EP2008035A1 - Transport refrigeration unit - Google Patents
Transport refrigeration unitInfo
- Publication number
- EP2008035A1 EP2008035A1 EP07751951A EP07751951A EP2008035A1 EP 2008035 A1 EP2008035 A1 EP 2008035A1 EP 07751951 A EP07751951 A EP 07751951A EP 07751951 A EP07751951 A EP 07751951A EP 2008035 A1 EP2008035 A1 EP 2008035A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- refrigerant flow
- refrigerant
- refrigeration unit
- flow path
- primary
- 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.)
- Withdrawn
Links
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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- 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
- F25B2500/00—Problems to be solved
- F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2501—Bypass 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2400/00—General features of, or devices for refrigerators, cold rooms, ice-boxes, or for cooling or freezing apparatus not covered by any other subclass
- F25D2400/28—Quick cooling
Definitions
- This invention relates generally to transport refrigeration units and, more specifically, to facilitating the pull down of the temperature of product when loaded into a transport container provided with a refrigeration unit.
- Refrigerated freight containers require a refrigeration unit for maintaining a desired temperature environment within the interior volume of the container.
- the refrigeration unit must have sufficient refrigeration capacity to maintain the product stored within the container at the desired temperature over a wide range of outdoor ambient temperatures and load conditions.
- Refrigerated freight containers are used to transport a wide variety of products, ranging for example from freshly picked produce to deep frozen seafood. Product may be loaded into the container unit directly from the field, such as freshly picked fruits and vegetables, or from a warehouse.
- Conventional transport refrigeration units used in connection with cooling refrigerated freight containers include a refrigerant compressor, a condenser coil, a thermostatic expansion valve (TXV), and an evaporator coil connected via appropriate refrigerant lines in a closed refrigerant flow circuit.
- TXV thermostatic expansion valve
- the refrigeration unit is generally contained in a housing mountable to the container such that the air or gas/air mixture or other gas within the interior volume of the container may be circulated over the evaporator coil by means of an evaporator fan associated with the evaporator coil.
- the refrigerant unit may also be equipped with an economizer incorporated into the refrigerant circuit, if desired.
- the refrigeration unit is typically designed with a refrigeration capacity sized to provide stable temperature at a low box temperature desired for deep frozen product, which as noted before when loaded into the container has already been pre-cooled to the desired product storage temperature for transport.
- the TXV which is located in the refrigerant circuit at the inlet to the evaporator coil, is a mechanical device using a thermal expansion bulb measuring refrigerant temperature leaving the evaporator to meter the refrigerant entering the evaporator, thereby adjusting and controlling the amount of refrigerant flow through the refrigerant circuit.
- the TXV is sized to be the largest possible yet most stable valve at the deep frozen condition.
- Products applied hot require the refrigeration unit to pull the product temperature down to set point temperature, typically about 2 ° C (about 36 ° F) from product temperatures ranging as high as 38°C (100 ° F) or above.
- set point temperature typically about 2 ° C (about 36 ° F) from product temperatures ranging as high as 38°C (100 ° F) or above.
- the refrigerant unit requires high refrigerant mass flow to cool the product down as rapidly as possible.
- the refrigerant mass flow through the refrigerant circuit is limited by the TXV size required for low temperature stability.
- the TXV typically will respond by opening up to maintain a desired superheat. In the event the TXV reaches its maximum capacity the valve is no longer able to provide a stable or adequate superheat.
- EXV electronic expansion valve
- a transport refrigerant unit is provided with a dual-path, parallel flow expansion circuit.
- the expansion circuit is inserted in the refrigerant circuit to increase the refrigerant mass flow during pull down.
- the expansion circuit includes a primary expansion device disposed in a primary refrigerant flow path and an auxiliary expansion device disposed in a secondary refrigerant flow path.
- the main refrigerant line from the condenser coil outlet to the evaporator coil forms the primary refrigerant flow path of the expansion circuit and the primary expansion device is the evaporator TXV disposed in this refrigerant line.
- the secondary refrigerant flow path of the expansion circuit comprises a bypass refrigerant line which connects at its inlet end to the refrigerant circuit upstream with respect to refrigerant flow of the evaporator TXV and at its outlet end to the refrigerant circuit downstream with respect to refrigerant flow of the evaporator TXV.
- the auxiliary expansion device and a bypass valve are disposed in the bypass line.
- the bypass line is shut off during low box temperature operation.
- the auxiliary expansion device may be a fixed orifice or an additional TXV.
- a controller opens the bypass valve when it is desired to allow refrigerant flow through the bypass line and closes the bypass valve when it is desired to pass refrigerant flow only through the TXV.
- the fixed orifice is located within the bypass valve itself.
- FIG. 1 is a schematic representation of an exemplary embodiment of a transport refrigeration unit with a dual-path, parallel flow expansion circuit depicting operation during a stable product storage temperature maintenance mode;
- FIG. 2 is a schematic representation of the embodiment of the transport refrigeration unit of Fig. 1 depicting operation during a product temperature pull-down mode;
- FIG. 3 is another exemplary embodiment of a transport refrigeration unit with a dual-path, parallel flow expansion circuit
- FIG. 4 is a further exemplary embodiment of a transport refrigeration unit with a dual-path, parallel flow expansion circuit
- Fig. 5 is an exemplary embodiment of a transport refrigeration unit with a dual-path, parallel flow expansion circuit and including an economizer circuit;
- FIG. 6 is a perspective view of an exemplary embodiment of a dual-path, parallel flow expansion circuit. Detailed Description of the Invention
- FIG. 1 through 5 there are shown schematically, various exemplary embodiments of a transport refrigeration unit 10 designed for regulating and maintaining a desired product storage temperature range within a refrigerated volume wherein a perishable product is stored during transport, such as a refrigerated freight container or the box of a truck or trailer.
- a transport refrigeration unit 10 designed for regulating and maintaining a desired product storage temperature range within a refrigerated volume wherein a perishable product is stored during transport, such as a refrigerated freight container or the box of a truck or trailer.
- the refrigeration unit 10 includes a compressor 20, a condenser 30 including a condenser heat exchange coil 32 and associated condenser fan(s) 34, an evaporator heat exchanger 40 including an evaporator heat exchanger coil 42 and associated evaporator fan(s) 44, and an evaporator thermal expansion valve (TXV) 50 connected in a conventional manner by refrigerant lines 2, 4 and 6 in a refrigerant flow circuit.
- the compressor 20 is a reciprocating compressor or a scroll compressor, single-stage or two-stage; however, the particular type of compressor used is not germane to or limiting of the invention.
- the refrigeration unit 10 depicted in Fig. 5 further includes an economizer 80 operatively associated with a scroll compressor.
- refrigerant line 2 connects the discharge outlet of the compressor 20 in refrigerant flow communication with the inlet to the condenser heat exchanger coil 32
- refrigerant line 4 connects the outlet of the condenser heat exchanger coil 32 in refrigerant flow communication with the inlet to the evaporator heat exchanger coil 42
- refrigerant line 6 connects the outlet of the evaporator heat exchanger coil 42 in refrigerant flow communication with the suction inlet of the compressor 20, thereby completing the refrigerant flow circuit.
- a refrigerant-to-refrigerant in-line heat exchanger 60 may be included in the refrigerant flow circuit for passing the liquid refrigerant passing through refrigerant line 4 in heat exchange relationship with the vapor refrigerant passing through refrigerant line 6.
- a suction modulation valve 12, a suction solenoid valve 13, a quench expansion valve 14, a filter/drier 16, and a receiver 18 with slight glass 15 may be included in the refrigerant circuit in refrigerant line 6 as in conventional practice.
- the refrigeration unit also includes an electronic controller 55 such as, for example an MicroLinkTM controller available from Carrier Corporation of Syracuse, N. Y., USA.
- the electronic controller 55 is configured to operate the refrigeration unit 10 to maintain a predetermined thermal environment within the enclosed volume, termed a box, wherein the product is stored.
- the electronic controller 55 maintains the predetermined environment by selectively controlling the operation of the compressor 20, the condenser fan(s) 34 associated with the condenser heat exchanger coil 32, the evaporator fan(s) 44 associated with the evaporator heat exchanger coil 42, and the suction modulation valve 12. For example, when cooling of the environment within the box is required, the electronic controller 55 provides electrical power to activate the compressor 20, the condenser fan and the evaporator fan.
- the electronic controller 55 adjusts the position of the suction modulation valve 12 to increase or decrease the flow of refrigerant supplied to the compressor 20 as appropriate to control and stabilize the temperature within the box at the set point temperature, which coiTesponds to the desired product storage temperature for the particular product stored within the box.
- the refrigeration unit 10 incorporates an economizer circuit including an economizer heat exchanger 80 wherein liquid refrigerant passing through refrigerant line 4 passes in heat exchange relationship wilh refrigerant vapor passing through economizer line 82.
- economizer heat exchanger 80 wherein liquid refrigerant passing through refrigerant line 4 passes in heat exchange relationship wilh refrigerant vapor passing through economizer line 82.
- a portion of the liquid refrigerant having traversed the condenser coil 32 and passing through refrigerant line 4 may be diverted into economizer line 82 upstream of the economizer heat exchanger 80.
- the diverted refrigerant traverses an expansion device 86, such as for example a thermostatic expansion valve, disposed in economizer line 82 wherein the liquid refrigerant is expanded to a lower pressure and lower temperature vapor refrigerant.
- the refrigerant vapor continues through refrigerant line 82 to pass through the economizer heat exchanger 80 in heat exchange relationship with the higher pressure, higher temperature refrigerant passing through refrigerant line 4.
- the refrigerant vapor thereafter continues through the refrigerant line 82 to be injected into an intermediate pressure stage of the compressor 20.
- the compressor 20 comprises a scroll compressor, but it is to be understood that any multiple stage compressor or multiple compressors could be used.
- the liquid refrigerant having passed through the economizer heat exchanger 80 continues through refrigerant line 4 to the evaporator 40.
- a flow control valve 84 disposed in the economizer line 82 upstream with respect to refrigerant flow of the expansion device 86, is operative under direction of the system controller 55 to selectively open or close the economizer line 82 to refrigerant flow there through.
- a liquid injection line 88 may be provided to divert a portion of the liquid refrigerant from refrigerant line 4 into the economizer line 82 downstream of the economizer heat exchanger 80 to be injected into an intermediate compression stage of the compressor 20.
- the refrigerant circuit of the refrigeration unit 10 includes a dual-path, parallel-flow expansion circuit 70 in operative association with the evaporator 40.
- the expansion circuit is incorporated into the refrigerant circuit in line 4 downstream of the refrigerant-to-refrigerant heat exchanger 60 and upstream of the inlet to the evaporator heat exchanger coil 42.
- the expansion circuit 70 is incorporated into the refrigerant circuit in line 4 downstream with respect to refrigerant flow of the economizer 80 and upstream with respect to refrigerant flow of the inlet to the evaporator heat exchanger coil 42.
- the expansion circuit 70 includes a primary expansion device disposed in a primary refrigerant flow path and an auxiliary expansion device disposed in a secondary refrigerant flow path.
- the refrigerant line 4 forms the primary refrigerant flow path of the expansion circuit and the primary expansion device comprises the evaporator TXV 50 disposed in refrigerant line 4 with section 4A of refrigerant line 4 upstream of the TXV 50 and with section 4B of refrigerant line 4 downstream with respect to refrigerant flow of the TXV.
- the secondary refrigerant flow path of the expansion circuit 70 comprises a bypass refrigerant line 8 which connects at its inlet end to section 4A of refrigerant line 4 of the refrigerant circuit upstream with respect to refrigerant flow of the evaporator TXV 50 and at its outlet end to section 4B of refrigerant line 4 of the refrigerant circuit downstream with respect to refrigerant flow of the evaporator TXV.
- the auxiliary expansion device 72 and a bypass valve 74 are disposed in the bypass line 70.
- the auxiliary expansion device 72 may be positioned downstream or upstream with respect to refrigerant flow of the bypass valve 74.
- the auxiliary expansion device 72 comprises a fixed orifice device disposed in refrigerant line 8 downstream with respect to refrigerant flow of the bypass valve 74.
- the auxiliary expansion valve 72 comprises a fixed orifice device disposed in refrigerant line 8 upstream with respect to refrigerant flow of the bypass valve 74.
- the auxiliary expansion device 72 could also be a fixed-bore device such as a capillary tube.
- the auxiliary expansion device 72 comprises a fixed orifice embodied within the bypass valve 74.
- the auxiliary expansion device 72 comprises a thermostatic expansion valve disposed in refrigerant line 8 downstream with respect to refrigerant flow of the bypass valve 74.
- the bypass valve 74 comprises a solenoid valve having an open position in which refrigerant may pass from section 4A of refrigerant line 4 through refrigerant line 8 and into section 4B of refrigerant line 4 and having a closed position in which refrigerant flow through refrigerant line 8 is blocked.
- the solenoid valve 72 is in electrical communication with the controller 55 which controls the positioning of the solenoid valve 74 is either its open or closed position.
- the controller 55 maintains the bypass valve 74 in its noi ⁇ nal closed position.
- the bypass valve 74 in its closed position, no refrigerant flows through refrigerant line 8 of the expansion circuit 70. Rather, all refrigerant flow through refrigerant line 4 passes through the evaporator TXV 50.
- the amount of flow passing through the evaporator heat exchanger coil 42 is adjusted and controlled by the evaporator TXV 50 in a conventional manner.
- the controller 55 will energize the solenoid valve 74 to position the solenoid valve 74 in its open position, thereby permitting refrigerant to flow from section 4A of refrigerant line 4 through refrigerant line 8 into section 4B of refrigerant line 4 to pass through the evaporator heat exchanger coil 42 while bypass the TXV 50.
- refrigerant flows through both paths of the dual- path, parallel flow expansion circuit 70.
- a first flow of liquid refrigerant passes through refrigerant line 4 traversing the primary expansion device, TXV 50, wherein it is expanded to a vapor state, and thence passes to the evaporator heat exchanger coil 42.
- a second flow of liquid refrigerant passes from section 4A of the refrigerant line 4 through refrigerant line 8 traversing the auxiliary expansion device 72, wherein it is expanded to a vapor state, and thence passes to and through section 4B of refrigerant line 4 to the evaporator heat exchanger coil 42. ha this manner, the amount of refrigerant flowing through the evaporator heat exchanger coil 42 is significantly increased, thereby increasing the refrigeration capacity of the evaporator 40.
- the controller 55 may be configured to open and close the bypass solenoid valve 74 in response to evaporator or compressor suction superheat in addition to a fixed return air temperature range.
- a fixed temperature range can be used knowing the existing limitations of the current valve and system.
- the controller 55 will de-energize the solenoid valve 74 thereby causing the solenoid valve 74 to move to its closed position, thereby closing refrigerant line 8. With the solenoid valve 74 closed, the mechanical evaporator TXV 50 will assume control of the amount of refrigerant flowing through the evaporator heat exchanger coil 42 as in conventional practice.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US78724406P | 2006-03-30 | 2006-03-30 | |
PCT/US2007/005220 WO2007126523A1 (en) | 2006-03-30 | 2007-02-28 | Transport refrigeration unit |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2008035A1 true EP2008035A1 (en) | 2008-12-31 |
EP2008035A4 EP2008035A4 (en) | 2013-01-23 |
Family
ID=38655821
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07751951A Withdrawn EP2008035A4 (en) | 2006-03-30 | 2007-02-28 | Transport refrigeration unit |
Country Status (5)
Country | Link |
---|---|
US (1) | US20090038322A1 (en) |
EP (1) | EP2008035A4 (en) |
JP (1) | JP2009532654A (en) |
CN (1) | CN101416004A (en) |
WO (1) | WO2007126523A1 (en) |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9057548B2 (en) | 2009-10-14 | 2015-06-16 | Carrier Corporation | Receiver with flow metering device |
CN102575890B (en) | 2009-11-03 | 2015-08-26 | 开利公司 | Pressure spike in conjunction with the refrigerant system of micro channel heat exchanger reduces |
ES2855008T3 (en) | 2009-12-18 | 2021-09-23 | Carrier Corp | Transport refrigeration system and methods therefor to cope with dynamic conditions |
CN103038099A (en) | 2010-08-13 | 2013-04-10 | 开利公司 | Transport refrigeration security system |
US8820104B2 (en) * | 2010-10-22 | 2014-09-02 | Tai-Her Yang | Temperature regulation system with active jetting type refrigerant supply and regulation |
US9074783B2 (en) * | 2010-11-12 | 2015-07-07 | Tai-Her Yang | Temperature regulation system with hybrid refrigerant supply and regulation |
US9074800B2 (en) * | 2010-11-12 | 2015-07-07 | Tai-Her Yang | Temperature regulation system with hybrid refrigerant supply and regulation |
EP2668051B1 (en) | 2011-01-26 | 2019-02-06 | Carrier Corporation | Efficient control algorithm for start-stop operation of refrigeration unit powered by an engine |
KR101912837B1 (en) * | 2011-12-21 | 2018-10-29 | 양태허 | Temperature regulation system with active jetting type refrigerant supply and regulation |
WO2014082069A1 (en) * | 2012-11-26 | 2014-05-30 | Thermo King Corporation | Auxiliary subcooling circuit for a transport refrigeration system |
CN104870916B (en) * | 2012-12-28 | 2017-05-03 | 大金工业株式会社 | Refrigeration device |
CN107356012A (en) | 2016-05-09 | 2017-11-17 | 开利公司 | Heat pump and its control method |
JP2018080861A (en) * | 2016-11-15 | 2018-05-24 | 富士電機株式会社 | Refrigerant circuit device |
CN110612416B (en) * | 2017-05-18 | 2022-10-18 | 开利公司 | Balanced pressure valve for transport refrigeration unit |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2306534A (en) * | 1940-04-30 | 1942-12-29 | Anthony F Hoesel | Refrigerating system |
DE951815C (en) * | 1952-09-30 | 1956-11-08 | Carrier Corp | Method and device for controlling a compression refrigeration system |
US3866439A (en) * | 1973-08-02 | 1975-02-18 | Carrier Corp | Evaporator with intertwined circuits |
GB2328270A (en) * | 1997-08-13 | 1999-02-17 | Toshiba Kk | Air conditioner |
JP2002039637A (en) * | 2000-07-25 | 2002-02-06 | Shin Meiwa Ind Co Ltd | Freezer and freezing method |
JP2002062020A (en) * | 2000-08-17 | 2002-02-28 | Toshiba Corp | Refrigerator |
DE10055916A1 (en) * | 2000-11-10 | 2002-05-23 | Bsh Bosch Siemens Hausgeraete | Coolant circuit for refrigeration machine has feed line containing capillary and pilot valve, with at least some coolant flowing through pilot valve and capillary in succession |
EP1923645A1 (en) * | 2005-09-08 | 2008-05-21 | Dairei Co., Ltd. | Control system for refrigerating machine employing non-azeotropic refrigerant |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4186562A (en) * | 1976-11-01 | 1980-02-05 | Lewis Tyree Jr | Cryogenic refrigeration for vehicles |
JPS5995350A (en) * | 1982-11-22 | 1984-06-01 | 三菱電機株式会社 | Controller for capacity control type refrigeration cycle |
US4873838A (en) * | 1986-10-31 | 1989-10-17 | Carrier Corporation | Refrigerant metering in a variable flow system |
US5095712A (en) * | 1991-05-03 | 1992-03-17 | Carrier Corporation | Economizer control with variable capacity |
JPH1054616A (en) * | 1996-08-14 | 1998-02-24 | Daikin Ind Ltd | Air conditioner |
JP3965717B2 (en) * | 1997-03-19 | 2007-08-29 | 株式会社日立製作所 | Refrigeration equipment and refrigerator |
US6566198B2 (en) * | 2001-03-29 | 2003-05-20 | International Business Machines Corporation | CMOS structure with non-epitaxial raised source/drain and self-aligned gate and method of manufacture |
US7143593B2 (en) * | 2003-03-24 | 2006-12-05 | Sanyo Electric Co., Ltd. | Refrigerant cycle apparatus |
-
2007
- 2007-02-28 CN CNA2007800122581A patent/CN101416004A/en active Pending
- 2007-02-28 WO PCT/US2007/005220 patent/WO2007126523A1/en active Application Filing
- 2007-02-28 EP EP07751951A patent/EP2008035A4/en not_active Withdrawn
- 2007-02-28 JP JP2009502805A patent/JP2009532654A/en not_active Withdrawn
- 2007-02-28 US US12/282,771 patent/US20090038322A1/en not_active Abandoned
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2306534A (en) * | 1940-04-30 | 1942-12-29 | Anthony F Hoesel | Refrigerating system |
DE951815C (en) * | 1952-09-30 | 1956-11-08 | Carrier Corp | Method and device for controlling a compression refrigeration system |
US3866439A (en) * | 1973-08-02 | 1975-02-18 | Carrier Corp | Evaporator with intertwined circuits |
GB2328270A (en) * | 1997-08-13 | 1999-02-17 | Toshiba Kk | Air conditioner |
JP2002039637A (en) * | 2000-07-25 | 2002-02-06 | Shin Meiwa Ind Co Ltd | Freezer and freezing method |
JP2002062020A (en) * | 2000-08-17 | 2002-02-28 | Toshiba Corp | Refrigerator |
DE10055916A1 (en) * | 2000-11-10 | 2002-05-23 | Bsh Bosch Siemens Hausgeraete | Coolant circuit for refrigeration machine has feed line containing capillary and pilot valve, with at least some coolant flowing through pilot valve and capillary in succession |
EP1923645A1 (en) * | 2005-09-08 | 2008-05-21 | Dairei Co., Ltd. | Control system for refrigerating machine employing non-azeotropic refrigerant |
Non-Patent Citations (1)
Title |
---|
See also references of WO2007126523A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN101416004A (en) | 2009-04-22 |
US20090038322A1 (en) | 2009-02-12 |
EP2008035A4 (en) | 2013-01-23 |
WO2007126523A1 (en) | 2007-11-08 |
JP2009532654A (en) | 2009-09-10 |
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