerant tube 8, the refrigerant discharged to the first inlet-sideintermediate branch tube 81 is drawn in into thecompression element 203 d via an intermediate header tube 82 and a first discharge-sideintermediate branch tube 83 constituting the intermediaterefrigerant tube 8, and the refrigerant is further compressed and then discharged to the firstdischarge branch tube 203 b. Thecompressor 30 is configured so that refrigerant is drawn in through the secondintake branch tube 204 a, the drawn-in refrigerant is compressed by thecompression element 204 c and then discharged to a second inlet-sideintermediate branch tube 84 constituting the intermediaterefrigerant tube 8, the refrigerant discharged to the second inlet-sideintermediate branch tube 84 is drawn in into thecompression element 204 d via the intermediate header tube 82 and a second outlet-sideintermediate branch tube 85 constituting the intermediaterefrigerant tube 8, and the refrigerant is further compressed and then discharged to the seconddischarge branch tube 204 b. In the present modification, the intermediaterefrigerant tube 8 is a refrigerant tube for admitting refrigerant discharged from thecompression elements compression elements compression elements compression elements refrigerant tube 8 primarily comprises the first inlet-sideintermediate branch tube 81 connected to the discharge side of the first-stage compression element 203 c of thefirst compression mechanism 203, the second inlet-sideintermediate branch tube 84 connected to the discharge side of the first-stage compression element 204 c of thesecond compression mechanism 204, the intermediate header tube 82 whose flow merges with both inlet-sideintermediate branch tubes intermediate branch tube 83 branching off from the intermediate header tube 82 and connected to the intake side of the second-stage compression element 203 d of thefirst compression mechanism 203, and the second outlet-sideintermediate branch tube 85 branching off from the intermediate header tube 82 and connected to the intake side of the second-stage compression element 204 d of thesecond compression mechanism 204. Thedischarge header tube 202 b is a refrigerant tube for feeding the refrigerant discharged from thecompression mechanism 202 to the heat source-side heat exchanger 4, and the firstdischarge branch tube 203 b connected to thedischarge header tube 202 b is provided with a firstoil separation mechanism 241 and a firstnon-return mechanism 242, while the seconddischarge branch tube 204 b connected to thedischarge header tube 202 b is provided with a secondoil separation mechanism 243 and a secondnon-return mechanism 244. The firstoil separation mechanism 241 is a mechanism for separating from the refrigerant the refrigeration oil accompanying the refrigerant discharged from thefirst compression mechanism 203 and returning the oil to the intake side of thecompression mechanism 202. The firstoil separation mechanism 241 primarily comprises afirst oil separator 241 a for separating from the refrigerant the refrigeration oil accompanying the refrigerant discharged from thefirst compression mechanism 203, and a firstoil return tube 241 b connected to thefirst oil separator 241 a for returning the refrigeration oil separated from the refrigerant to the intake side of thecompression mechanism 202. The secondoil separation mechanism 243 is a mechanism for separating from the refrigerant the refrigeration oil accompanying the refrigerant discharged from thesecond compression mechanism 204 and returning the oil to the intake side of thecompression mechanism 202. The secondoil separation mechanism 243 primarily comprises asecond oil separator 243 a for separating from the refrigerant the refrigeration oil accompanying the refrigerant discharged from thesecond compression mechanism 204, and a secondoil return tube 243 b connected to thesecond oil separator 243 a for returning the refrigeration oil separated from the refrigerant to the intake side of thecompression mechanism 202. In the present modification, the firstoil return tube 241 b is connected to the secondintake branch tube 204 a, and the secondoil return tube 243 b is connected to the firstintake branch tube 203 a. Therefore, even if there is a disparity between the amount of refrigeration oil accompanying the refrigerant discharged from thefirst compression mechanism 203 and the amount of refrigeration oil accompanying the refrigerant discharged from thesecond compression mechanism 204, which occurs as a result of a disparity between the amount of refrigeration oil retained in thefirst compression mechanism 203 and the amount of refrigeration oil retained in thesecond compression mechanism 204, more refrigeration oil returns to whichever of thecompression mechanisms first compression mechanism 203 and the amount of refrigeration oil retained in thesecond compression mechanism 204. In the present modification, the firstintake branch tube 203 a is configured so that the portion leading from the flow juncture with the secondoil return tube 243 b to the flow juncture with theintake header tube 202 a slopes downward toward the flow juncture with theintake header tube 202 a, while the secondintake branch tube 204 a is configured so that the portion leading from the flow juncture with the firstoil return tube 241 b to the flow juncture with theintake header tube 202 a slopes downward toward the flow juncture with theintake header tube 202 a. Therefore, even if either one of the two-stage compression-type compression mechanisms intake header tube 202 a, and there will be little likelihood of a shortage of oil supplied to the operating compression mechanism. Theoil return tubes mechanisms oil return tubes non-return mechanisms compression mechanisms side heat exchanger 4 and for blocking the flow of refrigerant from the heat source-side heat exchanger 4 to the discharge sides of thecompression mechanisms - Thus, in the present modification, the
compression mechanism 202 is configured by connecting two compression mechanisms in parallel; namely, thefirst compression mechanism 203 having twocompression elements compression elements second compression mechanism 204 having twocompression elements compression elements - In the present modification, the
intercooler 7 is provided to the intermediate header tube 82 constituting the intermediaterefrigerant tube 8, and theintercooler 7 is a heat exchanger for cooling the conjoined flow of the refrigerant discharged from the first-stage compression element 203 c of thefirst compression mechanism 203 and the refrigerant discharged from the first-stage compression element 204 c of thesecond compression mechanism 204. In other words, theintercooler 7 functions as a cooler shared by the twocompression mechanisms compression mechanism 202 when theintercooler 7 is provided to a parallel multistage compression-type compression mechanism 202 in which a plurality of multistage compression-type compression mechanisms - In the present modification, the intermediate
oil separation mechanism 16 is provided in the section between the inlet of theintercooler 7 and the flow juncture between the inlet-sideintermediate branch tubes refrigerant tube 8, and the intermediateoil separation mechanism 16 is provided to be shared by the twocompression mechanisms intercooler 7. In the present modification, the intermediateoil return tube 16 b connects the oil outlet of theintermediate oil separator 16 a with theintake header tube 202 a of thecompression mechanism 202. - The first inlet-side
intermediate branch tube 81 constituting the intermediaterefrigerant tube 8 is provided with anon-return mechanism 81 a for allowing the flow of refrigerant from the discharge side of the first-stage compression element 203 c of thefirst compression mechanism 203 toward the intermediate header tube 82 and for blocking the flow of refrigerant from the intermediate header tube 82 toward the discharge side of the first-stage compression element 203 c, while the second inlet-sideintermediate branch tube 84 constituting the intermediaterefrigerant tube 8 is provided with anon-return mechanism 84 a for allowing the flow of refrigerant from the discharge side of the first-stage compression element 204 c of thesecond compression mechanism 204 toward the intermediate header tube 82 and for blocking the flow of refrigerant from the intermediate header tube 82 toward the discharge side of the first-stage compression element 204 c. In the present modification, non-return valves are used as thenon-return mechanisms compression mechanisms refrigerant tube 8 and travels to the discharge side of the first-stage compression element of the stopped compression mechanism. Therefore, there are no instances in which refrigerant discharged from the first-stage compression element of the operating compression mechanism passes through the interior of the first-stage compression element of the stopped compression mechanism and exits out through the intake side of thecompression mechanism 202, which would cause the refrigeration oil of the stopped compression mechanism to flow out, and it is thus unlikely that there will be insufficient refrigeration oil for starting up the stopped compression mechanism. In the case that thecompression mechanisms second compression mechanism 204, and therefore in this case only thenon-return mechanism 84 a corresponding to thesecond compression mechanism 204 need be provided. - In cases of a compression mechanism which prioritizes operating the
first compression mechanism 203 as described above, since a shared intermediaterefrigerant tube 8 is provided for bothcompression mechanisms stage compression element 203 c corresponding to the operatingfirst compression mechanism 203 passes through the second outlet-sideintermediate branch tube 85 of the intermediaterefrigerant tube 8 and travels to the intake side of the second-stage compression element 204 d of the stoppedsecond compression mechanism 204, whereby there is a danger that refrigerant discharged from the first-stage compression element 203 c of the operatingfirst compression mechanism 203 will pass through the interior of the second-stage compression element 204 d of the stoppedsecond compression mechanism 204 and exit out through the discharge side of thecompression mechanism 202, causing the refrigeration oil of the stoppedsecond compression mechanism 204 to flow out, resulting in insufficient refrigeration oil for starting up the stoppedsecond compression mechanism 204. In view of this, an on/offvalve 85 a is provided to the second outlet-sideintermediate branch tube 85 in the present modification, and when thesecond compression mechanism 204 has stopped, the flow of refrigerant through the second outlet-sideintermediate branch tube 85 is blocked by the on/offvalve 85 a. The refrigerant discharged from the first-stage compression element 203 c of the operatingfirst compression mechanism 203 thereby no longer passes through the second outlet-sideintermediate branch tube 85 of the intermediaterefrigerant tube 8 and travels to the intake side of the second-stage compression element 204 d of the stoppedsecond compression mechanism 204; therefore, there are no longer any instances in which the refrigerant discharged from the first-stage compression element 203 c of the operatingfirst compression mechanism 203 passes through the interior of the second-stage compression element 204 d of the stoppedsecond compression mechanism 204 and exits out through the discharge side of thecompression mechanism 202 which causes the refrigeration oil of the stoppedsecond compression mechanism 204 to flow out, and it is thereby even more unlikely that there will be insufficient refrigeration oil for starting up the stoppedsecond compression mechanism 204. An electromagnetic valve is used as the on/offvalve 85 a in the present modification. - In the case of a compression mechanism which prioritizes operating the
first compression mechanism 203, thesecond compression mechanism 204 is started up in continuation from the starting up of thefirst compression mechanism 203, but at this time, since a shared intermediaterefrigerant tube 8 is provided for bothcompression mechanisms stage compression element 203 c of thesecond compression mechanism 204 and the pressure in the intake side of the second-stage compression element 203 d are greater than the pressure in the intake side of the first-stage compression element 203 c and the pressure in the discharge side of the second-stage compression element 203 d, and it is difficult to start up thesecond compression mechanism 204 in a stable manner. In view of this, in the present modification, there is provided astartup bypass tube 86 for connecting the discharge side of the first-stage compression element 204 c of thesecond compression mechanism 204 and the intake side of the second-stage compression element 204 d, and an on/offvalve 86 a is provided to thisstartup bypass tube 86. In cases in which thesecond compression mechanism 204 has stopped, the flow of refrigerant through thestartup bypass tube 86 is blocked by the on/offvalve 86 a and the flow of refrigerant through the second outlet-sideintermediate branch tube 85 is blocked by the on/offvalve 85 a. When thesecond compression mechanism 204 is started up, a state in which refrigerant is allowed to flow through thestartup bypass tube 86 can be restored via the on/offvalve 86 a, whereby the refrigerant discharged from the first-stage compression element 204 c of thesecond compression mechanism 204 is drawn into the second-stage compression element 204 d via thestartup bypass tube 86 without being mixed with the refrigerant discharged from the first-stage compression element 203 c of thefirst compression mechanism 203, a state of allowing refrigerant to flow through the second outlet-sideintermediate branch tube 85 can be restored via the on/offvalve 85 a at point in time when the operating state of thecompression mechanism 202 has been stabilized (e.g., a point in time when the intake pressure, discharge pressure, and intermediate pressure of thecompression mechanism 202 have been stabilized), the flow of refrigerant through thestartup bypass tube 86 can be blocked by the on/offvalve 86 a, and operation can transition to the normal air-cooling operation. In the present modification, one end of thestartup bypass tube 86 is connected between the on/offvalve 85 a of the second outlet-sideintermediate branch tube 85 and the intake side of the second-stage compression element 204 d of thesecond compression mechanism 204, while the other end is connected between the discharge side of the first-stage compression element 204 c of thesecond compression mechanism 204 and thenon-return mechanism 84 a of the second inlet-sideintermediate branch tube 84, and when thesecond compression mechanism 204 is started up, thestartup bypass tube 86 can be kept in a state of being substantially unaffected by the intermediate pressure portion of thefirst compression mechanism 203. An electromagnetic valve is used as the on/offvalve 86 a in the present modification. - The actions of the air-
conditioning apparatus 1 of the present modification during the air-cooling operation are essentially the same as the actions in the above-described embodiment (FIGS. 1 through 3 and the relevant descriptions), except for the points modified by the circuit configuration surrounding thecompression mechanism 202 are somewhat more complex due to thecompression mechanism 202 being provided instead of thecompression mechanism 2, and these actions are therefore not described herein. - The accumulation of refrigeration oil in the
intercooler 7 can be prevented and oil shortages to thecompression mechanism 202 can be prevented with this configuration ofModification 4 as well, because the refrigeration oil accompanying the refrigerant discharged from the first-stage compression element 203 c of thefirst compression mechanism 203 and the first-stage compression element 204 c of thesecond compression mechanism 204 can be suppressed from flowing into theintercooler 7. It is also possible to prevent the loss of heat transfer performance and the increase of pressure drop in theintercooler 7 caused by the accumulation of refrigeration oil in theintercooler 7, and the performance of the air-conditioning apparatus 1 can be improved. In the configuration of the present modification, although a parallel multistage compression-type compression mechanism 202 is used in which a plurality of multistage compression-type compression mechanisms compression mechanism 202 because the intermediateoil separation mechanism 16 is provided to be shared by the twocompression mechanisms oil return tube 16 b connects the oil outlet of theintermediate oil separator 16 a with theintake header tube 202 a of thecompression mechanism 202, refrigeration oil can be reliably returned to bothcompression mechanisms - Though not described in detail herein, other possible options instead of the two-stage compression-
type compression mechanisms compression mechanism 102 in Modification 3) or the like, or a parallel multistage compression-type compression mechanism in which three or more multistage compression-type compression mechanisms are connected in parallel. In this case, the same effects as those of the present modification can be achieved. - In
Modification 4 described above, the intermediateoil separation mechanism 16 was provided to be shared by the twocompression mechanisms FIG. 11 , but another possible option is to provide an intermediateoil separation mechanism 16 corresponding for each of thecompression mechanisms FIG. 12 . For example, for thefirst compression mechanism 203, an intermediateoil separation mechanism 16 can be provided in a first inlet-sideintermediate branch tube 81 connected to the discharge side of a first-stage compression element 203 c, and for thesecond compression mechanism 204, another intermediateoil separation mechanism 16 can be provided to a second inlet-sideintermediate branch tube 84 connected to the discharge side of a first-stage compression element 204 c. - The accumulation of refrigeration oil in the
intercooler 7 can be prevented and oil shortages to thecompression mechanism 202 can be prevented with this configuration ofModification 5 as well, because the refrigeration oil accompanying the refrigerant discharged from the first-stage compression element 203 c of thefirst compression mechanism 203 and the first-stage compression element 204 c of thesecond compression mechanism 204 can be suppressed from flowing into theintercooler 7. It is also possible to prevent the loss of heat transfer performance and the increase of pressure drop in theintercooler 7 caused by the accumulation of refrigeration oil in theintercooler 7, and the performance of the air-conditioning apparatus 1 can be improved. In the configuration of the present modification, since an intermediateoil separation mechanism 16 is provided so as to correspond to each of thecompression mechanisms intermediate oil separators 16 a in the vicinities of the first-stage compression elements stage compression elements intercooler 7 but also in the intermediate header tube 82, the inlet-sideintermediate branch tubes refrigerant tube 8. - In the configuration shown in
FIG. 12 , the intermediateoil return tube 16 b of the intermediateoil separation mechanism 16 provided for thefirst compression mechanism 203 may be connected to the portion of the secondintake branch tube 204 a configured so as to slope downward toward the flow juncture with theintake header tube 202 a, and the intermediateoil return tube 16 b of the intermediateoil separation mechanism 16 provided for thesecond compression mechanism 204 may be connected to the portion of the firstintake branch tube 203 a configured so as to slope downward toward the flow juncture with theintake header tube 202 a (seeFIG. 13 ). - In this configuration, in addition to the effects described above, even in cases of a disparity between the amount of refrigeration oil accompanying the refrigerant discharged from the first-
stage compression element 203 c of thefirst compression mechanism 203 and the amount of refrigeration oil accompanying the refrigerant discharged from the first-stage compression element 204 c of thesecond compression mechanism 204, which occurs as a result of a disparity between the amount of refrigeration oil retained in thefirst compression mechanism 203 and the amount of refrigeration oil retained in thesecond compression mechanism 204; more refrigeration oil returns to whichever of thecompression mechanisms first compression mechanism 203 and the amount of refrigeration oil retained in thesecond compression mechanism 204. Moreover, even if either one of thecompression mechanisms intake header tube 202 a, and oil shortages to the operating compression mechanism can be impeded. - In the above-described embodiment and the modifications thereof, in the air-
conditioning apparatus 1 configured to be capable of the air-cooling operation, theintercooler 7 was provided to the intermediaterefrigerant tube 8 and the intermediateoil separation mechanism 16 was provided between the first-stage compression element of the intermediaterefrigerant tube 8 and the inlet of theintercooler 7, thereby achieving the effects of reducing heat radiation loss in the heat source-side heat exchanger 4 functioning as a refrigerant cooler, improving operating efficiency, preventing oil shortages in the operating compression mechanism, and other effects. However, in addition to this configuration, another possibility is to enable switching between an air-cooling operation and an air-warming operation, and to further provide a second-stage injection tube for branching off the refrigerant cooled in the heat source-side heat exchanger 4 or the usage-side heat exchanger 6 and returning the refrigerant to the second-stage compression element 2 d. - For example, in the above-described embodiment in which a two-stage compression-
type compression mechanism 2 is used, arefrigerant circuit 310 can be used in which aswitching mechanism 3 is provided for switching between an air-cooling operation and an air-warming operation, a receiverinlet expansion mechanism 5 a and a receiveroutlet expansion mechanism 5 b are provided instead of theexpansion mechanism 5, and abridge circuit 17, areceiver 18, a second-stage injection tube 19, and aneconomizer heat exchanger 20 are provided as shown inFIG. 14 . - The
switching mechanism 3 is a mechanism for switching the direction of refrigerant flow in therefrigerant circuit 310. In order to allow the heat source-side heat exchanger 4 to function as a cooler of refrigerant compressed by thecompression mechanism 2 and to allow the usage-side heat exchanger 6 to function as a heater of refrigerant cooled in the heat source-side heat exchanger 4 during the air-cooling operation, theswitching mechanism 3 is capable of connecting the discharge side of thecompression mechanism 2 and one end of the heat source-side heat exchanger 4 and also connecting the intake side of thecompressor 21 and the usage-side heat exchanger 6 (refer to the solid lines of theswitching mechanism 3 inFIG. 14 , this state of theswitching mechanism 3 is hereinbelow referred to as the “cooling operation state”). In order to allow the usage-side heat exchanger 6 to function as a cooler of refrigerant compressed by thecompression mechanism 2 and to allow the heat source-side heat exchanger 4 to function as a heater of refrigerant cooled in the usage-side heat exchanger 6 during the air-warming operation, theswitching mechanism 3 is capable of connecting the discharge side of thecompression mechanism 2 and the usage-side heat exchanger 6 and also of connecting the intake side of thecompression mechanism 2 and one end of the heat source-side heat exchanger 4 (refer to the dashed lines of theswitching mechanism 3 inFIG. 14 , this state of theswitching mechanism 3 is hereinbelow referred to as the “heating operation state”). In the present modification, theswitching mechanism 3 is a four-way switching valve connected to the intake side of thecompression mechanism 2, the discharge side of thecompression mechanism 2, the heat source-side heat exchanger 4, and the usage-side heat exchanger 6. Theswitching mechanism 3 is not limited to a four-way switching valve, and may also be configured by combining a plurality of electromagnetic valves, for example, so as to provide the same function of switching the direction of refrigerant flow as described above. - Thus, the
switching mechanism 3 is configured so as to be capable of switching between the cooling operation state in which refrigerant is circulated in sequence through thecompression mechanism 2, the heat source-side heat exchanger 4, theexpansion mechanisms side heat exchanger 6; and the heating operation state in which refrigerant is circulated in sequence through thecompression mechanism 2, the usage-side heat exchanger 6, theexpansion mechanisms side heat exchanger 4. - An
intercooler bypass tube 9 is connected to the intermediaterefrigerant tube 8 so as to bypass theintercooler 7. Thisintercooler bypass tube 9 functions as an intercooler limiting mechanism for limiting the flow rate of refrigerant flowing through theintercooler 7. Theintercooler bypass tube 9 is provided with an intercooler bypass on/offvalve 11. The intercooler bypass on/offvalve 11 is an electromagnetic valve in the present modification. The intercooler bypass on/offvalve 11 is closed when theswitching mechanism 3 is set to the cooling operation state and opened when theswitching mechanism 3 is set to the heating operation state. - The intermediate
refrigerant tube 8 is provided with a cooler on/offvalve 12 in a position leading toward theintercooler 7 from the part connecting with the intercooler bypass tube 9 (i.e., in the portion leading from the part connecting with theintercooler bypass tube 9 nearer the inlet of theintercooler 7 to the connecting part nearer the outlet of the intercooler 7). The cooler on/offvalve 12 functions as an intercooler limiting mechanism for limiting the flow rate of refrigerant flowing through theintercooler 7. The cooler on/offvalve 12 is an electromagnetic valve in the present modification. The cooler on/offvalve 12 is controlled so as to open when theswitching mechanism 3 is set to the cooling operation state and close when theswitching mechanism 3 is set to the heating operation state. - The
bridge circuit 17 is provided between the heat source-side heat exchanger 4 and the usage-side heat exchanger 6, and is connected to areceiver inlet tube 18 a connected to an inlet of thereceiver 18, and to areceiver outlet tube 18 b connected to an outlet of thereceiver 18. Thebridge circuit 17 has fournon-return valves non-return valve 17 a is a non-return valve for allowing refrigerant to flow only from the heat source-side heat exchanger 4 to thereceiver inlet tube 18 a. The inletnon-return valve 17 b is a non-return valve for allowing refrigerant to flow only from the usage-side heat exchanger 6 to thereceiver inlet tube 18 a. In other words, the inletnon-return valves receiver inlet tube 18 a from either the heat source-side heat exchanger 4 or the usage-side heat exchanger 6. The outletnon-return valve 17 c is a non-return valve for allowing refrigerant to flow only from thereceiver outlet tube 18 b to the usage-side heat exchanger 6. The outletnon-return valve 17 d is a non-return valve for allowing refrigerant to flow only from thereceiver outlet tube 18 b to the heat source-side heat exchanger 4. In other words, the outletnon-return valves receiver outlet tube 18 b to the other of the heat source-side heat exchanger 4 and the usage-side heat exchanger 6. - The receiver
inlet expansion mechanism 5 a is a refrigerant-depressurizing mechanism provided to thereceiver inlet tube 18 a, and an electric expansion valve is used in the present modification. In the present modification, the receiverinlet expansion mechanism 5 a depressurizes the high-pressure refrigerant cooled in the heat source-side heat exchanger 4 before feeding the refrigerant to the usage-side heat exchanger 6 during the air-cooling operation, and depressurizes the high-pressure refrigerant cooled in the usage-side heat exchanger 6 before feeding the refrigerant to the heat source-side heat exchanger 4 during the air-warming operation. - The
receiver 18 is a container provided in order to temporarily retain refrigerant after it is depressurized by the receiverinlet expansion mechanism 5 a, wherein the inlet of the receiver is connected to thereceiver inlet tube 18 a and the outlet is connected to thereceiver outlet tube 18 b. Also connected to thereceiver 18 is anintake return tube 18 c capable of withdrawing refrigerant from inside thereceiver 18 and returning the refrigerant to theintake tube 2 a of the compression mechanism 2 (i.e., to the intake side of thecompression element 2 c on the first-stage side of the compression mechanism 2). Theintake return tube 18 c is provided with an intake return on/offvalve 18 d. The intake return on/offvalve 18 d is an electromagnetic valve in the present modification. - The receiver
outlet expansion mechanism 5 b is a refrigerant-depressurizing mechanism provided to thereceiver outlet tube 18 b, and an electric expansion valve is used in the present modification. In the present modification, the receiveroutlet expansion mechanism 5 b further depressurizes refrigerant depressurized by the receiverinlet expansion mechanism 5 a to an even lower pressure before feeding the refrigerant to the usage-side heat exchanger 6 during the air-cooling operation, and further depressurizes refrigerant depressurized by the receiverinlet expansion mechanism 5 a to an even lower pressure before feeding the refrigerant to the heat source-side heat exchanger 4. - Thus, when the
switching mechanism 3 is brought to the cooling operation state by thebridge circuit 17, thereceiver 18, thereceiver inlet tube 18 a, and thereceiver outlet tube 18 b, the high-pressure refrigerant cooled in the heat source-side heat exchanger 4 can be fed to the usage-side heat exchanger 6 through the inletnon-return valve 17 a of thebridge circuit 17, the receiverinlet expansion mechanism 5 a of thereceiver inlet tube 18 a, thereceiver 18, the receiveroutlet expansion mechanism 5 b of thereceiver outlet tube 18 b, and the outletnon-return valve 17 c of thebridge circuit 17. When theswitching mechanism 3 is brought to the heating operation state, the high-pressure refrigerant cooled in the usage-side heat exchanger 6 can be fed to the heat source-side heat exchanger 4 through the inletnon-return valve 17 b of thebridge circuit 17, the receiverinlet expansion mechanism 5 a of thereceiver inlet tube 18 a, thereceiver 18, the receiveroutlet expansion mechanism 5 b of thereceiver outlet tube 18 b, and the outletnon-return valve 17 d of thebridge circuit 17. - The second-
stage injection tube 19 has the function of branching off the refrigerant cooled in the heat source-side heat exchanger 4 or the usage-side heat exchanger 6 and returning the refrigerant to thecompression element 2 d on the second-stage side of thecompression mechanism 2. In the present modification, the second-stage injection tube 19 is provided so as to branch off refrigerant flowing through thereceiver inlet tube 18 a and return the refrigerant to the second-stage compression element 2 d. More specifically, the second-stage injection tube 19 is provided so as to branch off refrigerant from a position upstream of the receiverinlet expansion mechanism 5 a of thereceiver inlet tube 18 a (specifically, between the heat source-side heat exchanger 4 and the receiverinlet expansion mechanism 5 a when theswitching mechanism 3 is in the cooling operation state, and between the usage-side heat exchanger 6 and the receiverinlet expansion mechanism 5 a when theswitching mechanism 3 is in the heating operation state) and return the refrigerant to a position downstream of theintercooler 7 of the intermediaterefrigerant tube 8. The second-stage injection tube 19 is provided with a second-stage injection valve 19 a whose opening degree can be controlled. The second-stage injection valve 19 a is an electric expansion valve in the present modification. - The
economizer heat exchanger 20 is a heat exchanger for conducting heat exchange between the refrigerant cooled in the heat source-side heat exchanger 4 or the usage-side heat exchanger 6 and the refrigerant flowing through the second-stage injection tube 19 (more specifically, the refrigerant that has been depressurized nearly to an intermediate pressure in the second-stage injection valve 19 a). In the present modification, theeconomizer heat exchanger 20 is provided so as to conduct heat exchange between the refrigerant flowing through a position upstream (specifically, between the heat source-side heat exchanger 4 and the receiverinlet expansion mechanism 5 a when theswitching mechanism 3 is in the cooling operation state, and between the usage-side heat exchanger 6 and the receiverinlet expansion mechanism 5 a when theswitching mechanism 3 is in the heating operation state) of the receiverinlet expansion mechanism 5 a of thereceiver inlet tube 18 a and the refrigerant flowing through the second-stage injection tube 19, and theeconomizer heat exchanger 20 has flow channels through which both refrigerants flow so as to oppose each other. In the present modification, theeconomizer heat exchanger 20 is provided upstream of the second-stage injection tube 19 of thereceiver inlet tube 18 a. Therefore, the refrigerant cooled in the heat source-side heat exchanger 4 or usage-side heat exchanger 6 is branched off in thereceiver inlet tube 18 a to the second-stage injection tube 19 before undergoing heat exchange in theeconomizer heat exchanger 20, and heat exchange is then conducted in theeconomizer heat exchanger 20 with the refrigerant flowing through the second-stage injection tube 19. - Furthermore, the air-
conditioning apparatus 1 of the present modification is provided with various sensors. Specifically, anintermediate pressure sensor 54 for detecting the pressure of refrigerant flowing through the intermediaterefrigerant tube 8 is provided to the intermediaterefrigerant tube 8 or thecompression mechanism 2. The outlet on the second-stage injection tube 19 side of theeconomizer heat exchanger 20 is provided with an economizeroutlet temperature sensor 55 for detecting the temperature of refrigerant at the outlet on the second-stage injection tube 19 side of theeconomizer heat exchanger 20. - Next, the action of the air-
conditioning apparatus 1 of the present modification will be described usingFIGS. 14 through 18 .FIG. 15 is a pressure-enthalpy graph representing the refrigeration cycle during the air-cooling operation inModification 6,FIG. 16 is a temperature-entropy graph representing the refrigeration cycle during the air-cooling operation inModification 6,FIG. 17 is a pressure-enthalpy graph representing the refrigeration cycle during the air-warming operation inModification 6, andFIG. 18 is a temperature-entropy graph representing the refrigeration cycle during the air-warming operation inModification 6. Operation control in the air-cooling operation and the air-warming operation described hereinbelow is performed by the aforementioned controller (not shown). In the following description, the term “high pressure” means a high pressure in the refrigeration cycle (specifically, the pressure at points D, D′, E, and H inFIGS. 15 and 16 , and the pressure at points D, D′, F, and H inFIGS. 17 and 18 ), the term “low pressure” means a low pressure in the refrigeration cycle (specifically, the pressure at points A, F, and F′ inFIGS. 15 and 16 , and the pressure at points A, E, and E′ inFIGS. 17 and 18 ), and the term “intermediate pressure” means an intermediate pressure in the refrigeration cycle (specifically, the pressure at points B1, C1, U, J, and K inFIGS. 15 through 18 ). - <Air-Cooling Operation>
- During the air-cooling operation, the
switching mechanism 3 is brought to the cooling operation state shown by the solid lines inFIG. 14 . The opening degrees of the receiverinlet expansion mechanism 5 a and the receiveroutlet expansion mechanism 5 b are adjusted. Since theswitching mechanism 3 is in the cooling operation state, the cooler on/offvalve 12 is opened and the intercooler bypass on/offvalve 11 of theintercooler bypass tube 9 is closed, thereby putting theintercooler 7 into a state of functioning as a cooler. Furthermore, the opening degree of the second-stage injection valve 19 a is also adjusted. More specifically, in the present modification, so-called superheat degree control is performed wherein the opening degree of the second-stage injection valve 19 a is adjusted so that a target value is achieved in the degree of superheat of the refrigerant at the outlet in the second-stage injection tube 19 side of theeconomizer heat exchanger 20. In the present modification, the degree of superheat of the refrigerant at the outlet in the second-stage injection tube 19 side of theeconomizer heat exchanger 20 is obtained by converting the intermediate pressure detected by theintermediate pressure sensor 54 to a saturation temperature and subtracting this refrigerant saturation temperature value from the refrigerant temperature detected by the economizeroutlet temperature sensor 55. Though not used in the present modification, another possible option is to provide a temperature sensor to the inlet in the second-stage injection tube 19 side of theeconomizer heat exchanger 20, and to obtain the degree of superheat of the refrigerant at the outlet in the second-stage injection tube 19 side of theeconomizer heat exchanger 20 by subtracting the refrigerant temperature detected by this temperature sensor from the refrigerant temperature detected by the economizeroutlet temperature sensor 55. - When the
compression mechanism 2 is driven while therefrigerant circuit 310 is in this state, low-pressure refrigerant (refer to point A inFIGS. 14 to 16 ) is drawn into thecompression mechanism 2 through theintake tube 2 a, and after the refrigerant is first compressed by thecompression element 2 c to an intermediate pressure, the refrigerant is discharged to the intermediate refrigerant tube 8 (refer to point B1 inFIGS. 14 to 16 ). As in the embodiment described above, the intermediate-pressure refrigerant discharged from the first-stage compression element 2 c flows into theintermediate oil separator 16 a constituting the intermediateoil separation mechanism 16, and after the accompanying refrigeration oil is separated, the refrigerant is fed to theintercooler 7. - The refrigeration oil separated from the intermediate-pressure refrigerant in the
intermediate oil separator 16 a flows into the intermediateoil return tube 16 b constituting the intermediateoil separation mechanism 16, and after being depressurized by thedepressurizing mechanism 16 c provided to the intermediateoil return tube 16 b, the refrigerant is returned to the compression mechanism 2 (theintake tube 2 a in this case) and led back into thecompression mechanism 2. After the refrigeration oil has been separated in the intermediateoil separation mechanism 16, the intermediate-pressure refrigerant is then cooled in theintercooler 7 by undergoing heat exchange with water or air as a cooling source (refer to point C1 inFIGS. 14 to 16 ). The refrigerant cooled in theintercooler 7 is further cooled (refer to point G inFIGS. 14 to 16 ) by mixing with refrigerant being returned from the second-stage injection tube 19 to the second-stageside compression element 2 d (refer to point K inFIGS. 14 to 16 ). Next, having been mixed with the refrigerant returned from the second-stage injection tube 19, the intermediate-pressure refrigerant is drawn into and further compressed in thecompression element 2 d connected to the second-stage side of thecompression element 2 c, and the refrigerant is then discharged from thecompression mechanism 2 to thedischarge tube 2 b (refer to point D inFIGS. 14 to 16 ). The high-pressure refrigerant discharged from thecompression mechanism 2 is compressed by the two-stage compression action of thecompression elements FIG. 15 ). The high-pressure refrigerant discharged from thecompression mechanism 2 is fed via theswitching mechanism 3 to the heat source-side heat exchanger 4 functioning as a refrigerant cooler, and the refrigerant is cooled by heat exchange with water or air as a cooling source (refer to point E inFIGS. 14 to 16 ). The high-pressure refrigerant cooled in the heat source-side heat exchanger 4 flows through the inletnon-return valve 17 a of thebridge circuit 17 into thereceiver inlet tube 18 a, and some of the refrigerant is branched off to the second-stage injection tube 19. The refrigerant flowing through the second-stage injection tube 19 is depressurized to a nearly intermediate pressure in the second-stage injection valve 19 a and is then fed to the economizer heat exchanger 20 (refer to point J inFIGS. 14 to 16 ). The refrigerant flowing through thereceiver inlet tube 18 a after being branched off to the second-stage injection tube 19 then flows into theeconomizer heat exchanger 20, where it is cooled by heat exchange with the refrigerant flowing through the second-stage injection tube 19 (refer to point H inFIGS. 14 to 16 ). The refrigerant flowing through the second-stage injection tube 19 is heated by heat exchange with the refrigerant flowing through thereceiver inlet tube 18 a (refer to point K inFIGS. 14 to 16 ), and this refrigerant mixes with the refrigerant cooled in theintercooler 7 as described above. - The high-pressure refrigerant cooled in the
economizer heat exchanger 20 is depressurized to a nearly saturated pressure by the receiverinlet expansion mechanism 5 a and is temporarily retained in the receiver 18 (refer to point I inFIGS. 14 to 16 ). The refrigerant retained in thereceiver 18 is fed to thereceiver outlet tube 18 b and is depressurized by the receiveroutlet expansion mechanism 5 b to become a low-pressure gas-liquid two-phase refrigerant, and is then fed through the outletnon-return valve 17 c of thebridge circuit 17 to the usage-side heat exchanger 6 functioning as a refrigerant heater (refer to point F inFIGS. 14 to 16 ). The low-pressure gas-liquid two-phase refrigerant fed to the usage-side heat exchanger 6 is heated by heat exchange with water or air as a heating source, and the refrigerant is evaporated as a result (refer to point A inFIGS. 14 to 16 ). The low-pressure refrigerant heated in the usage-side heat exchanger 6 is led once again into thecompression mechanism 2 via theswitching mechanism 3. In this manner the air-cooling operation is performed. - In the configuration of the present modification, as in the embodiment described above, since the
intercooler 7 is in a state of functioning as a cooler during the air-cooling operation in which theswitching mechanism 3 is brought to the cooling operation state, heat radiation loss in the heat source-side heat exchanger 4 can be reduced in comparison with cases in which nointercooler 7 is provided. - In the configuration of the present modification, as in the embodiment described above, since an intermediate
oil separation mechanism 16 is provided in a section of the intermediaterefrigerant tube 8 between the first-stage compression element 2 c and the inlet of theintercooler 7, it is possible to prevent oil shortages to thecompression mechanism 2 caused by the accumulation of refrigeration oil in theintercooler 7, and also to prevent loss of heat transfer performance and increases in pressure drop in theintercooler 7. Furthermore, in the present modification, since the intermediateoil separation mechanism 16 is provided in a position farther upstream than the connecting point between the intermediaterefrigerant tube 8 and theintercooler bypass tube 9, the accumulation of refrigeration oil in theintercooler bypass tube 9 can also be prevented. - Moreover, in the configuration of the present modification, since the second-
stage injection tube 19 is provided so as to branch off refrigerant fed from the heat source-side heat exchanger 4 to theexpansion mechanisms stage compression element 2 d, the temperature of refrigerant drawn into the second-stage compression element 2 d can be kept even lower (refer to points C1 and G inFIG. 16 ) without performing heat radiation to the exterior, such as is done with theintercooler 7. The temperature of refrigerant discharged from thecompression mechanism 2 is thereby kept even lower (refer to points D and D′ inFIG. 16 ), and operating efficiency can be further improved because heat radiation loss can be further reduced in proportion to the area enclosed by connecting the points C1, D′, D, and G inFIG. 16 , in comparison with cases in which no second-stage injection tube 19 is provided. - In the configuration of the present modification, since an
economizer heat exchanger 20 is also provided for conducting heat exchange between the refrigerant fed from the heat source-side heat exchanger 4 to theexpansion mechanisms stage injection tube 19, the refrigerant fed from the heat source-side heat exchanger 4 to theexpansion mechanisms FIGS. 15 and 16 ), and the cooling capacity per flow rate of refrigerant in the usage-side heat exchanger 6 can be increased in comparison with cases in which the second-stage injection tube 19 andeconomizer heat exchanger 20 are not provided (in this case, the refrigeration cycle inFIGS. 15 and 16 is performed in the following sequence: point A→point B1→point C1→point D′→point E→point F′). - <Air-Warming Operation>
- During the air-warming operation, the
switching mechanism 3 is brought to the heating operation state shown by the dashed lines inFIG. 14 . The opening degrees of the receiverinlet expansion mechanism 5 a and receiveroutlet expansion mechanism 5 b are adjusted. Since theswitching mechanism 3 is in the heating operation state, the cooler on/offvalve 12 is closed and the intercooler bypass on/offvalve 11 of theintercooler bypass tube 9 is opened, thereby putting theintercooler 7 in a state of not functioning as a cooler. Furthermore, the opening degree of the second-stage injection valve 19 a is also adjusted by the same superheat degree control as in the air-cooling operation. - When the
compression mechanism 2 is driven while therefrigerant circuit 310 is in this state, low-pressure refrigerant (refer to point A inFIGS. 14 , 17, and 18) is drawn into thecompression mechanism 2 through theintake tube 2 a, and after the refrigerant is first compressed by thecompression element 2 c to an intermediate pressure, the refrigerant is discharged to the intermediate refrigerant tube 8 (refer to point B1 inFIGS. 14 , 17, and 18). As in the embodiment described above, the intermediate-pressure discharged from the first-stage compression element 2 c flows into theintermediate oil separator 16 a constituting the intermediateoil separation mechanism 16, and after the accompanying refrigeration oil is separated, the refrigerant is fed to theintercooler 7. The refrigeration oil separated from the intermediate-pressure refrigerant in theintermediate oil separator 16 a flows into the intermediateoil return tube 16 b constituting the intermediateoil separation mechanism 16, and after being depressurized by thedepressurizing mechanism 16 c provided to the intermediateoil return tube 16 b, the refrigerant is returned to the compression mechanism 2 (theintake tube 2 a in this case) and led back into thecompression mechanism 2. After the refrigeration oil has been separated in the intermediateoil separation mechanism 16, the intermediate-pressure refrigerant then passes through the intercooler bypass tube 9 (refer to point C1 inFIGS. 14 , 17, and 18) without passing through the intercooler 7 (i.e. without being cooled), unlike the air-cooling operation, and the refrigerant is cooled (refer to point G inFIGS. 14 , 17, and 18) by being mixed with refrigerant being returned from the second-stage injection tube 19 to thecompression element 2 d (refer to point K inFIGS. 14 , 17, and 18). Next, having been mixed with the refrigerant returning from the second-stage injection tube 19, the intermediate-pressure refrigerant is led to and further compressed in thecompression element 2 d connected to the second-stage side of thecompression element 2 c, and the refrigerant is discharged from thecompression mechanism 2 to thedischarge tube 2 b (refer to point D inFIGS. 14 , 17, and 18). The high-pressure refrigerant discharged from thecompression mechanism 2 is compressed by the two-stage compression action of thecompression elements FIG. 17 ), similar to the air-cooling operation. The high-pressure refrigerant discharged from thecompression mechanism 2 is fed via theswitching mechanism 3 to the usage-side heat exchanger 6 functioning as a refrigerant cooler, and the refrigerant is cooled by heat exchange with water or air as a cooling source (refer to point F inFIGS. 14 , 17, and 18). The high-pressure refrigerant cooled in the usage-side heat exchanger 6 flows through the inletnon-return valve 17 b of thebridge circuit 17 into thereceiver inlet tube 18 a, and some of the refrigerant is branched off to the second-stage injection tube 19. The refrigerant flowing through the second-stage injection tube 19 is depressurized to a nearly intermediate pressure in the second-stage injection valve 19 a, and is then fed to the economizer heat exchanger 20 (refer to point J inFIGS. 14 , 17, and 18). The refrigerant flowing through thereceiver inlet tube 18 a after being branched off to the second-stage injection tube 19 then flows into theeconomizer heat exchanger 20 and is cooled by heat exchange with the refrigerant flowing through the second-stage injection tube 19 (refer to point H inFIGS. 14 , 17, and 18). The refrigerant flowing through the second-stage injection tube 19 is heated by heat exchange with the refrigerant flowing through thereceiver inlet tube 18 a (refer to point K inFIGS. 14 , 17, and 18), and the refrigerant is mixed with the intermediate-pressure refrigerant discharged from the first-stage compression element 2 c as described above. The high-pressure refrigerant cooled in theeconomizer heat exchanger 20 is depressurized to a nearly saturated pressure by the receiverinlet expansion mechanism 5 a and is temporarily retained in the receiver 18 (refer to point I inFIGS. 14 , 17, and 18). The refrigerant retained in thereceiver 18 is fed to thereceiver outlet tube 18 b and is depressurized by the receiveroutlet expansion mechanism 5 b to become a low-pressure gas-liquid two-phase refrigerant, and is then fed through the outletnon-return valve 17 d of thebridge circuit 17 to the heat source-side heat exchanger 4 functioning as a refrigerant heater (refer to point E inFIGS. 14 , 17, and 18). The low-pressure gas-liquid two-phase refrigerant fed to the heat source-side heat exchanger 4 is heated by heat exchange with water or air as a heating source, and the refrigerant is evaporated as a result (refer to point A inFIGS. 14 , 17, and 18). The low-pressure refrigerant heated in the heat source-side heat exchanger 4 is led once again into thecompression mechanism 2 via theswitching mechanism 3. In this manner the air-warming operation is performed. - In the configuration of the present modification, since the
intercooler 7 is brought to a state of not functioning as a cooler by closing the cooler on/offvalve 12 and opening the intercooler bypass on/offvalve 11 of theintercooler bypass tube 9 during the air-warming operation in which theswitching mechanism 3 is set to the heating operation state, the temperature decrease in the refrigerant discharged from thecompression mechanism 2 is minimized (refer to points D and D′ inFIG. 18 ) in comparison with cases in which only theintercooler 7 is provided or cases in which theintercooler 7 is made to function as a cooler as in the air-cooling operation described above. Therefore, in this air-conditioning apparatus 1, heat radiation to the exterior can be minimized, it is possible to minimize the decrease in the temperature of refrigerant supplied to the usage-side heat exchanger 6 functioning as a refrigerant cooler, the decrease of heating capacity can be minimized, and reduction in operating efficiency can be prevented, in comparison with cases in which only theintercooler 7 is provided or cases in which theintercooler 7 is made to function as a cooler as in the air-cooling operation described above. - In the configuration of the present modification, as in the air-cooling operation described above, since the intermediate
oil separation mechanism 16 is provided in a section of the intermediaterefrigerant tube 8 between the first-stage compression element 2 c and the inlet of theintercooler 7, it is possible to prevent oil shortages to thecompression mechanism 2 caused by the accumulation of refrigeration oil in theintercooler 7, and loss of heat transfer performance and increases in pressure drop in theintercooler 7 can also be prevented. - Moreover, in the configuration of the present modification, since the second-
stage injection tube 19 is provided so as to branch off refrigerant fed from the usage-side heat exchanger 6 to theexpansion mechanisms stage compression element 2 d, the temperature of the refrigerant discharged from thecompression mechanism 2 is lower (refer to points D and D′ inFIG. 18 ), and the heating capacity per flow rate of refrigerant in the usage-side heat exchanger 6 thereby decreases (refer to points D, D′, and F inFIG. 17 ), but since the flow rate of refrigerant discharged from the second-stage compression element 2 d increases, the heating capacity in the usage-side heat exchanger 6 is preserved, and operating efficiency can be improved. - In the configuration of the present modification, since an
economizer heat exchanger 20 is also provided for conducting heat exchange between the refrigerant fed from the usage-side heat exchanger 6 to theexpansion mechanisms stage injection tube 19, the refrigerant flowing through the second-stage injection tube 19 can be heated by the refrigerant fed from the usage-side heat exchanger 6 to theexpansion mechanisms FIGS. 17 and 18 ), and the flow rate of refrigerant discharged from the second-stage compression element 2 d can be increased in comparison with cases in which the second-stage injection tube 19 andeconomizer heat exchanger 20 are not provided (in this case, the refrigeration cycle inFIGS. 17 and 18 is performed in the following sequence: point A→point B1→point C1→point D′→point F→point E′). - Advantages of both the air-cooling operation and the air-warming operation in the configuration of the present modification are that the
economizer heat exchanger 20 is a heat exchanger which has flow channels through which refrigerant fed from the heat source-side heat exchanger 4 or usage-side heat exchanger 6 to theexpansion mechanisms stage injection tube 19 both flow so as to oppose each other; therefore, it is possible to reduce the temperature difference between the refrigerant fed to theexpansion mechanisms side heat exchanger 4 or the usage-side heat exchanger 6 in theeconomizer heat exchanger 20 and the refrigerant flowing through the second-stage injection tube 19, and high heat exchange efficiency can be achieved. In the configuration of the present modification, since the second-stage injection tube 19 is provided so as to branch off the refrigerant fed to theexpansion mechanisms side heat exchanger 4 or the usage-side heat exchanger 6 before the refrigerant fed to theexpansion mechanisms side heat exchanger 4 or the usage-side heat exchanger 6 undergoes heat exchange in theeconomizer heat exchanger 20, it is possible to reduce the flow rate of the refrigerant fed from the heat source-side heat exchanger 4 or usage-side heat exchanger 6 to theexpansion mechanisms stage injection tube 19 in theeconomizer heat exchanger 20, the quantity of heat exchanged in theeconomizer heat exchanger 20 can be reduced, and the size of theeconomizer heat exchanger 20 can be reduced. - Though not described in detail herein, a compression mechanism having more stages than a two-stage compression system, such as a three-stage compression system (e.g. the
compression mechanism 102 in Modification 3) or the like, may be used instead of the two-stage compression-type compression mechanism 2, or a parallel multi-stage compression-type compression mechanism in which a plurality of compression mechanisms are connected in parallel, such as a refrigerant circuit 410 (seeFIG. 19 ) which uses thecompression mechanism 202 having the two-stage compression-type compression mechanisms Modification 4, may be used instead of the two-stage compression-type compression mechanism 2, and the same effects as those of the present modification can be achieved in this case as well. In the air-conditioning apparatus 1 of the present modification, the use of thebridge circuit 17 is included from the standpoint of keeping the direction of refrigerant flow constant in the receiverinlet expansion mechanism 5 a, the receiveroutlet expansion mechanism 5 b, thereceiver 18, the second-stage injection tube 19, or theeconomizer heat exchanger 20, regardless of whether the air-cooling operation or air-warming operation is in effect. However, thebridge circuit 17 may be omitted in cases in which there is no need to keep the direction of refrigerant flow constant in the receiverinlet expansion mechanism 5 a, the receiveroutlet expansion mechanism 5 b, thereceiver 18, the second-stage injection tube 19, or theeconomizer heat exchanger 20 regardless of whether the air-cooling operation or the air-warming operation is taking place, such as cases in which the second-stage injection tube 19 andeconomizer heat exchanger 20 are used either during the air-cooling operation alone or during the air-warming operation alone, for example. - The refrigerant circuit 310 (see
FIG. 14 ) and the refrigerant circuit 410 (seeFIG. 19 ) inModification 6 described above had configurations in which one usage-side heat exchanger 6 was connected, but they may alternatively have configurations in which a plurality of usage-side heat exchangers 6 are connected and these usage-side heat exchangers 6 can be started and stopped individually. - For example, the refrigerant circuit 310 (
FIG. 15 ) ofModification 7, which uses a two-stage compression-type compression mechanism 2, may be fashioned into arefrigerant circuit 510 in which two usage-side heat exchangers 6 are connected, usage-side expansion mechanisms 5 c are provided corresponding to the ends of the usage-side heat exchangers 6 on the sides facing thebridge circuit 17, the receiveroutlet expansion mechanism 5 b previously provided to thereceiver outlet tube 18 b is omitted, and a bridgeoutlet expansion mechanism 5 d is provided instead of the outletnon-return valve 17 d of thebridge circuit 17, as shown inFIG. 20 . Alternatively, the refrigerant circuit 410 (seeFIG. 19 ) ofModification 6 which uses the parallel two-stage compression-type compression mechanism 202 may be fashioned into arefrigerant circuit 610 in which two usage-side heat exchangers 6 are connected, usage-side expansion mechanisms 5 c are provided corresponding to the ends of the usage-side heat exchangers 6 on the sides facing thebridge circuit 17, the receiveroutlet expansion mechanism 5 b previously provided to thereceiver outlet tube 18 b is omitted, and a bridgeoutlet expansion mechanism 5 d is provided instead of the outletnon-return valve 17 d of thebridge circuit 17, as shown inFIG. 21 . - The configuration of the present modification has different actions during the air-cooling operation in
Modification 6 in that during the air-cooling operation, the bridgeoutlet expansion mechanism 5 d is fully closed, and in place of the receiveroutlet expansion mechanism 5 b inModification 7, the usage-side expansion mechanisms 5 c perform the action of further depressurizing the refrigerant already depressurized by the receiverinlet expansion mechanism 5 a to a lower pressure before the refrigerant is fed to the usage-side heat exchangers 6; but the other actions of the present modification are essentially the same as the actions during the air-cooling operation in Modification 6 (FIGS. 14 through 16 and their relevant descriptions). The present modification also has different actions from those during the air-warming operation inModification 6 in that during the air-warming operation, the opening degrees of the usage-side expansion mechanisms 5 c are adjusted so as to control the flow rate of refrigerant flowing through the usage-side heat exchangers 6, and in place of the receiveroutlet expansion mechanism 5 b inModification 6, the bridgeoutlet expansion mechanism 5 d performs the action of further depressurizing the refrigerant already depressurized by the receiverinlet expansion mechanism 5 a to a lower pressure before the refrigerant is fed to the heat source-side heat exchanger 4; but the other actions of the present modification are essentially the same as the actions during the air-warming operation in Modification 6 (FIGS. 14 , 17, 18, and their relevant descriptions). - The same operational effects as those of
Modification 6 described above can also be achieved with the configuration of the present modification. - Though not described in detail herein, a compression mechanism having more stages than a two-stage compression system, such as a three-stage compression system (e.g. the
compression mechanism 102 in Modification 3) or the like, may be used instead of the two-stage compression-type compression mechanisms - Embodiments of the present invention and modifications thereof were described above with reference to the drawings, but the specific configuration is not limited to these embodiments or their modifications, and the configuration can be changed within a range that does not deviate from the scope of the invention.
- For example, in the above-described embodiment and modifications thereof, the present invention may be applied to a so-called chiller-type air-conditioning apparatus in which water or brine is used as a heating source or cooling source for conducting heat exchange with the refrigerant flowing through the usage-
side heat exchanger 6, and a secondary heat exchanger is provided for conducting heat exchange between indoor air and the water or brine that has undergone heat exchange in the usage-side heat exchanger 6. - The present invention can also be applied to other types of refrigeration apparatuses besides the above-described chiller-type air-conditioning apparatus, as long as the apparatus performs a multistage compression refrigeration cycle by using a refrigerant that operates in a supercritical range as its refrigerant.
- The refrigerant that operates in a supercritical range is not limited to carbon dioxide, and ethylene, ethane, nitric oxide, and other gases may also be used.
- If the present invention is used, in a refrigeration apparatus which performs a multistage compression refrigeration cycle by using a refrigerant that operates in a supercritical range, oil shortages to the compression mechanism can be prevented.
Claims (6)
1. A refrigeration apparatus which uses a refrigerant that operates in a supercritical range, the refrigeration apparatus comprising:
a compression mechanism having a plurality of compression elements, the compression mechanism being configured and arranged so that refrigerant discharged from a first-stage compression element of the plurality of compression elements is sequentially compressed by a second-stage compression element;
a heat source-side heat exchanger;
an expansion mechanism configured and arranged to depressurize the refrigerant;
a usage-side heat exchanger;
an intercooler configured and arranged to cool refrigerant flowing through an intermediate refrigerant tube that draws refrigerant discharged from the first-stage compression element into the second-stage compression element; and
an intermediate oil separation mechanism configured and arranged to separate a refrigeration oil from the refrigerant, the refrigeration oil accompanying the refrigerant discharged from the first-stage compression element, and the intermediate oil separation mechanism being arranged at a section of the intermediate refrigerant tube between the first-stage compression element and an inlet of the intercooler.
2. The refrigeration apparatus according to claim 1 , wherein
the intermediate oil separation mechanism has
an intermediate oil separator configured and arranged to separate the refrigeration oil from the refrigerant discharged from the first-stage compression element, and
an intermediate oil return tube configured and arranged to return the refrigeration oil separated from the refrigerant to the compression mechanism, the intermediate oil return tube being connected to the intermediate oil separator.
3. The refrigeration apparatus according to claim 1 , wherein
the intermediate oil separation mechanism has
a header arranged at the inlet of the intercooler, and
an intermediate oil return tube for connecting a lower end of the header to the compression mechanism.
4. The refrigeration apparatus according to claim 1 , wherein
the refrigerant that operates in the supercritical range is carbon dioxide.
5. The refrigeration apparatus according to claim 2 , wherein the refrigerant that operates in the supercritical range is carbon dioxide.
6. The refrigeration apparatus according to claim 3 , wherein the refrigerant that operates in the supercritical range is carbon dioxide.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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JP2007311692A JP2009133585A (en) | 2007-11-30 | 2007-11-30 | Refrigerating device |
JP2007-311692 | 2007-11-30 | ||
PCT/JP2008/071362 WO2009069604A1 (en) | 2007-11-30 | 2008-11-26 | Refrigeration device |
Publications (1)
Publication Number | Publication Date |
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US20100242529A1 true US20100242529A1 (en) | 2010-09-30 |
Family
ID=40678500
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US12/744,249 Abandoned US20100242529A1 (en) | 2007-11-30 | 2008-11-26 | Refrigeration apparatus |
Country Status (7)
Country | Link |
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US (1) | US20100242529A1 (en) |
EP (1) | EP2230471A4 (en) |
JP (1) | JP2009133585A (en) |
KR (1) | KR101157798B1 (en) |
CN (1) | CN101878402A (en) |
AU (1) | AU2008330740B2 (en) |
WO (1) | WO2009069604A1 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20120257939A1 (en) * | 2010-12-28 | 2012-10-11 | Per Hansson | reaming tool as well as a head and a cutting insert therefor |
US20140311177A1 (en) * | 2011-12-28 | 2014-10-23 | Daikin Industries, Ltd. | Refrigeration apparatus |
US20140326008A1 (en) * | 2011-10-21 | 2014-11-06 | Lg Electronics Ltd. | Air conditioner |
WO2015077275A1 (en) * | 2013-11-25 | 2015-05-28 | The Coca-Cola Company | Compressor with an oil separator |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2011214758A (en) * | 2010-03-31 | 2011-10-27 | Daikin Industries Ltd | Refrigerating device |
JP5573302B2 (en) * | 2010-03-31 | 2014-08-20 | ダイキン工業株式会社 | Refrigeration equipment |
CN102374694B (en) * | 2011-07-11 | 2013-06-19 | 中国科学院广州能源研究所 | CO2 multi-stage ejecting circulation heat pump/air conditioner system |
WO2014083674A1 (en) * | 2012-11-30 | 2014-06-05 | 三菱電機株式会社 | Compressor, refrigeration cycle device, and heat pump hot-water supply device |
JP6111655B2 (en) * | 2012-12-26 | 2017-04-12 | ダイキン工業株式会社 | Refrigeration equipment |
JP2014126284A (en) * | 2012-12-26 | 2014-07-07 | Daikin Ind Ltd | Refrigeration device |
JP2014190614A (en) * | 2013-03-27 | 2014-10-06 | Ebara Refrigeration Equipment & Systems Co Ltd | Turbo refrigerator |
JP6033348B2 (en) * | 2015-02-26 | 2016-11-30 | 株式会社大木工藝 | Frozen car |
CN107709896A (en) * | 2015-09-01 | 2018-02-16 | 株式会社电装 | Two level boosting type refrigeration circulates |
CN111256388B (en) * | 2018-11-30 | 2021-10-19 | 广东美芝精密制造有限公司 | Refrigeration system |
CN109682105B (en) * | 2019-02-12 | 2024-04-09 | 珠海格力电器股份有限公司 | Air Conditioning System |
Citations (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3680973A (en) * | 1970-06-08 | 1972-08-01 | Carrier Corp | Compressor power recovery |
US3719057A (en) * | 1971-10-08 | 1973-03-06 | Vilter Manufacturing Corp | Two-stage refrigeration system having crankcase pressure regulation in high stage compressor |
US3848422A (en) * | 1972-04-27 | 1974-11-19 | Svenska Rotor Maskiner Ab | Refrigeration plants |
US4151724A (en) * | 1977-06-13 | 1979-05-01 | Frick Company | Pressurized refrigerant feed with recirculation for compound compression refrigeration systems |
US4660384A (en) * | 1986-04-25 | 1987-04-28 | Vilter Manufacturing, Inc. | Defrost apparatus for refrigeration system and method of operating same |
US4947655A (en) * | 1984-01-11 | 1990-08-14 | Copeland Corporation | Refrigeration system |
US5150581A (en) * | 1991-06-24 | 1992-09-29 | Baltimore Aircoil Company | Head pressure controller for air conditioning and refrigeration systems |
US5769610A (en) * | 1994-04-01 | 1998-06-23 | Paul; Marius A. | High pressure compressor with internal, cooled compression |
US20020014088A1 (en) * | 2000-08-02 | 2002-02-07 | Mitsubishi Heavy Industries, Ltd. | Turbocompressor and refrigerating machine |
US20030177782A1 (en) * | 2002-03-20 | 2003-09-25 | Sivakumar Gopalnarayanan | Method for increasing efficiency of a vapor compression system by evaporator heating |
US20030192338A1 (en) * | 2002-04-10 | 2003-10-16 | Shailesh Manohar | Method for increasing efficiency of a vapor compression system by compressor cooling |
US20040007006A1 (en) * | 2001-02-13 | 2004-01-15 | Toshiyuki Ebara | On-vehicle air conditioner |
US20050115260A1 (en) * | 2003-12-01 | 2005-06-02 | Yap Zer K. | Water heating system |
US20050132729A1 (en) * | 2003-12-23 | 2005-06-23 | Manole Dan M. | Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device |
US20050210895A1 (en) * | 2004-03-29 | 2005-09-29 | Horton W T | Method and apparatus for reducing inrush current in a multi-stage compressor |
US20050279127A1 (en) * | 2004-06-18 | 2005-12-22 | Tao Jia | Integrated heat exchanger for use in a refrigeration system |
US20060083626A1 (en) * | 2004-10-19 | 2006-04-20 | Manole Dan M | Compressor and hermetic housing with minimal housing ports |
US20060083627A1 (en) * | 2004-10-19 | 2006-04-20 | Manole Dan M | Vapor compression system including a swiveling compressor |
US20060086110A1 (en) * | 2004-10-21 | 2006-04-27 | Manole Dan M | Method and apparatus for control of carbon dioxide gas cooler pressure by use of a two-stage compressor |
US20060230782A1 (en) * | 2005-03-30 | 2006-10-19 | Satoshi Imai | Refrigerating device and refrigerator |
US7131294B2 (en) * | 2004-01-13 | 2006-11-07 | Tecumseh Products Company | Method and apparatus for control of carbon dioxide gas cooler pressure by use of a capillary tube |
US7331196B2 (en) * | 2004-12-28 | 2008-02-19 | Sanyo Electric Co., Ltd. | Refrigerating apparatus and refrigerator |
US20090044564A1 (en) * | 2006-02-28 | 2009-02-19 | Masakazu Okamoto | Refrigerating Apparatus |
US7631510B2 (en) * | 2005-02-28 | 2009-12-15 | Thermal Analysis Partners, LLC. | Multi-stage refrigeration system including sub-cycle control characteristics |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5812687U (en) * | 1981-07-17 | 1983-01-26 | ダイキン工業株式会社 | Refrigeration equipment |
JP4080605B2 (en) * | 1998-08-26 | 2008-04-23 | 株式会社前川製作所 | Full liquid cooler |
JP2006329567A (en) * | 2005-05-30 | 2006-12-07 | Matsushita Electric Ind Co Ltd | Heat pump device |
-
2007
- 2007-11-30 JP JP2007311692A patent/JP2009133585A/en active Pending
-
2008
- 2008-11-26 EP EP08854068A patent/EP2230471A4/en not_active Withdrawn
- 2008-11-26 KR KR1020107013329A patent/KR101157798B1/en not_active IP Right Cessation
- 2008-11-26 WO PCT/JP2008/071362 patent/WO2009069604A1/en active Application Filing
- 2008-11-26 CN CN2008801182870A patent/CN101878402A/en active Pending
- 2008-11-26 US US12/744,249 patent/US20100242529A1/en not_active Abandoned
- 2008-11-26 AU AU2008330740A patent/AU2008330740B2/en not_active Ceased
Patent Citations (32)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3680973A (en) * | 1970-06-08 | 1972-08-01 | Carrier Corp | Compressor power recovery |
US3719057A (en) * | 1971-10-08 | 1973-03-06 | Vilter Manufacturing Corp | Two-stage refrigeration system having crankcase pressure regulation in high stage compressor |
US3848422A (en) * | 1972-04-27 | 1974-11-19 | Svenska Rotor Maskiner Ab | Refrigeration plants |
US4151724A (en) * | 1977-06-13 | 1979-05-01 | Frick Company | Pressurized refrigerant feed with recirculation for compound compression refrigeration systems |
US4947655A (en) * | 1984-01-11 | 1990-08-14 | Copeland Corporation | Refrigeration system |
US4660384A (en) * | 1986-04-25 | 1987-04-28 | Vilter Manufacturing, Inc. | Defrost apparatus for refrigeration system and method of operating same |
US5150581A (en) * | 1991-06-24 | 1992-09-29 | Baltimore Aircoil Company | Head pressure controller for air conditioning and refrigeration systems |
US5769610A (en) * | 1994-04-01 | 1998-06-23 | Paul; Marius A. | High pressure compressor with internal, cooled compression |
US20020014088A1 (en) * | 2000-08-02 | 2002-02-07 | Mitsubishi Heavy Industries, Ltd. | Turbocompressor and refrigerating machine |
US20040007006A1 (en) * | 2001-02-13 | 2004-01-15 | Toshiyuki Ebara | On-vehicle air conditioner |
US20030177782A1 (en) * | 2002-03-20 | 2003-09-25 | Sivakumar Gopalnarayanan | Method for increasing efficiency of a vapor compression system by evaporator heating |
US6698234B2 (en) * | 2002-03-20 | 2004-03-02 | Carrier Corporation | Method for increasing efficiency of a vapor compression system by evaporator heating |
US20030192338A1 (en) * | 2002-04-10 | 2003-10-16 | Shailesh Manohar | Method for increasing efficiency of a vapor compression system by compressor cooling |
US6658888B2 (en) * | 2002-04-10 | 2003-12-09 | Carrier Corporation | Method for increasing efficiency of a vapor compression system by compressor cooling |
US20050115260A1 (en) * | 2003-12-01 | 2005-06-02 | Yap Zer K. | Water heating system |
US20050132729A1 (en) * | 2003-12-23 | 2005-06-23 | Manole Dan M. | Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device |
US7096679B2 (en) * | 2003-12-23 | 2006-08-29 | Tecumseh Products Company | Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device |
US7131294B2 (en) * | 2004-01-13 | 2006-11-07 | Tecumseh Products Company | Method and apparatus for control of carbon dioxide gas cooler pressure by use of a capillary tube |
US20070000281A1 (en) * | 2004-01-13 | 2007-01-04 | Tecumseh Products Company | Method and apparatus for control of carbon dioxide gas cooler pressure by use of a capillary tube |
US7721569B2 (en) * | 2004-01-13 | 2010-05-25 | Tecumseh Products Company | Method and apparatus for control of carbon dioxide gas cooler pressure by use of a capillary tube |
US7028491B2 (en) * | 2004-03-29 | 2006-04-18 | Tecumseh Products Company | Method and apparatus for reducing inrush current in a multi-stage compressor |
US20050210895A1 (en) * | 2004-03-29 | 2005-09-29 | Horton W T | Method and apparatus for reducing inrush current in a multi-stage compressor |
US20050279127A1 (en) * | 2004-06-18 | 2005-12-22 | Tao Jia | Integrated heat exchanger for use in a refrigeration system |
US20060083626A1 (en) * | 2004-10-19 | 2006-04-20 | Manole Dan M | Compressor and hermetic housing with minimal housing ports |
US20060083627A1 (en) * | 2004-10-19 | 2006-04-20 | Manole Dan M | Vapor compression system including a swiveling compressor |
US20060086110A1 (en) * | 2004-10-21 | 2006-04-27 | Manole Dan M | Method and apparatus for control of carbon dioxide gas cooler pressure by use of a two-stage compressor |
US7600390B2 (en) * | 2004-10-21 | 2009-10-13 | Tecumseh Products Company | Method and apparatus for control of carbon dioxide gas cooler pressure by use of a two-stage compressor |
US20090301109A1 (en) * | 2004-10-21 | 2009-12-10 | Tecumseh Products Company | Method and apparatus for control of carbon dioxide gas cooler pressure by use of a two-stage compressor |
US7331196B2 (en) * | 2004-12-28 | 2008-02-19 | Sanyo Electric Co., Ltd. | Refrigerating apparatus and refrigerator |
US7631510B2 (en) * | 2005-02-28 | 2009-12-15 | Thermal Analysis Partners, LLC. | Multi-stage refrigeration system including sub-cycle control characteristics |
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Also Published As
Publication number | Publication date |
---|---|
KR20100095601A (en) | 2010-08-31 |
EP2230471A1 (en) | 2010-09-22 |
CN101878402A (en) | 2010-11-03 |
WO2009069604A1 (en) | 2009-06-04 |
JP2009133585A (en) | 2009-06-18 |
AU2008330740B2 (en) | 2011-08-04 |
EP2230471A4 (en) | 2011-02-09 |
KR101157798B1 (en) | 2012-06-19 |
AU2008330740A1 (en) | 2009-06-04 |
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