EP1990587A1 - Refrigeration device - Google Patents
Refrigeration device Download PDFInfo
- Publication number
- EP1990587A1 EP1990587A1 EP07714753A EP07714753A EP1990587A1 EP 1990587 A1 EP1990587 A1 EP 1990587A1 EP 07714753 A EP07714753 A EP 07714753A EP 07714753 A EP07714753 A EP 07714753A EP 1990587 A1 EP1990587 A1 EP 1990587A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- refrigerant
- compression mechanism
- gas
- pressure side
- volume ratio
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000005057 refrigeration Methods 0.000 title claims abstract description 11
- 239000003507 refrigerant Substances 0.000 claims abstract description 166
- 230000006835 compression Effects 0.000 claims abstract description 145
- 238000007906 compression Methods 0.000 claims abstract description 145
- 230000007246 mechanism Effects 0.000 claims abstract description 125
- 239000007788 liquid Substances 0.000 claims abstract description 71
- 238000006073 displacement reaction Methods 0.000 claims abstract description 10
- 238000002347 injection Methods 0.000 description 24
- 239000007924 injection Substances 0.000 description 24
- 238000001816 cooling Methods 0.000 description 17
- 238000010438 heat treatment Methods 0.000 description 15
- 230000002829 reductive effect Effects 0.000 description 9
- 230000000717 retained effect Effects 0.000 description 6
- 230000000694 effects Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000002401 inhibitory effect Effects 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 238000011156 evaluation Methods 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
-
- 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
-
- 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
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
Definitions
- the present invention relates to a refrigerating apparatus including a refrigerant circuit including a gas-liquid separator for performing two-stage compression/two-stage expansion refrigeration cycle utilizing of CO 2 refrigerant at high pressure as that at its critical pressure.
- refrigerating apparatuses including a refrigerant circuit are widely applied to air conditioners and the like.
- Patent Document 1 discloses an air conditioner including a refrigerant circuit including a gas-liquid separator for performing a two-stage compression/two-stage expansion refrigeration cycle.
- the refrigerant circuit of this air conditioner includes a compressor, a first heat exchanger, a first expansion valve, a gas-liquid separator, a second expansion valve, and a second heat exchanger.
- the compressor is of two-stage compression type in which a low pressure side compression mechanism and a high pressure side compression mechanism are connected by means of a drive shaft.
- the gas-liquid separator is so composed to separate intermediate-pressure refrigerant in a gas-liquid two-phase state into liquid refrigerant and gas refrigerant.
- refrigerant discharged form the compressor flows into the first heat exchanger.
- the refrigerant release heat to the air.
- the refrigerant having passed through the first heat exchanger is reduced in pressure up to intermediate pressure through the first expansion valve and flows then into the gas-liquid separator.
- the intermediate-pressure refrigerant in the gas-liquid two-phase state is separated into the gas refrigerant and the liquid refrigerant.
- the liquid refrigerant thus separated in the gas-liquid separator is reduced in pressure up to low pressure through the second expansion valve and flows then into the second heat exchanger.
- the refrigerant absorbs heat from the air to be evaporated. In this way, the indoor cooling is performed.
- the refrigerant having passed through the second heat exchanger is sucked into the compressor to be compressed up to intermediate pressure in the low pressure side compression mechanism.
- the refrigerant discharged from the low pressure side compression mechanism is mixed with the gas refrigerant separated in the gas-liquid separator.
- the air conditioner performs generally-called intermediate pressure gas injection in which the intermediate-pressure gas refrigerant is mixed with the refrigerant discharged from the low pressure side compression mechanism. Thereafter, the thus mixed refrigerant is compressed up to high pressure in the high pressure side compression mechanism and is then discharged from the compressor again.
- the air conditioner of Patent Document 1 performs the intermediate pressure gas injection to lower the temperature of the refrigerant discharged from the compressor for reducing the power required for driving the compressor, thereby increasing the COP (coefficient of performance) of the air conditioner.
- Patent Document 2 discloses an air conditioner in which the aforementioned intermediate pressure gas injection is performed with CO 2 refrigerant filled in a refrigerant circuit. This air conditioner performs a generally-called supercritical cycle in which the refrigerant discharged from the compressor is compressed over its critical pressure.
- the volume (displacement volume) of each compression mechanism of the two-stage compression type compressor is so designed to attain efficient two-stage compression.
- the refrigerant after being compressed up to its supercritical pressure and releasing heat in an heat exchanger may be at the supercritical pressure yet in the gas-liquid separator.
- the refrigerant at supercritical pressure (in the critical state) in the gas-liquid separator is difficult to be separated into the gas refrigerant and the liquid refrigerant. This inhibits sending of only the gas refrigerant to the intermediate-pressure refrigerant in the compressor to inhibit the aforementioned intermediate pressure gas injection. Accordingly, desired effects by the intermediate pressure gas injection cannot be attained to invite lowering of the COP of the air conditioner.
- the present invention has been made in view of the foregoing and has its object of enabling operation at an optimal COP in a refrigerating apparatus performing two-stage compression/two-stage expansion refrigeration cycle using CO 2 refrigerant.
- a first aspect of the present invention premises a refrigerating apparatus including a refrigerant circuit for performing a two-stage compression/two-stage expansion refrigeration cycle in which CO 2 refrigerant at high pressure is utilized as that at its critical pressure, the refrigerant circuit including: a compressor including a low pressure side compression mechanism and a high pressure side compression mechanism connected to each other by means of a drive shaft; and a gas-liquid separator for separating refrigerant at intermediate pressure into gas refrigerant and liquid refrigerant.
- a volume ratio of a displacement volume of the high pressure side compression mechanism to that of the low pressure side compression mechanism falls in a range between 0.8 and 1.3, both exclusive.
- the refrigerant circuit ( 10 ) in the first aspect is filled with CO 2 refrigerant. Further, the compressor ( 30 ) including the low pressure side compression mechanism ( 34 ) and the high pressure side compression mechanism ( 35 ) is provided in the refrigerant circuit ( 10 ). In the refrigerant circuit ( 10 ), the following two-stage compression/two-stage expansion refrigeration cycle is performed.
- the refrigerant compressed up to its critical pressure in the high pressure side compression mechanism ( 35 ) releases heat in, for example, an indoor heat exchanger, is reduced in pressure up to intermediate pressure, and flows then into the gas-liquid separator ( 15 ).
- the intermediate-pressure refrigerant is separated into the gas refrigerant and the liquid refrigerant.
- the liquid refrigerant is reduced in pressure up to low pressure, is evaporated in, for example, an outdoor heat exchanger, and is then sucked into the low pressure side compression mechanism ( 34 ).
- This refrigerant is compressed up to intermediate pressure in the low pressure side compression mechanism ( 34 ).
- the gas refrigerant separated in the liquid-gas separator ( 15 ) is introduced into this refrigerant.
- the aforementioned intermediate pressure gas injection is performed.
- the refrigerant is compressed up to high pressure (critical pressure) in the high pressure side compression mechanism ( 35 ).
- the intermediate-pressure refrigerant in the gas-liquid separator may reach its critical pressure in the conventional refrigerating apparatus. If so, the refrigerant in the gas-liquid separator cannot be separated into the gas refrigerant and the liquid refrigerant to inhibit desired intermediate pressure gas injection.
- the volume ratio of the high pressure side compression mechanism ( 35 ) to the low pressure side compression mechanism ( 34 ) is set greater than 0.8.
- the volume ratio When the volume ratio is set equal to or smaller than 0.8, the displacement volume of the high pressure side compression mechanism ( 35 ) becomes relatively smaller than that of the low pressure side compression mechanism ( 34 ), thereby increasing the pressure of the intermediate-pressure refrigerant to invite an increase in pressure of the refrigerant in the gas-liquid separator ( 15 ) over its critical pressure.
- the volume ratio in which the volume ratio is set greater than 0.8, the refrigerant in the gas-liquid separator ( 15 ) can be suppressed at its subcritical pressure.
- the refrigerant in the gas-liquid separator ( 15 ) is definitely separated into the gas refrigerant and the liquid refrigerant to attain desired effects by the intermediate pressure gas injection.
- the displacement volume of the high pressure side compression mechanism ( 35 ) is relatively greater than that of the low pressure side compression mechanism ( 34 ).
- the amount of the refrigerant sucked in the high pressure side compression mechanism ( 35 ) is secured insufficiently to invite lowering of the compression efficiency of the compressor ( 30 ).
- this aspect of the present invention sets the volume ratio to be smaller than 1.3 to secure a sufficient amount of the refrigerant sucked in the high pressure side compression mechanism ( 35 ), with a result that the refrigerant can be compressed in two stages efficiently.
- the volume ratio falls in a range between 0.9 and 1.1, both inclusive.
- the volume ratio of the displacement volume of the high pressure side compression mechanism ( 35 ) to that of the low pressure side compression mechanism ( 34 ) is set in the range between 0.9 and 1.1, both inclusive.
- the volume ratio exceeding 0.9 definitely makes the refrigerant in the gas-liquid separator ( 15 ) reach its critical pressure. While, the volume ratio not exceeding 1.1 attains further efficient two-stage compression of the refrigerant.
- the volume ratio is 1.0.
- the volume of the low pressure side compression mechanism ( 34 ) and that of the high pressure side compression mechanism ( 35 ) are set equal to each other.
- the low pressure side compression mechanism and the high pressure side compression mechanism are rotary compression mechanisms.
- the compressor ( 30 ) is so composed that the low pressure side compression mechanism ( 34 ) and the high pressure side compression mechanism ( 35 ) are connected to each other by means of the drive shaft ( 33 ).
- the volume ratio of the high pressure side compression mechanism ( 35 ) to the low pressure side compression mechanism ( 34 ) is set in the range between 0.8 and 1.3, both exclusive.
- the volume ratio over 0.8 reduces the pressure of the refrigerant in the gas-liquid separator ( 15 ) lower than its critical pressure. Accordingly, desired intermediate pressure gas injection can be performed in the refrigerant circuit ( 10 ) to increase the COP of the refrigerating apparatus in the present invention.
- the volume ratio below 1.3 invites no lowering of the compression efficiency accompanied by insufficiency of the amount of the refrigerant sucked in the high pressure side compression mechanism ( 35 ), thereby attaining two-stage compression of the refrigerant.
- the COP of the refrigerating apparatus can be increased further in the present invention.
- the volume ratio of the high pressure side compression mechanism ( 35 ) to the low pressure side compression mechanism ( 34 ) is set in the range between 0.9 and 1.1, both inclusive, in the second aspect of the present invention.
- the volume ratio of the high pressure side compression mechanism ( 35 ) to the low pressure side compression mechanism ( 34 ) is set in further optimum range.
- the COP of the refrigerating apparatus can be increased further in this aspect.
- the volume ratio of the low pressure side compression mechanism ( 34 ) to the volume ratio of the high pressure side compression mechanism ( 35 ) are set equal to each other. Accordingly, the low pressure side compression mechanism ( 34 ) and the high pressure side compression mechanism ( 35 ) can be structured according to the same specification in their compression mechanism, thereby contemplating cost reduction and simplification of the compressor ( 30 ).
- desired intermediate pressure gas injection is performed in the refrigerating apparatus including the compressor ( 30 ) including the two rotary compression mechanisms to thus increase the COP thereof.
- a refrigerating apparatus in accordance with one embodiment composes an air conditioner ( 1 ) performing indoor air conditioning.
- the air conditioner ( 1 ) is capable of heating and cooling the interior of a room.
- the air conditioner ( 1 ) includes an indoor unit ( 11 ) installed indoors and an outdoor unit ( 12 ) installed outdoors.
- the indoor unit ( 11 ) and the outdoor unit ( 12 ) are connected to each other by means of two communication pipes. Accordingly, a refrigerant circuit ( 10 ) is formed across the indoor unit ( 11 ) and the outdoor unit ( 12 ) in the air conditioner ( 1 ).
- CO 2 refrigerant is filled so that a two-stage compression/two-stage expansion refrigeration cycle is performed with the CO 2 refrigerant at high pressure utilized as that at its critical pressure.
- an indoor heat exchanger ( 13 ) is provided which is of fin-and-tube type.
- the indoor air blown by an indoor fan is heat-exchanged with the refrigerant.
- the outdoor unit ( 12 ) includes a compressor ( 30 ), which will be described later, an outdoor heat exchanger ( 14 ), and a gas-liquid separator ( 15 ).
- the outdoor heat exchanger ( 14 ) is of fin-and-tube type. In the outdoor heat exchanger ( 14 ), the outdoor air blown by an outdoor fan is heat-exchanged with the refrigerant.
- the gas-liquid separator ( 15 ) is composed of a cylindrical hermetic container.
- An inflow pipe ( 15a ) and a gas injection pipe ( 15b ) are connected to the gas-liquid separator ( 15 ) so as to pass through the top of the gas-liquid separator ( 15 ).
- the gas injection pipe ( 15b ) forms a flow path for introducing gas refrigerant at intermediate pressure into the compressor ( 30 ).
- An outflow pipe ( 15c ) is connected to the gas-liquid separator ( 15 ) so as to pass through the lower part of the gas-liquid separator ( 15 ).
- the intermediate-pressure refrigerant in a gas-liquid two-phase state is separated into gas refrigerant and liquid refrigerant.
- the outdoor unit ( 12 ) further includes a four-way switching valve ( 16 ), a bridge circuit ( 17 ), a first expansion valve ( 18 ), and a second expansion valve ( 19 ).
- the four-way switching valve ( 16 ) includes first to fourth ports.
- the first port is connected to a discharge pipe ( 41 ) of the compressor ( 30 )
- the second port is connected to the outdoor heat exchanger ( 14 )
- the third port is connected to the indoor heat exchanger ( 13 )
- the fourth port is connected to a suction pipe ( 42 ) of the compressor ( 30 ).
- the four-way switching valve ( 16 ) is exchangeable between a state (the state indicated by solid lines in FIG. 1 ) in which the first port and the second port communicate with each other while the third port and the fourth port communicate with each other and a state (the state indicated by broken lines in FIG. 1 ) in which the first port and the third port communicate with each other while the second port and the fourth port communicate with each other.
- the bridge circuit ( 17 ) is composed of four pipes in a bridge like combination and four check valves provided at the pipes.
- the check valves of the bridge circuit ( 17 ) allow the refrigerant to flow only in the directions indicated by the arrows in FIG. 1 .
- the first expansion valve ( 18 ) and the second expansion valve ( 19 ) are electronic expansion valves of which opening is adjustable.
- the first expansion valve ( 18 ) is provided in the piping on the inflow side of the gas-liquid separator ( 15 ) while the second expansion valve ( 19 ) is provided in the piping on the outflow side thereof.
- the compressor ( 30) is composed of a generally-called two-stage compression type compressor that compresses refrigerant in two stages by two compression mechanisms.
- the compressor ( 30 ) includes a cylindrical hermetic casing ( 31 ).
- An electric motor ( 32 ), a drive shaft ( 33 ), a first compression mechanism ( 34 ), and a second compression mechanism ( 35 ) are accommodated in the casing ( 31 ).
- the electric motor ( 32 ) is composed of a stator fixed on the inner peripheral face of the casing ( 31 ) and a rotor fixed on the outer peripheral face of the drive shaft ( 33 ).
- the drive shaft ( 33 ) is supported by a bearing so as to extend vertically.
- the drive shaft ( 33 ) is rotatable by being driven by the electric motor ( 32 ).
- the first compression mechanism ( 34 ) is arranged near the bottom of the casing ( 31 ) and serves as a low pressure side compression mechanism.
- the second compression mechanism ( 35 ) is arranged near the electric motor ( 32 ) and serves as a high pressure side compression mechanism.
- the first compression mechanism ( 34 ) and the second compression mechanism ( 35 ) are rotary swing type compression mechanisms. Pistons are accommodated in cylindrical cylinder chambers of the compression mechanisms ( 34 , 35 ). Each piston is connected to the drive shaft ( 33 ) so as to be eccentric from the axis of the drive shaft ( 33 ). Accordingly, when the drive shaft ( 33 ) is rotated, each piston of the compression mechanisms ( 34 , 35 ) rotates with their centers being eccentric with respect to the drive shaft ( 33 ). Further, the pistons of the compression mechanisms ( 34 , 35 ) are connected to the drive shaft ( 33 ) so as to be phase-sifted by 180° from each other. This offsets the centrifugal forces of the pistons in operation, thereby suppressing vibration and variation in torque load.
- the first compression mechanism ( 34 ) is connected on the suction side thereof to the suction pipe ( 42 ) and is connected on the discharge side thereof to one end of an intermediate communication pipe ( 43 ).
- the second compression mechanism ( 35 ) is connected on the suction side thereof to the other end of the intermediate communication pipe ( 43 ) and is connected on the discharge side thereof to the discharge pipe ( 41 ).
- the intermediate communication pipe ( 43 ) forms a flow path for introducing the refrigerant after being compressed in the first compression mechanism ( 34 ) into the suction side of the second compression mechanism ( 35 ).
- the outflow end of the gas injection pipe ( 15b ) is connected to a U-shape curved part of the intermediate communication pipe (43).
- the ratio (volume ratio V2/V1) of the displacement volume V2 of the second compression mechanism ( 35 ) to that V1 of the first compression mechanism ( 34 ) are set in the range between 0.8 and 1.3, both exclusive. This increases the COP (coefficient of performance) of the air conditioner ( 1 ).
- the relationship between the volume ratio V2/V1 and the COP will be described later in detail.
- the air conditioner ( 1 ) is capable of performing the following heating and cooling operations.
- the four-way switching valve ( 16 ) is set as shown in FIG. 2 .
- Each opening of the first expansion valve ( 18 ) and the second expansion valve ( 19 ) is adjusted appropriately.
- the refrigerant compressed up to its critical pressure is discharged from the compressor ( 30 ).
- the refrigerant passes through the four-way switching valve ( 16 ) and then flows into the indoor heat exchanger ( 13 ).
- the indoor heat exchanger ( 13 ) the refrigerant releases heat to the indoor air. This means indoor heating.
- the refrigerant flowing out from the indoor heat exchanger ( 13 ) passes through the first expansion valve ( 18 ) to be reduced in pressure up to intermediate pressure and flows then into the gas-liquid separator ( 15 ).
- the intermediate-pressure refrigerant in the gas-liquid two-phase state is retained. This refrigerant is separated into the gas refrigerant and the liquid refrigerant in the gas-liquid separator ( 15 ).
- the gas refrigerant retained in the upper part of the gas-liquid separator ( 15 ) flows into the gas injection pipe ( 15b ).
- the liquid refrigerant retained in the lower part of the gas-liquid separator ( 15 ) passes through the second expansion valve ( 19 ) to be reduced in pressure up to low pressure and flows then into the outdoor heat exchanger ( 14 ).
- the refrigerant absorbs heat from the outdoor air to be evaporated. The refrigerant flowing out from the outdoor heat exchanger ( 14 ) is sucked into the compressor ( 30 ).
- the refrigerant is first sucked into the first compression mechanism ( 34 ) through the suction pipe ( 42 ).
- the refrigerant is compressed up to intermediate pressure in the first compression mechanism ( 34 ).
- the refrigerant discharged from the first compression mechanism ( 34 ) flows into the intermediate communication pipe ( 43 ).
- This discharged refrigerant is mixed with the gas refrigerant flowing out from the gas injection pipe ( 15b ).
- the refrigerant flowing out from the intermediate communication pipe ( 43 ) is sucked into the second compression mechanism ( 35 ).
- the refrigerant is compressed up to its critical pressure.
- the four-way switching valve ( 16 ) is set as shown in FIG. 3 .
- Each opening of the first expansion valve ( 18 ) and the second expansion valve ( 19 ) is adjusted appropriately.
- the refrigerant compressed up to its critical pressure is discharged from the compressor ( 30 ).
- the refrigerant passes through the four-way switching valve ( 16 ) and flows then into the outdoor heat exchanger ( 14 ).
- the refrigerant release heat to the outdoor air.
- the refrigerant flowing out from the outdoor heat exchanger ( 14 ) passes through the first expansion valve ( 18 ) to be reduced in pressure up to intermediate pressure and flows then into the gas-liquid separator ( 15 ).
- the intermediate-pressure refrigerant in the gas-liquid two-phase state is retained. This refrigerant is separated into the gas refrigerant and the liquid refrigerant in the gas-liquid separator ( 15 ).
- the gas refrigerant retained in the upper part of the gas-liquid separator ( 15 ) flows into the gas injection pipe ( 15b ).
- the liquid refrigerant retained in the lower part of the gas-liquid separator ( 15 ) passes through the second expansion valve ( 19 ) to be reduced in pressure up to low pressure and flows then into the indoor heat exchanger ( 13 ).
- the indoor heat exchanger ( 13 ) the refrigerant absorbs heat from the indoor air to be evaporated. This means indoor cooling.
- the refrigerant flowing out from the indoor heat exchanger ( 13 ) is sucked into the compressor ( 30 ).
- the refrigerant is first sucked into the first compression mechanism ( 34 ) through the suction pipe ( 42 ).
- the refrigerant is compressed up to intermediate pressure in the first compression mechanism ( 34 ).
- the refrigerant discharged from the first compression mechanism ( 34 ) flows into the intermediate communication pipe ( 43 ).
- This discharged refrigerant is mixed with the gas refrigerant flowing out from the gas injection pipe ( 15b ).
- the refrigerant flowing out from the intermediate communication pipe ( 43 ) is sucked into the second compression mechanism ( 35 ).
- the refrigerant is compressed up to its critical pressure.
- the generally-called intermediate pressure gas injection is performed by mixing the gas refrigerant separated in the gas-liquid separator ( 15 ) with the intermediate-pressure refrigerant in the compressor ( 30 ).
- this air conditioner ( 1 ) the temperature of the refrigerant discharged from the first compression mechanism ( 34 ) is lowered and the power required for driving the compressor ( 30 ) is reduced, thereby increasing the COP.
- the volume ratio (V2/V1) of the volume V2 of the second compression mechanism ( 35 ) to that V1 of the first compression mechanism ( 34 ) is set in the optimum range to allow the pressure of the intermediate-pressure refrigerant in the gas-liquid separator ( 15 ) to be lower than its critical pressure, thereby enabling desired intermediate pressure gas injection.
- FIG. 4 shows the result obtained by examining the above relationship between the volume ratio (V2/V1) and the COP.
- the COPs in the heating operation and the cooling operation are obtained in air conditioners having volume ratios (V2/V1) different form each other.
- each COP of the air conditioners is obtained in the heating operation under a temperature condition in the outdoor temperature range (from -10°C to 15°C) in general winter season and in the cooling operation under a temperature condition in the outdoor temperature range (from 25°C to 35°C) in general summer season.
- the "COP ratio" herein means a relative evaluation of each COP of the air conditioners with various volume ratios with reference to, as a standard, the lowest COP of an air condition with a volume ratio of 0.65 (for example, the COP in the heating operation at an outdoor temperature of 15°C and the COP in the cooling operation at an outdoor temperature of 25°C).
- the air conditioners with volume ratios of 0.8 or smaller have low COPs in the heating operation and the cooling operation. This is because: with a volume ratio of 0.8 or smaller, the displacement volume of the second compression mechanism ( 35 ) is too small relative to that of the first compression mechanism ( 34 ), so that the refrigerant in the gas-liquid separator ( 15 ) exceeds its critical pressure to inhibit separation of the gas refrigerant from the refrigerant in the gas-liquid separator ( 15 ), thereby inhibiting desired intermediate pressure gas injection.
- the refrigerant in the gas-liquid separator ( 15 ) can be allowed to reach its subcritical pressure to leads to separation of the gas refrigerant from the refrigerant in the gas-liquid separator ( 15 ).
- the air conditioner with a volume ratio greater than 0.8 can perform desired intermediate pressure gas injection, thereby attaining a high COP.
- the air conditioner with a volume ratio of 1.3 has low COPs in the heating operation and in the cooling operation under a low outdoor temperature condition. This is because: with a volume ratio of 1.3 or greater, the displacement volume of the second compression mechanism ( 35 ) is too great relative to that of the first compression mechanism ( 34 ), so that an insufficient amount of the refrigerant sucked in the second compression mechanism ( 35) is secured. In other words, with a volume ratio of 1.3 or greater, the refrigerant is compressed in two stages inefficiently to increase the power required for driving the compressor ( 30 ) with a result of lowering of the COP. In reverse, the air conditioner with a volume ratio smaller than 1.3 can perform relatively efficient two-stage compression of the refrigerant to attain a high COP.
- each COP in the cooling operation and in the heating operation is high when the volume ratio is not within the range between 0.9 and 1.1, both inclusive.
- the volume ratio (V2/V1) of the volume V2 of the second compression mechanism ( 35 ) to that V1 of the first compression mechanism ( 34 ) is preferably within the range between 0.9 and 1.1, both inclusive.
- the volume ratio is set at 1.0, a high COP can be attained in each of the cooling operation and the heating operation.
- the volume ratio of the second compression mechanism ( 35 ) to the first compression mechanism ( 34 ) is set within the range between 0.8 and 1.3, both exclusive.
- the volume ratio is set greater than 0.8, the pressure of the refrigerant in the gas-liquid separator ( 15 ) is allowed to be smaller than its critical pressure. This attains desired intermediate pressure gas injection in the refrigerant circuit ( 10 ) to increase the COP of the air conditioner ( 1 ) in the present embodiment.
- the volume ratio is set smaller than 1.3, the refrigerant can be compressed in two stages with no lowering of the compression efficiency invited, which is accompanied by an insufficient amount of the refrigerant sucked in the second compression mechanism ( 35 ).
- the COP of the air conditioner ( 1 ) can be increased further.
- volume ratio of the second compression mechanism ( 35 ) to the first compression mechanism ( 34 ) is set within the range between 0.9 and 1.1, both inclusive, a high COP can be obtained as shown in FIG. 4 .
- the compression mechanisms can be structured according to the same specification in their compression mechanism. Hence, the compressor ( 30 ) can be manufactured comparatively easily at low cost.
- the above embodiment may have any of the following structure.
- the discharge side of the low pressure side compression mechanism ( 34 ) and the suction side of the high pressure side compression mechanism ( 35 ) are connected by means of the intermediate communication pipe ( 43 ), and the outflow end of the gas injection pipe ( 15b ) is connected to the intermediate communication pipe ( 43 ).
- the intermediate-pressure gas refrigerant may be introduced into the casing ( 31 ) in the case where the compressor ( 30 ) is a generally-called intermediate pressure dome type compressor by filling the casing ( 31 ) of the compressor ( 30 ) with the refrigerant discharged from, for example, the low pressure side compression mechanism ( 34 ).
- the low pressure side compression mechanism ( 34 ) and the high pressure side compression mechanism ( 35 ) are composed of swing type compression mechanisms in the above embodiment but may be rotary piston type compression mechanisms or compression mechanisms each composed of an anchor tooth and a movable tooth (of scroll type, for example).
- the present invention is useful in refrigerating apparatuses including a refrigerant circuit including a gas-liquid separator for performing two-stage compression/two-state expansion refrigeration cycle utilizing CO 2 refrigerant at high pressure as that at its critical pressure.
Abstract
Description
- The present invention relates to a refrigerating apparatus including a refrigerant circuit including a gas-liquid separator for performing two-stage compression/two-stage expansion refrigeration cycle utilizing of CO2 refrigerant at high pressure as that at its critical pressure.
- Conventionally, refrigerating apparatuses including a refrigerant circuit are widely applied to air conditioners and the like.
- For example,
Patent Document 1 discloses an air conditioner including a refrigerant circuit including a gas-liquid separator for performing a two-stage compression/two-stage expansion refrigeration cycle. - The refrigerant circuit of this air conditioner includes a compressor, a first heat exchanger, a first expansion valve, a gas-liquid separator, a second expansion valve, and a second heat exchanger. The compressor is of two-stage compression type in which a low pressure side compression mechanism and a high pressure side compression mechanism are connected by means of a drive shaft. The gas-liquid separator is so composed to separate intermediate-pressure refrigerant in a gas-liquid two-phase state into liquid refrigerant and gas refrigerant.
- In a cooling operation of the air conditioner, refrigerant discharged form the compressor flows into the first heat exchanger. In the first heat exchanger, the refrigerant release heat to the air. The refrigerant having passed through the first heat exchanger is reduced in pressure up to intermediate pressure through the first expansion valve and flows then into the gas-liquid separator. In the gas-liquid separator, the intermediate-pressure refrigerant in the gas-liquid two-phase state is separated into the gas refrigerant and the liquid refrigerant. The liquid refrigerant thus separated in the gas-liquid separator is reduced in pressure up to low pressure through the second expansion valve and flows then into the second heat exchanger. In the second heat exchanger, the refrigerant absorbs heat from the air to be evaporated. In this way, the indoor cooling is performed.
- The refrigerant having passed through the second heat exchanger is sucked into the compressor to be compressed up to intermediate pressure in the low pressure side compression mechanism. The refrigerant discharged from the low pressure side compression mechanism is mixed with the gas refrigerant separated in the gas-liquid separator. In other words, the air conditioner performs generally-called intermediate pressure gas injection in which the intermediate-pressure gas refrigerant is mixed with the refrigerant discharged from the low pressure side compression mechanism. Thereafter, the thus mixed refrigerant is compressed up to high pressure in the high pressure side compression mechanism and is then discharged from the compressor again.
- As described above, the air conditioner of
Patent Document 1 performs the intermediate pressure gas injection to lower the temperature of the refrigerant discharged from the compressor for reducing the power required for driving the compressor, thereby increasing the COP (coefficient of performance) of the air conditioner. -
Patent Document 2 discloses an air conditioner in which the aforementioned intermediate pressure gas injection is performed with CO2 refrigerant filled in a refrigerant circuit. This air conditioner performs a generally-called supercritical cycle in which the refrigerant discharged from the compressor is compressed over its critical pressure. - Patent Document 1: Japanese Unexamined Patent Application Publication
7-110167 - Patent Document 2: Japanese Unexamined Patent Application Publication
2001-241797 - In the air conditioner as disclosed in
Patent Document 1, the volume (displacement volume) of each compression mechanism of the two-stage compression type compressor is so designed to attain efficient two-stage compression. On the other hand, in the supercritical cycle using CO2 as the refrigerant of such an air conditioner, the refrigerant after being compressed up to its supercritical pressure and releasing heat in an heat exchanger may be at the supercritical pressure yet in the gas-liquid separator. The refrigerant at supercritical pressure (in the critical state) in the gas-liquid separator is difficult to be separated into the gas refrigerant and the liquid refrigerant. This inhibits sending of only the gas refrigerant to the intermediate-pressure refrigerant in the compressor to inhibit the aforementioned intermediate pressure gas injection. Accordingly, desired effects by the intermediate pressure gas injection cannot be attained to invite lowering of the COP of the air conditioner. - The present invention has been made in view of the foregoing and has its object of enabling operation at an optimal COP in a refrigerating apparatus performing two-stage compression/two-stage expansion refrigeration cycle using CO2 refrigerant.
- A first aspect of the present invention premises a refrigerating apparatus including a refrigerant circuit for performing a two-stage compression/two-stage expansion refrigeration cycle in which CO2 refrigerant at high pressure is utilized as that at its critical pressure, the refrigerant circuit including: a compressor including a low pressure side compression mechanism and a high pressure side compression mechanism connected to each other by means of a drive shaft; and a gas-liquid separator for separating refrigerant at intermediate pressure into gas refrigerant and liquid refrigerant. In this refrigerating apparatus, a volume ratio of a displacement volume of the high pressure side compression mechanism to that of the low pressure side compression mechanism falls in a range between 0.8 and 1.3, both exclusive.
- The refrigerant circuit (10) in the first aspect is filled with CO2 refrigerant. Further, the compressor (30) including the low pressure side compression mechanism (34) and the high pressure side compression mechanism (35) is provided in the refrigerant circuit (10). In the refrigerant circuit (10), the following two-stage compression/two-stage expansion refrigeration cycle is performed.
- The refrigerant compressed up to its critical pressure in the high pressure side compression mechanism (35) releases heat in, for example, an indoor heat exchanger, is reduced in pressure up to intermediate pressure, and flows then into the gas-liquid separator (15). In the gas-liquid separator (15), the intermediate-pressure refrigerant is separated into the gas refrigerant and the liquid refrigerant. The liquid refrigerant is reduced in pressure up to low pressure, is evaporated in, for example, an outdoor heat exchanger, and is then sucked into the low pressure side compression mechanism (34). This refrigerant is compressed up to intermediate pressure in the low pressure side compression mechanism (34). Then, the gas refrigerant separated in the liquid-gas separator (15) is introduced into this refrigerant. Thus, the aforementioned intermediate pressure gas injection is performed. Thereafter, the refrigerant is compressed up to high pressure (critical pressure) in the high pressure side compression mechanism (35).
- In the case where the two-stage compression/two-stage expansion refrigeration cycle is performed with the use of CO2 refrigerant in this way, the intermediate-pressure refrigerant in the gas-liquid separator may reach its critical pressure in the conventional refrigerating apparatus. If so, the refrigerant in the gas-liquid separator cannot be separated into the gas refrigerant and the liquid refrigerant to inhibit desired intermediate pressure gas injection. To tackle this problem, the volume ratio of the high pressure side compression mechanism (35) to the low pressure side compression mechanism (34) is set greater than 0.8. When the volume ratio is set equal to or smaller than 0.8, the displacement volume of the high pressure side compression mechanism (35) becomes relatively smaller than that of the low pressure side compression mechanism (34), thereby increasing the pressure of the intermediate-pressure refrigerant to invite an increase in pressure of the refrigerant in the gas-liquid separator (15) over its critical pressure. In contrast, in this aspect of the present invention, in which the volume ratio is set greater than 0.8, the refrigerant in the gas-liquid separator (15) can be suppressed at its subcritical pressure. Hence, in this aspect, the refrigerant in the gas-liquid separator (15) is definitely separated into the gas refrigerant and the liquid refrigerant to attain desired effects by the intermediate pressure gas injection.
- When assumed that the volume ratio is set equal to or greater than 1.3, the displacement volume of the high pressure side compression mechanism (35) is relatively greater than that of the low pressure side compression mechanism (34). As a result, the amount of the refrigerant sucked in the high pressure side compression mechanism (35) is secured insufficiently to invite lowering of the compression efficiency of the compressor (30). In contrast, this aspect of the present invention sets the volume ratio to be smaller than 1.3 to secure a sufficient amount of the refrigerant sucked in the high pressure side compression mechanism (35), with a result that the refrigerant can be compressed in two stages efficiently.
- Referring to a second aspect of the present invention, in the first aspect, the volume ratio falls in a range between 0.9 and 1.1, both inclusive.
- In the second aspect of the present invention, the volume ratio of the displacement volume of the high pressure side compression mechanism (35) to that of the low pressure side compression mechanism (34) is set in the range between 0.9 and 1.1, both inclusive. The volume ratio exceeding 0.9 definitely makes the refrigerant in the gas-liquid separator (15) reach its critical pressure. While, the volume ratio not exceeding 1.1 attains further efficient two-stage compression of the refrigerant.
- Referring to a third aspect of the present invention, in the second aspect, the volume ratio is 1.0.
- In the third aspect of the present invention, the volume of the low pressure side compression mechanism (34) and that of the high pressure side compression mechanism (35) are set equal to each other.
- Referring to a fourth aspect of the present invention, in any one of the first to third aspects, the low pressure side compression mechanism and the high pressure side compression mechanism are rotary compression mechanisms.
- In the fourth aspect of the present invention, the compressor (30) is so composed that the low pressure side compression mechanism (34) and the high pressure side compression mechanism (35) are connected to each other by means of the drive shaft (33).
- In the present invention, the volume ratio of the high pressure side compression mechanism (35) to the low pressure side compression mechanism (34) is set in the range between 0.8 and 1.3, both exclusive. The volume ratio over 0.8 reduces the pressure of the refrigerant in the gas-liquid separator (15) lower than its critical pressure. Accordingly, desired intermediate pressure gas injection can be performed in the refrigerant circuit (10) to increase the COP of the refrigerating apparatus in the present invention. On the other hand, the volume ratio below 1.3 invites no lowering of the compression efficiency accompanied by insufficiency of the amount of the refrigerant sucked in the high pressure side compression mechanism (35), thereby attaining two-stage compression of the refrigerant. Hence, the COP of the refrigerating apparatus can be increased further in the present invention.
- Particularly, the volume ratio of the high pressure side compression mechanism (35) to the low pressure side compression mechanism (34) is set in the range between 0.9 and 1.1, both inclusive, in the second aspect of the present invention. In other words, the volume ratio of the high pressure side compression mechanism (35) to the low pressure side compression mechanism (34) is set in further optimum range. Hence, the COP of the refrigerating apparatus can be increased further in this aspect.
- In the third aspect of the present invention, the volume ratio of the low pressure side compression mechanism (34) to the volume ratio of the high pressure side compression mechanism (35) are set equal to each other. Accordingly, the low pressure side compression mechanism (34) and the high pressure side compression mechanism (35) can be structured according to the same specification in their compression mechanism, thereby contemplating cost reduction and simplification of the compressor (30).
- According to the fourth aspect of the present invention, desired intermediate pressure gas injection is performed in the refrigerating apparatus including the compressor (30) including the two rotary compression mechanisms to thus increase the COP thereof.
-
- [
FIG. 1] FIG. 1 is a piping system diagram of a refrigerant circuit in an air conditioner in accordance with one embodiment. - [
FIG. 2] FIG. 2 is a piping system diagram for explaining refrigerant flow in a heating operation of the air conditioner. - [
FIG. 3] FIG. 3 is a piping system diagram for explaining refrigerant flow in a cooling operation of the air conditioner. - [
FIG. 4] FIG. 4 is a graph showing the relationship between the COP and the volume ratio of a high pressure side compression mechanism to a low pressure side compression mechanism. -
- 1 air conditioner
- 10 refrigerant circuit
- 30 compressor
- 34 first compression mechanism (low pressure side compression mechanism)
- 35 second compression mechanism (high pressure side compression mechanism)
- A refrigerating apparatus in accordance with one embodiment composes an air conditioner (1) performing indoor air conditioning. The air conditioner (1) is capable of heating and cooling the interior of a room.
- The air conditioner (1) includes an indoor unit (11) installed indoors and an outdoor unit (12) installed outdoors. The indoor unit (11) and the outdoor unit (12) are connected to each other by means of two communication pipes. Accordingly, a refrigerant circuit (10) is formed across the indoor unit (11) and the outdoor unit (12) in the air conditioner (1). In the refrigerant circuit (10), CO2 refrigerant is filled so that a two-stage compression/two-stage expansion refrigeration cycle is performed with the CO2 refrigerant at high pressure utilized as that at its critical pressure.
- In the indoor unit (11), an indoor heat exchanger (13) is provided which is of fin-and-tube type. In the indoor heat exchanger (13), the indoor air blown by an indoor fan is heat-exchanged with the refrigerant.
- The outdoor unit (12) includes a compressor (30), which will be described later, an outdoor heat exchanger (14), and a gas-liquid separator (15).
- The outdoor heat exchanger (14) is of fin-and-tube type. In the outdoor heat exchanger (14), the outdoor air blown by an outdoor fan is heat-exchanged with the refrigerant.
- The gas-liquid separator (15) is composed of a cylindrical hermetic container. An inflow pipe (15a) and a gas injection pipe (15b) are connected to the gas-liquid separator (15) so as to pass through the top of the gas-liquid separator (15). The gas injection pipe (15b) forms a flow path for introducing gas refrigerant at intermediate pressure into the compressor (30). An outflow pipe (15c) is connected to the gas-liquid separator (15) so as to pass through the lower part of the gas-liquid separator (15). In the gas-liquid separator (15), the intermediate-pressure refrigerant in a gas-liquid two-phase state is separated into gas refrigerant and liquid refrigerant.
- The outdoor unit (12) further includes a four-way switching valve (16), a bridge circuit (17), a first expansion valve (18), and a second expansion valve (19).
- The four-way switching valve (16) includes first to fourth ports. In the four-way switching valve (16), the first port is connected to a discharge pipe (41) of the compressor (30), the second port is connected to the outdoor heat exchanger (14), the third port is connected to the indoor heat exchanger (13), and the fourth port is connected to a suction pipe (42) of the compressor (30). The four-way switching valve (16) is exchangeable between a state (the state indicated by solid lines in
FIG. 1 ) in which the first port and the second port communicate with each other while the third port and the fourth port communicate with each other and a state (the state indicated by broken lines inFIG. 1 ) in which the first port and the third port communicate with each other while the second port and the fourth port communicate with each other. - The bridge circuit (17) is composed of four pipes in a bridge like combination and four check valves provided at the pipes. The check valves of the bridge circuit (17) allow the refrigerant to flow only in the directions indicated by the arrows in
FIG. 1 . - The first expansion valve (18) and the second expansion valve (19) are electronic expansion valves of which opening is adjustable. The first expansion valve (18) is provided in the piping on the inflow side of the gas-liquid separator (15) while the second expansion valve (19) is provided in the piping on the outflow side thereof.
- As shown in
FIG. 2 , the compressor (30) is composed of a generally-called two-stage compression type compressor that compresses refrigerant in two stages by two compression mechanisms. The compressor (30) includes a cylindrical hermetic casing (31). An electric motor (32), a drive shaft (33), a first compression mechanism (34), and a second compression mechanism (35) are accommodated in the casing (31). - The electric motor (32) is composed of a stator fixed on the inner peripheral face of the casing (31) and a rotor fixed on the outer peripheral face of the drive shaft (33). The drive shaft (33) is supported by a bearing so as to extend vertically. The drive shaft (33) is rotatable by being driven by the electric motor (32).
- The first compression mechanism (34) is arranged near the bottom of the casing (31) and serves as a low pressure side compression mechanism. On the other hand, the second compression mechanism (35) is arranged near the electric motor (32) and serves as a high pressure side compression mechanism.
- The first compression mechanism (34) and the second compression mechanism (35) are rotary swing type compression mechanisms. Pistons are accommodated in cylindrical cylinder chambers of the compression mechanisms (34, 35). Each piston is connected to the drive shaft (33) so as to be eccentric from the axis of the drive shaft (33). Accordingly, when the drive shaft (33) is rotated, each piston of the compression mechanisms (34, 35) rotates with their centers being eccentric with respect to the drive shaft (33). Further, the pistons of the compression mechanisms (34, 35) are connected to the drive shaft (33) so as to be phase-sifted by 180° from each other. This offsets the centrifugal forces of the pistons in operation, thereby suppressing vibration and variation in torque load.
- The first compression mechanism (34) is connected on the suction side thereof to the suction pipe (42) and is connected on the discharge side thereof to one end of an intermediate communication pipe (43). The second compression mechanism (35) is connected on the suction side thereof to the other end of the intermediate communication pipe (43) and is connected on the discharge side thereof to the discharge pipe (41).
- The intermediate communication pipe (43) forms a flow path for introducing the refrigerant after being compressed in the first compression mechanism (34) into the suction side of the second compression mechanism (35). The outflow end of the gas injection pipe (15b) is connected to a U-shape curved part of the intermediate communication pipe (43).
- In the air conditioner (1) of the present embodiment, the ratio (volume ratio V2/V1) of the displacement volume V2 of the second compression mechanism (35) to that V1 of the first compression mechanism (34) are set in the range between 0.8 and 1.3, both exclusive. This increases the COP (coefficient of performance) of the air conditioner (1). The relationship between the volume ratio V2/V1 and the COP will be described later in detail.
- Driving operations of the air conditioner (1) in accordance with the present embodiment will be described. The air conditioner (1) is capable of performing the following heating and cooling operations.
- In the heating operation, the four-way switching valve (16) is set as shown in
FIG. 2 . Each opening of the first expansion valve (18) and the second expansion valve (19) is adjusted appropriately. - The refrigerant compressed up to its critical pressure is discharged from the compressor (30). The refrigerant passes through the four-way switching valve (16) and then flows into the indoor heat exchanger (13). In the indoor heat exchanger (13), the refrigerant releases heat to the indoor air. This means indoor heating. The refrigerant flowing out from the indoor heat exchanger (13) passes through the first expansion valve (18) to be reduced in pressure up to intermediate pressure and flows then into the gas-liquid separator (15).
- In the gas-liquid separator (15), the intermediate-pressure refrigerant in the gas-liquid two-phase state is retained. This refrigerant is separated into the gas refrigerant and the liquid refrigerant in the gas-liquid separator (15). The gas refrigerant retained in the upper part of the gas-liquid separator (15) flows into the gas injection pipe (15b). On the other hand, the liquid refrigerant retained in the lower part of the gas-liquid separator (15) passes through the second expansion valve (19) to be reduced in pressure up to low pressure and flows then into the outdoor heat exchanger (14). In the outdoor heat exchanger (14), the refrigerant absorbs heat from the outdoor air to be evaporated. The refrigerant flowing out from the outdoor heat exchanger (14) is sucked into the compressor (30).
- In the compressor (30), the refrigerant is first sucked into the first compression mechanism (34) through the suction pipe (42). The refrigerant is compressed up to intermediate pressure in the first compression mechanism (34). The refrigerant discharged from the first compression mechanism (34) flows into the intermediate communication pipe (43). This discharged refrigerant is mixed with the gas refrigerant flowing out from the gas injection pipe (15b). As a result, the temperature of the refrigerant discharged from the first compression mechanism (34) lowers. The refrigerant flowing out from the intermediate communication pipe (43) is sucked into the second compression mechanism (35). In the second compression mechanism (35), the refrigerant is compressed up to its critical pressure.
- In the cooling operation, the four-way switching valve (16) is set as shown in
FIG. 3 . Each opening of the first expansion valve (18) and the second expansion valve (19) is adjusted appropriately. - The refrigerant compressed up to its critical pressure is discharged from the compressor (30). The refrigerant passes through the four-way switching valve (16) and flows then into the outdoor heat exchanger (14). In the outdoor heat exchanger (14), the refrigerant release heat to the outdoor air. The refrigerant flowing out from the outdoor heat exchanger (14) passes through the first expansion valve (18) to be reduced in pressure up to intermediate pressure and flows then into the gas-liquid separator (15).
- In the gas-liquid separator (15), the intermediate-pressure refrigerant in the gas-liquid two-phase state is retained. This refrigerant is separated into the gas refrigerant and the liquid refrigerant in the gas-liquid separator (15). The gas refrigerant retained in the upper part of the gas-liquid separator (15) flows into the gas injection pipe (15b). On the other hand, the liquid refrigerant retained in the lower part of the gas-liquid separator (15) passes through the second expansion valve (19) to be reduced in pressure up to low pressure and flows then into the indoor heat exchanger (13). In the indoor heat exchanger (13), the refrigerant absorbs heat from the indoor air to be evaporated. This means indoor cooling. The refrigerant flowing out from the indoor heat exchanger (13) is sucked into the compressor (30).
- In the compressor (30), the refrigerant is first sucked into the first compression mechanism (34) through the suction pipe (42). The refrigerant is compressed up to intermediate pressure in the first compression mechanism (34). The refrigerant discharged from the first compression mechanism (34) flows into the intermediate communication pipe (43). This discharged refrigerant is mixed with the gas refrigerant flowing out from the gas injection pipe (15b). As a result, the temperature of the refrigerant discharged from the first compression mechanism (34) lowers. The refrigerant flowing out from the intermediate communication pipe (43) is sucked into the second compression mechanism (35). In the second compression mechanism (35), the refrigerant is compressed up to its critical pressure.
- As described above, in the heating operation and the cooling operation of the air conditioner (1) of the present embodiment, the generally-called intermediate pressure gas injection is performed by mixing the gas refrigerant separated in the gas-liquid separator (15) with the intermediate-pressure refrigerant in the compressor (30). As a result, in this air conditioner (1), the temperature of the refrigerant discharged from the first compression mechanism (34) is lowered and the power required for driving the compressor (30) is reduced, thereby increasing the COP.
- In the refrigerant circuit (10) of the air conditioner (1), a generally-called supercritical cycle is performed by compressing the high-pressure refrigerant up to its critical pressure. Therefore, if the intermediate-pressure refrigerant in the gas-liquid separator (15) reaches its critical pressure, it becomes difficult to separate the refrigerant in the gas-liquid separator (15) into the gas refrigerant and the liquid refrigerant, thereby inhibiting performance of the intermediate pressure gas injection. To tackle this problem, in the present invention, the volume ratio (V2/V1) of the volume V2 of the second compression mechanism (35) to that V1 of the first compression mechanism (34) is set in the optimum range to allow the pressure of the intermediate-pressure refrigerant in the gas-liquid separator (15) to be lower than its critical pressure, thereby enabling desired intermediate pressure gas injection.
-
FIG. 4 shows the result obtained by examining the above relationship between the volume ratio (V2/V1) and the COP. InFIG. 4 , the COPs in the heating operation and the cooling operation are obtained in air conditioners having volume ratios (V2/V1) different form each other. Specifically, inFIG. 4 , each COP of the air conditioners is obtained in the heating operation under a temperature condition in the outdoor temperature range (from -10°C to 15°C) in general winter season and in the cooling operation under a temperature condition in the outdoor temperature range (from 25°C to 35°C) in general summer season. The "COP ratio" herein means a relative evaluation of each COP of the air conditioners with various volume ratios with reference to, as a standard, the lowest COP of an air condition with a volume ratio of 0.65 (for example, the COP in the heating operation at an outdoor temperature of 15°C and the COP in the cooling operation at an outdoor temperature of 25°C). - As shown in
FIG. 4 , the air conditioners with volume ratios of 0.8 or smaller have low COPs in the heating operation and the cooling operation. This is because: with a volume ratio of 0.8 or smaller, the displacement volume of the second compression mechanism (35) is too small relative to that of the first compression mechanism (34), so that the refrigerant in the gas-liquid separator (15) exceeds its critical pressure to inhibit separation of the gas refrigerant from the refrigerant in the gas-liquid separator (15), thereby inhibiting desired intermediate pressure gas injection. In contrast, with a volume ratio greater than 0.8, the refrigerant in the gas-liquid separator (15) can be allowed to reach its subcritical pressure to leads to separation of the gas refrigerant from the refrigerant in the gas-liquid separator (15). Thus, the air conditioner with a volume ratio greater than 0.8 can perform desired intermediate pressure gas injection, thereby attaining a high COP. - On the other hand, the air conditioner with a volume ratio of 1.3 has low COPs in the heating operation and in the cooling operation under a low outdoor temperature condition. This is because: with a volume ratio of 1.3 or greater, the displacement volume of the second compression mechanism (35) is too great relative to that of the first compression mechanism (34), so that an insufficient amount of the refrigerant sucked in the second compression mechanism (35) is secured. In other words, with a volume ratio of 1.3 or greater, the refrigerant is compressed in two stages inefficiently to increase the power required for driving the compressor (30) with a result of lowering of the COP. In reverse, the air conditioner with a volume ratio smaller than 1.3 can perform relatively efficient two-stage compression of the refrigerant to attain a high COP.
- In addition, as shown in
FIG. 4 , each COP in the cooling operation and in the heating operation is high when the volume ratio is not within the range between 0.9 and 1.1, both inclusive. Accordingly, the volume ratio (V2/V1) of the volume V2 of the second compression mechanism (35) to that V1 of the first compression mechanism (34) is preferably within the range between 0.9 and 1.1, both inclusive. Particularly, when the volume ratio is set at 1.0, a high COP can be attained in each of the cooling operation and the heating operation. - In the above embodiment, the volume ratio of the second compression mechanism (35) to the first compression mechanism (34) is set within the range between 0.8 and 1.3, both exclusive. When the volume ratio is set greater than 0.8, the pressure of the refrigerant in the gas-liquid separator (15) is allowed to be smaller than its critical pressure. This attains desired intermediate pressure gas injection in the refrigerant circuit (10) to increase the COP of the air conditioner (1) in the present embodiment. Further, when the volume ratio is set smaller than 1.3, the refrigerant can be compressed in two stages with no lowering of the compression efficiency invited, which is accompanied by an insufficient amount of the refrigerant sucked in the second compression mechanism (35). Hence, according to the above embodiment, the COP of the air conditioner (1) can be increased further.
- Particularly, when the volume ratio of the second compression mechanism (35) to the first compression mechanism (34) is set within the range between 0.9 and 1.1, both inclusive, a high COP can be obtained as shown in
FIG. 4 . - Further, when the volumes of the first compression mechanism (34) and the second compression mechanism (35) are set equal to each other (volume ratio is 1.0), a high COP can be obtained in each of the cooling operation and the heating operation. In addition, when the volumes of the first compression mechanism (34) and the second compression mechanism (35) are set equal to each other, the compression mechanisms can be structured according to the same specification in their compression mechanism. Hence, the compressor (30) can be manufactured comparatively easily at low cost.
- The above embodiment may have any of the following structure.
- In the above embodiment, the discharge side of the low pressure side compression mechanism (34) and the suction side of the high pressure side compression mechanism (35) are connected by means of the intermediate communication pipe (43), and the outflow end of the gas injection pipe (15b) is connected to the intermediate communication pipe (43). However; the intermediate-pressure gas refrigerant may be introduced into the casing (31) in the case where the compressor (30) is a generally-called intermediate pressure dome type compressor by filling the casing (31) of the compressor (30) with the refrigerant discharged from, for example, the low pressure side compression mechanism (34).
- Further, the low pressure side compression mechanism (34) and the high pressure side compression mechanism (35) are composed of swing type compression mechanisms in the above embodiment but may be rotary piston type compression mechanisms or compression mechanisms each composed of an anchor tooth and a movable tooth (of scroll type, for example).
- It should be noted that the above embodiments are mere essentially preferable examples and is not intended to limit the present invention, applicable objects, and usable range.
- As described above, the present invention is useful in refrigerating apparatuses including a refrigerant circuit including a gas-liquid separator for performing two-stage compression/two-state expansion refrigeration cycle utilizing CO2 refrigerant at high pressure as that at its critical pressure.
Claims (4)
- A refrigerating apparatus comprising a refrigerant circuit for performing a two-stage compression/two-stage expansion refrigeration cycle in which CO2 refrigerant at high pressure is utilized as that at its critical pressure, the refrigerant circuit including: a compressor including a low pressure side compression mechanism and a high pressure side compression mechanism connected to each other by means of a drive shaft; and a gas-liquid separator for separating refrigerant at intermediate pressure into gas refrigerant and liquid refrigerant,
wherein a volume ratio of a displacement volume of the high pressure side compression mechanism to that of the low pressure side compression mechanism falls in a range between 0.8 and 1.3, both exclusive. - The refrigerating apparatus of Claim 1,
wherein the volume ratio falls in a range between 0.9 and 1.1, both inclusive. - The refrigerating apparatus of Claim 2,
wherein the volume ratio is 1.0. - The refrigerating apparatus of any one of Claims 1 to 3,
wherein the low pressure side compression mechanism and the high pressure side compression mechanism are rotary compression mechanisms.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006053431A JP2007232263A (en) | 2006-02-28 | 2006-02-28 | Refrigeration unit |
PCT/JP2007/053255 WO2007105440A1 (en) | 2006-02-28 | 2007-02-22 | Refrigeration device |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1990587A1 true EP1990587A1 (en) | 2008-11-12 |
EP1990587A4 EP1990587A4 (en) | 2014-11-19 |
EP1990587B1 EP1990587B1 (en) | 2019-04-17 |
Family
ID=38509276
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07714753.6A Active EP1990587B1 (en) | 2006-02-28 | 2007-02-22 | Refrigeration device |
Country Status (9)
Country | Link |
---|---|
US (1) | US20090044564A1 (en) |
EP (1) | EP1990587B1 (en) |
JP (1) | JP2007232263A (en) |
KR (1) | KR20080090528A (en) |
CN (1) | CN101384865B (en) |
AU (1) | AU2007226005B2 (en) |
ES (1) | ES2733021T3 (en) |
TR (1) | TR201909681T4 (en) |
WO (1) | WO2007105440A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2339272A1 (en) * | 2009-12-18 | 2011-06-29 | Climaveneta S.p.A. | Thermo-frigorific unit and its control method |
US20110232325A1 (en) * | 2008-12-05 | 2011-09-29 | Shuji Furui | Refrigerating apparatus |
WO2011091014A3 (en) * | 2010-01-20 | 2012-01-12 | Carrier Corporation | Refrigeration storage in a refrigerant vapor compression system |
Families Citing this family (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5003440B2 (en) * | 2007-11-30 | 2012-08-15 | ダイキン工業株式会社 | Refrigeration equipment |
JP5029326B2 (en) * | 2007-11-30 | 2012-09-19 | ダイキン工業株式会社 | Refrigeration equipment |
JP2009133585A (en) * | 2007-11-30 | 2009-06-18 | Daikin Ind Ltd | Refrigerating device |
JP5003439B2 (en) | 2007-11-30 | 2012-08-15 | ダイキン工業株式会社 | Refrigeration equipment |
KR101157799B1 (en) | 2007-11-30 | 2012-06-20 | 다이킨 고교 가부시키가이샤 | Freezing apparatus |
JP5239824B2 (en) * | 2008-02-29 | 2013-07-17 | ダイキン工業株式会社 | Refrigeration equipment |
JP5125611B2 (en) | 2008-02-29 | 2013-01-23 | ダイキン工業株式会社 | Refrigeration equipment |
JP2009264605A (en) * | 2008-04-22 | 2009-11-12 | Daikin Ind Ltd | Refrigerating device |
JP2009264606A (en) * | 2008-04-22 | 2009-11-12 | Daikin Ind Ltd | Refrigerating device |
JP5120056B2 (en) | 2008-05-02 | 2013-01-16 | ダイキン工業株式会社 | Refrigeration equipment |
JP5181813B2 (en) | 2008-05-02 | 2013-04-10 | ダイキン工業株式会社 | Refrigeration equipment |
JP5407173B2 (en) | 2008-05-08 | 2014-02-05 | ダイキン工業株式会社 | Refrigeration equipment |
WO2010036480A2 (en) * | 2008-09-29 | 2010-04-01 | Carrier Corporation | Flash tank economizer cycle control |
JP5040907B2 (en) * | 2008-09-30 | 2012-10-03 | ダイキン工業株式会社 | Refrigeration equipment |
JP2010085042A (en) * | 2008-10-01 | 2010-04-15 | Mitsubishi Electric Corp | Refrigerating cycle device |
JP5193011B2 (en) * | 2008-12-09 | 2013-05-08 | 三菱重工業株式会社 | Refrigeration cycle |
JP5403029B2 (en) * | 2011-10-07 | 2014-01-29 | ダイキン工業株式会社 | Refrigeration equipment |
KR102103360B1 (en) * | 2013-04-15 | 2020-05-29 | 엘지전자 주식회사 | Air Conditioner and Controlling method for the same |
JP6578517B2 (en) * | 2015-01-15 | 2019-09-25 | パナソニックIpマネジメント株式会社 | Refrigeration cycle apparatus and compressor used therefor |
CN105371514B (en) * | 2015-12-10 | 2018-05-18 | 珠海格力电器股份有限公司 | Compressibility, air-conditioning system with second vapor injection and its judge control method |
JP6765086B2 (en) * | 2017-02-14 | 2020-10-07 | パナソニックIpマネジメント株式会社 | Refrigeration equipment |
JP2023005307A (en) * | 2021-06-28 | 2023-01-18 | パナソニックIpマネジメント株式会社 | compressor |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2003065615A (en) * | 2001-08-23 | 2003-03-05 | Daikin Ind Ltd | Refrigerating machine |
JP2003074999A (en) * | 2001-08-31 | 2003-03-12 | Daikin Ind Ltd | Refrigerating machine |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04366377A (en) * | 1991-06-11 | 1992-12-18 | Daikin Ind Ltd | Gas-liquid separator |
JP2699724B2 (en) * | 1991-11-12 | 1998-01-19 | 松下電器産業株式会社 | Two-stage gas compressor |
JPH09196478A (en) * | 1996-01-23 | 1997-07-31 | Nippon Soken Inc | Refrigerating cycle |
JP3781880B2 (en) * | 1997-11-20 | 2006-05-31 | 松下電器産業株式会社 | Refrigeration apparatus with injection function |
JPH11241693A (en) * | 1998-02-24 | 1999-09-07 | Sanyo Electric Co Ltd | Compressor |
JPH11304269A (en) * | 1998-04-23 | 1999-11-05 | Nippon Soken Inc | Refrigerating cycle |
JP3847493B2 (en) * | 1999-09-01 | 2006-11-22 | 松下冷機株式会社 | Two-stage compression refrigeration system |
EP1215449A4 (en) * | 1999-09-24 | 2005-01-19 | Sanyo Electric Co | Multi-stage compression refrigerating device |
JP2001132675A (en) * | 1999-11-04 | 2001-05-18 | Sanyo Electric Co Ltd | Two-stage compression type rotary compressor and two- stage compression refrigerating device |
JP2001241797A (en) * | 2000-02-24 | 2001-09-07 | Sharp Corp | Refrigerating cycle |
JP3918421B2 (en) * | 2000-09-21 | 2007-05-23 | 三菱電機株式会社 | Air conditioner, operation method of air conditioner |
JP2003083247A (en) * | 2001-09-14 | 2003-03-19 | Toshiba Kyaria Kk | Compressor and refrigerating cycle device |
US7631510B2 (en) * | 2005-02-28 | 2009-12-15 | Thermal Analysis Partners, LLC. | Multi-stage refrigeration system including sub-cycle control characteristics |
JP2007010282A (en) * | 2005-07-04 | 2007-01-18 | Hitachi Ltd | Two-stage compression type refrigeration cycle device |
JP2007178042A (en) * | 2005-12-27 | 2007-07-12 | Mitsubishi Electric Corp | Supercritical vapor compression type refrigerating cycle and cooling and heating air conditioning facility and heat pump hot-water supply machine using it |
-
2006
- 2006-02-28 JP JP2006053431A patent/JP2007232263A/en active Pending
-
2007
- 2007-02-22 KR KR1020087020719A patent/KR20080090528A/en not_active Application Discontinuation
- 2007-02-22 CN CN2007800058509A patent/CN101384865B/en active Active
- 2007-02-22 TR TR2019/09681T patent/TR201909681T4/en unknown
- 2007-02-22 ES ES07714753T patent/ES2733021T3/en active Active
- 2007-02-22 WO PCT/JP2007/053255 patent/WO2007105440A1/en active Application Filing
- 2007-02-22 AU AU2007226005A patent/AU2007226005B2/en active Active
- 2007-02-22 US US12/224,086 patent/US20090044564A1/en not_active Abandoned
- 2007-02-22 EP EP07714753.6A patent/EP1990587B1/en active Active
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2003065615A (en) * | 2001-08-23 | 2003-03-05 | Daikin Ind Ltd | Refrigerating machine |
JP2003074999A (en) * | 2001-08-31 | 2003-03-12 | Daikin Ind Ltd | Refrigerating machine |
Non-Patent Citations (4)
Title |
---|
HUFF H-J ET AL: "OPTIONS FOR A TWO-STAGE TRANSCRIPTIONAL CARBON DIOXIDE CYCLE", IIR GUSTAV LORENTZEN CONFERENCE ON NATURAL WORKING FLUIDS.JOINT CONFERENCE OF THE INTERNATIONAL INSTITUTE OF REFRIGERATIONSECTION B AND E, XX, XX, 17 September 2002 (2002-09-17), pages 158-164, XP001176579, * |
INOKUTY H: "NEUE KREISPROZESSE AN KALTDAMPFMASCHINEN THEORIE UND VERSUCHE", ZEITSCHRIFT FUER DIE GESAMTE KAELTE-INDUSTRIE, VDI VERLAG, BERLIN, DE, vol. 36, no. 2, 1 February 1929 (1929-02-01), pages 21-26, XP001169158, ISSN: 0372-879X * |
JAKOBSEN A: "Improving efficiency of trans-critical CO2 refrigeration systems for reefers", IIF-IIR COMMISSION D2 D3,, 1 February 1998 (1998-02-01), pages 130-138, XP001168660, * |
See also references of WO2007105440A1 * |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20110232325A1 (en) * | 2008-12-05 | 2011-09-29 | Shuji Furui | Refrigerating apparatus |
EP2339272A1 (en) * | 2009-12-18 | 2011-06-29 | Climaveneta S.p.A. | Thermo-frigorific unit and its control method |
WO2011091014A3 (en) * | 2010-01-20 | 2012-01-12 | Carrier Corporation | Refrigeration storage in a refrigerant vapor compression system |
US9068765B2 (en) | 2010-01-20 | 2015-06-30 | Carrier Corporation | Refrigeration storage in a refrigerant vapor compression system |
Also Published As
Publication number | Publication date |
---|---|
AU2007226005A1 (en) | 2007-09-20 |
AU2007226005B2 (en) | 2010-05-20 |
JP2007232263A (en) | 2007-09-13 |
TR201909681T4 (en) | 2019-07-22 |
EP1990587A4 (en) | 2014-11-19 |
KR20080090528A (en) | 2008-10-08 |
CN101384865A (en) | 2009-03-11 |
CN101384865B (en) | 2012-04-18 |
WO2007105440A1 (en) | 2007-09-20 |
US20090044564A1 (en) | 2009-02-19 |
ES2733021T3 (en) | 2019-11-27 |
EP1990587B1 (en) | 2019-04-17 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
AU2007226005B2 (en) | Refrigerating apparatus | |
JP4797715B2 (en) | Refrigeration equipment | |
JP4813599B2 (en) | Refrigeration cycle equipment | |
US7415838B2 (en) | Second-refrigerant pump driving type air conditioner | |
JP4457928B2 (en) | Refrigeration equipment | |
EP2497955B1 (en) | Heat pump device, two-stage compressor, and method of operating heat pump device | |
JP4640142B2 (en) | Refrigeration equipment | |
EP1739369A1 (en) | Refrigeration system | |
KR100857794B1 (en) | Air-conditioning system and Controlling Method for the same | |
EP2196746A2 (en) | Refrigeration apparatus | |
CN100347490C (en) | Multi-stage operation type air conditioner and operating method thereof | |
US7908878B2 (en) | Refrigerating apparatus | |
JP2007155143A (en) | Refrigerating device | |
CN111954787A (en) | Double-compressor heat pump | |
JPH11223396A (en) | Multi-stage compression refrigerating unit | |
JP4581795B2 (en) | Refrigeration equipment | |
JP2007147228A (en) | Refrigerating device | |
KR100710312B1 (en) | Air-conditioning system and controlling method for the same | |
KR100710311B1 (en) | Air-conditioning system and controlling method for the same | |
KR102194017B1 (en) | Indoor unit and air conditioner comprising drain pump | |
TWI625465B (en) | Compressor and air conditioner using same | |
JP2001124444A (en) | Refrigerating cycle system | |
KR20040108250A (en) | A hotting drive method of heat pump multi-air conditioner |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20080819 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
DAX | Request for extension of the european patent (deleted) | ||
A4 | Supplementary search report drawn up and despatched |
Effective date: 20141020 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F25B 1/10 20060101AFI20141014BHEP Ipc: F25B 1/04 20060101ALI20141014BHEP Ipc: F25B 1/00 20060101ALI20141014BHEP |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: EXAMINATION IS IN PROGRESS |
|
17Q | First examination report despatched |
Effective date: 20180312 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
INTG | Intention to grant announced |
Effective date: 20181031 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: DAIKIN INDUSTRIES, LTD. |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602007058122 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 1121980 Country of ref document: AT Kind code of ref document: T Effective date: 20190515 Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20190417 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190819 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FG2A Ref document number: 2733021 Country of ref document: ES Kind code of ref document: T3 Effective date: 20191127 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190717 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190718 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 1121980 Country of ref document: AT Kind code of ref document: T Effective date: 20190417 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190817 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602007058122 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20200120 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20200229 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200222 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200229 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200229 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200222 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200229 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190417 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20221230 Year of fee payment: 17 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20230110 Year of fee payment: 17 Ref country code: ES Payment date: 20230310 Year of fee payment: 17 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: TR Payment date: 20230221 Year of fee payment: 17 Ref country code: IT Payment date: 20230110 Year of fee payment: 17 Ref country code: DE Payment date: 20221229 Year of fee payment: 17 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230525 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: ES Payment date: 20240304 Year of fee payment: 18 |