CN1226583C - Vapour compression refrigerating system with jector - Google Patents
Vapour compression refrigerating system with jector Download PDFInfo
- Publication number
- CN1226583C CN1226583C CN03123602.2A CN03123602A CN1226583C CN 1226583 C CN1226583 C CN 1226583C CN 03123602 A CN03123602 A CN 03123602A CN 1226583 C CN1226583 C CN 1226583C
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- CN
- China
- Prior art keywords
- refrigerant
- cold
- producing medium
- refrigeration system
- injector
- 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.)
- Expired - Fee Related
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
- F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
- F04F5/02—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid
- F04F5/04—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid displacing elastic fluids
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/001—Ejectors not being used as compression device
- F25B2341/0012—Ejectors with the cooled primary flow at high 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Thermal Sciences (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Jet Pumps And Other Pumps (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
Piping, which connects between a radiator and an ejector, is covered with a thermal insulator to thermally insulate a refrigerant passage defined in the piping. Thus, it is possible to limit a reduction in enthalpy of refrigerant, which could be induced by cooling of high temperature refrigerant by low temperature atmosphere to lose the enthalpy before depressurization of the high temperature refrigerant through the ejector. As a result, it is possible to limit a reduction in a theoretical value of recoverable energy at the time of depressurization and expansion of the refrigerant.
Description
Technical field
The present invention relates generally to a kind of vapor compression refrigeration system is vapor compression refrigeration system (vaporcompression refrigeration system).In particular, the present invention relates to a kind of refrigeration system (being a kind of injector circulation) that comprises an injector (injector is used as aspirator so that make low pressure refrigerant pass through the injector circulation).
Background technology
Picture has for example disclosed a kind of injector among the JIS Z8126 Number 2.1.1.3, and this injector is that a kind of power capacity transmits pump, and it extracts and circulating fluid by the effect of carrying secretly that utilizes the powerful liquid stream of discharging at a high speed through injector nozzle.
As known in the art, the injector circulation that comprises a kind of like this injector is as a vapor compression refrigeration system, wherein cold-producing medium is by injector step-down and gaseous state (evaporating in the evaporimeter) cold-producing medium that expands and evaporated to extract, like this injector just with the expansion energy (kinetic energy) of cold-producing medium thus the air inlet that changes pressure energy into and increased compressor press, therefore reduced the energy consumption of compressor.
In a word, make to common steam compression refrigerating system constant entropy the cold-producing medium step-down, and with the unique draw-out device of compressor as circulating refrigerant in the system.Different with it, in the injector circulation, the cold-producing medium of high pressure one side of injector circulation is to carry out step-down by injector constant entropy ground.In addition, the cold-producing medium of injector circulation low pressure one side is that the decimate action by injector circulates, and the cold-producing medium in injector circulation high pressure one side circulates by compressor.
Summary of the invention
One object of the present invention is exactly that a kind of like this injector by vapor compression refrigeration system promotes the recovery of energy to improve the overall efficiency of vapor compression refrigeration system.
In order to realize purpose of the present invention, provide a vapor compression refrigeration system of heat being transferred to high temperature one side from low temperature one side.The temperature of high temperature one side is than the temperature height of low temperature one side.Vapor compression refrigeration system comprises that vapour-liquid separator, a compressor, a radiator, an evaporimeter, an injector are connected the refrigerant passage device that radiator and injector are used with a fluid ground.The vapour-liquid separator is separated into gaseous refrigerant and liquid refrigerant with cold-producing medium.Compressor is used for the compression to cold-producing medium.Radiator is used to cool off the high-pressure refrigerant of discharging from compressor.Evaporimeter is used for vaporized refrigerant.Injector carries out step-down and makes its expansion the high-pressure refrigerant that provides from radiator, with the gaseous refrigerant that has evaporated that evaporates in the extraction evaporimeter, thereby injector just changes the expansion energy of cold-producing medium into admission pressure that pressure energy has increased compressor like this.Conduit is used for described liquid refrigerant is directed to evaporimeter, and described conduit is from refrigerant loop branch, and this refrigerant loop comprises compressor, radiator, injector and vapour-liquid separator, wherein supplies with the vapour-liquid separator from the cold-producing medium of injector output.The refrigerant passage device has carried out thermal isolation fully with the surrounding air that is centered around the refrigerant passage device.
Description of drawings
By following description, subsidiary claim and accompanying drawing, the present invention may be better understood and attached purpose, characteristic and advantage.Wherein accompanying drawing has:
Fig. 1 is the schematic diagram of the injector circulation of first kind of embodiment according to the present invention.
Fig. 2 is the injector enlarged diagram of injector circulation.
Fig. 3 is the perspective view according to the part signal of pipeline in first kind of embodiment injector circulation.
Fig. 4 shows the p-h figure that concerns between the pressure and enthalpy amount in the injector circulation of Fig. 1.
Fig. 5 be explain have the situation of certain heat insulator with not with the p-h figure of the situation difference of heat insulator.
Fig. 6 is the table that shows according to the injector circulation advantage of first kind of embodiment.
Fig. 7 is the schematic diagram according to second embodiment injector circulation of the present invention; With
Fig. 8 is the table that shows according to second kind of embodiment injector circulation advantage.
The specific embodiment
Hereinafter with reference to accompanying drawing various embodiment of the present invention is described.
(first kind of embodiment)
First kind of embodiment of the present invention is described with reference to Fig. 1 to Fig. 6.
In first kind of embodiment of the present invention, injector circulation of the present invention will specifically be implemented by a show cabinet or a refrigerator with refrigeration or freezing state storage food.Fig. 1 has schematically shown the injector circulation of the embodiment of the invention.
With reference to Fig. 1, compressor 10 by motor-driven to extract and compressed refrigerant.Radiator 20 be one between cold-producing medium (cold-producing medium of discharging) and outside air (be positioned at the storage cell of show cabinet or refrigerator outside air) from compressor 10 heat-shift so that the heat exchanger of high pressure one side of cooling refrigeration agent.
In the present embodiment, use chlorofluorocarbon (CFC) as cold-producing medium.Therefore, the refrigerant pressure in the radiator 20 will keep the critical pressure less than cold-producing medium.When cold-producing medium in radiator 20 during condensation, the enthalpy amount of cold-producing medium descends.Replace chlorofluorocarbon (CFC), carbon dioxide (CO2) also can be as cold-producing medium.
When carbon dioxide was used as cold-producing medium, the refrigerant pressure in the radiator 20 became and is equal to or greater than the critical pressure of cold-producing medium.Therefore, the temperature of cold-producing medium descends can not cause condensation of refrigerant, and the enthalpy amount of cold-producing medium can descend.
Evaporimeter 30 is heat exchangers of low pressure one side.In evaporimeter 30, at the cold-producing medium of liquid state with flow into heat-shift between the air in the refrigerator compartment, Ye Tai cold-producing medium cools off air in the inflow refrigerator compartment by gasify (promptly evaporating) like this.40 pairs of high-pressure refrigerants of injector carry out step-down and make its expansion and cold-producing medium is expanded, the gaseous refrigerant of evaporation just is drawn in the injector 40 in evaporimeter 30 so, thereby the expansion energy of high-pressure refrigerant just is converted into corresponding pressure energy to improve the admission pressure of compressor 10.
As shown in Figure 2, injector 40 comprises a nozzle 41,42 and diffusers 43 of mixing chamber (being blender).Nozzle 41 changes the pressure energy of high-pressure refrigerant into the speed energy, and by this way, promptly 41 pairs of cold-producing mediums of nozzle have carried out the constant entropy step-down and made its expansion.In mixing chamber 42, the high speed cold-producing medium stream of discharging from nozzle 41 will be evaporimeter 30 gaseous refrigerant of evaporation extract into mixing chamber 42, and with the refrigerant mixed of gaseous state.In diffuser 43, cold-producing medium of discharging from nozzle 41 and the cold-producing medium that extracts from evaporimeter 30 are further mixed, and by this way, promptly the speed energy of cold-producing medium changes pressure energy into and increased the pressure of cold-producing medium.
In the present embodiment, Laval nozzle (having a throttle part in its path) speed that is used for the cold-producing medium that will discharge from nozzle 41 is increased to the level that is equal to or greater than velocity of sound.
In mixing chamber 42, the cold-producing medium of two kinds of approach obtains mixing, so enter the summation conservation of the cold-producing medium kinetic momentum of injector 40 from the cold-producing medium kinetic momentum of nozzle 41 discharges with from evaporimeter 30 extractions.Therefore, even in mixing chamber 42, the static pressure of cold-producing medium increases.
In diffusion 43, the cross sectional area of path is towards the linear increase of diffuser 43 downstream, so that the dynamic pressure of cold-producing medium is converted to corresponding static pressure.Therefore, in injector 40, improve the pressure of cold-producing medium by mixing chamber 42 and diffuser 43.Thereby mixing chamber 42 and diffuser 43 are referred to as supercharging device.
Referring to Fig. 1, the cold-producing medium of discharging from injector 40 is fed to vapour-liquid separator 50.Vapour-liquid separator 50 separates the device that separates with the vapour-liquid of storage as a kind of cold-producing medium (being gaseous refrigerant and liquid refrigerant) that will be in two states.The gaseous refrigerant outlet of vapour-liquid separator 50 links to each other with the inlet of compressor 10, and the liquid refrigerant outlet of vapour-liquid separator 50 links to each other with the inlet of evaporimeter 30.
In the present embodiment, with reference to figure 1, pipeline 60 is connected between radiator 20 and the injector 40 and has formed a refrigerant passage.By forming refrigerant passage therein, pipeline 60 is as a kind of refrigerant passage device of the present invention, and pipeline 60 is connected between radiator 20 and the injector 40 with being used for fluid.With reference to Fig. 1 and Fig. 3, pipeline 60 is coated with certain heat insulator 61, thus with the air heat insulation.
In the present embodiment, heat insulator 61 by the heat conductivity resin material lower, foam resin than the heat conductivity of metal or with it materials similar constitute.In addition, in the present embodiment, as compressor 10, evaporimeter 20 and injector 40, these parts all are contained in the show cabinet.Therefore, above-mentioned air refers to the air in the show cabinet.
Fig. 4 is pressure-enthalpy amount (p-h) figure that shows injector circulation macro operation.The macro operation of the present embodiment injector circulation macro operation with the known injectors circulation in fact is identical.Therefore, in the present embodiment, for simplicity, the macro operation of injector circulation will be described no longer here.In addition, among Fig. 4, the point that digital 1-7 represents among the point that digital 1-7 represents and Fig. 1 is corresponding, is illustrated in the corresponding state that these 1-7 go up cold-producing medium.
When refrigerant charge increased, the rotating speed of compressor 10 increased the refrigerant flow of discharging from compressor 10 to increase.On the other hand, when refrigerant charge reduced, compressor 10 rotating speeds reduced to reduce from the refrigerant flow of compressor 10 discharges.
Below, will the advantage that present embodiment has be described.
In the injector circulation, as shown in Figure 5, injector 40 constant entropies ground reduces the pressure of cold-producing medium, and therefore the corresponding enthalpy amount of adiabatic heat potential difference (adiabatic thermal head) that obtains during the step-down of 40 pairs of cold-producing medium constant entropies of corresponding injector has obtained recovery, thereby reduces the power consumption of compressor 10.
On the other hand, shown in the p-h figure among Fig. 5, when the enthalpy amount descended, the corresponding isoentropic gradient increased (being steepening), so the amount of enthalpy quantitative changeization (being the adiabatic heat potential difference) descends with respect to the variation of pressure.Therefore, when expanding in the cold-producing medium step-down, the maximum theoretical of callable energy can descend.
Different with it, in the present embodiment, the pipeline 60 that connects between radiator 20 and injector 40 is covered with heat insulator 61.Therefore, the minimizing of cold-producing medium enthalpy amount can be limited, before 40 pairs of high temperature refrigerant step-downs of injector, the minimizing of cold-producing medium enthalpy amount can be caused, so that lose the enthalpy amount by Cryogenic air cooling down high-temperature cold-producing medium.Therefore, when cold-producing medium step-down and expansion, just can limit the minimizing of recoverable energy theoretical value.
This can improve the performance of injector, promptly improve the quantity that recovers energy reducing the power consumption of compressor 10 by injector 40, thereby the injector circulation can move more effectively.
Fig. 6 contrasts two kinds of situations, and promptly pipeline 60 is coated with the not situation of cover heating insulator 61 of the situation of heat insulator 61 and pipeline 60.As shown in Figure 6, around pipeline 60, heat insulator 61 is set and has improved the coefficient of performance (COP).
(second embodiment)
Below, with reference to Fig. 7 and Fig. 8 second embodiment of the present invention described.
As shown in Figure 7, be provided with an internal exchanger 70.Internal exchanger 70 is heat-shift between the low pressure refrigerant of the high-pressure refrigerant of discharging and supply with injector 40 from radiator 20 and supply compressor 10.Internal exchanger 70 is embedded in the pipeline 160, and pipeline 160 is connected between radiator 20 and the injector 40 as the refrigerant passage device fluid.Pipeline 160 is covered with certain heat insulator 161 so that refrigerant passage and air are carried out the heat isolation.
Fig. 8 be two kinds of situations relatively, promptly pipeline 160 is covered with the not situation of cover heating insulator 161 of the situation of heat insulator 161 and pipeline 160.As shown in Figure 8, around pipeline 160, heat insulator 161 is set and has improved the coefficient of performance (COP).
When by internal exchanger 70 between high-pressure refrigerant and low pressure refrigerant during heat-shift, the enthalpy amount of supplying with the cold-producing medium of injector 40 will reduce and reduce the performance of injector.Yet,, can become big so caloric receptivity is a thermal absorption capacity (refrigerating capacity) because the enthalpy amount difference between the enthalpy amount of the cold-producing medium at the enthalpy amount of the cold-producing medium at evaporimeter 30 refrigerant inlet places and evaporimeter 30 refrigerant outlet places increases.
(other embodiment)
As mentioned above, when the adiabatic heat potential difference increases when refrigerant pressure reduces and expands, advantage of the present invention will be more remarkable.Therefore, the present invention is specially adapted to require the temperature (evaporating temperature) in the evaporimeter 30 to be equal to or less than 0 degree centigrade vapor compression refrigeration system.The example of this vapor compression refrigeration system comprises the refrigerating plant of temperature requirement about-20 degrees centigrade in certain refrigerating plant.
In above embodiment, pipeline 60,160 is covered with certain heat insulator 61,161 so that refrigerant passage and air heat are isolated.The present invention is not limited in this set.For example, pipeline 60,160 itself just can be made by heat-insulating material.As selection, also heat Insulation film can be sticked to around the pipeline 60,160.As selection, heat-insulating material (as foam resin) can be injected in pipeline 60,160 around.Equally, pipeline 60,160 also can be made by the synthetic of heat-insulating material and corrosion-resistant material.
In addition, can prevent also that pipeline 60,160 ambient air temperature from dropping to and be lower than radiator 20 ambient air temperature, and the influence of the cold-producing medium of cross-ventilation piping 60,160 is reduced to minimum, refrigerant passage and air thermal isolation like this.
In addition, cold-producing medium also has more than and is limited to carbon dioxide or chlorofluorocarbon (CFC).For example, hydrocarbon also can be used as cold-producing medium.
For those skilled in the art, will expect other advantage and improvement easily.Therefore, from wideer angle, the present invention is not limited in above-mentioned clear and definite detailed content.
Claims (8)
1. vapor compression refrigeration system, described vapor compression refrigeration system transmits heat from a side of a side direction high temperature of low temperature, and wherein the temperature of high temperature one side is higher than the temperature of low temperature one side, and described vapor compression refrigeration system comprises:
Cold-producing medium is separated into the vapour-liquid separator (50) of gaseous refrigerant and liquid refrigerant;
The compressor of a compressed refrigerant (10);
The radiator (20) that the high-pressure refrigerant that compressor (10) is discharged cools off;
The evaporimeter of a vaporized refrigerant (30);
An injector (40), described injector reduces the high-pressure refrigerant pressure of supplying with from radiator (20) and expands to extract the vaporized refrigerant that has evaporated of evaporation in evaporimeter (30), and injector (40) just is converted to the expansion energy of cold-producing medium pressure energy and has improved the admission pressure of compressor (10) like this; And
Be used for described liquid refrigerant is directed to the conduit (5) of evaporimeter (30), described conduit (5) is from refrigerant loop branch, this refrigerant loop comprises compressor (10), radiator (20), injector (40) and vapour-liquid separator (50), wherein supply with vapour-liquid separator (50) from the cold-producing medium of injector (40) output
It is characterized in that, described vapor compression refrigeration system is connected the refrigerant passage device (60 between radiator (20) and the injector (40) with comprising fluid, 160), wherein the refrigerant passage device (60,160) be centered around refrigerant passage device (60,160) ambient air heat insulation in fact.
2. vapor compression refrigeration system according to claim 1 is characterized in that refrigerant passage device (60,160) comprises the pipeline (60,160) that is covered with certain heat insulator (61,161).
3. vapor compression refrigeration system according to claim 1, its feature also is from a heat exchanger (70) of heat-shift between the cold-producing medium of the cold-producing medium of radiator (20) discharge and supply compressor (10), wherein heat exchanger (70) is embedded in refrigerant passage device (60,160) in, and with refrigerant passage device (60,160) together with surrounding air heat insulation in fact.
4. vapor compression refrigeration system according to claim 1 is characterized in that cold-producing medium comprises chlorofluorocarbon CFC.
5. vapor compression refrigeration system according to claim 1 is characterized in that cold-producing medium comprises carbon dioxide CO
2
6. vapor compression refrigeration system according to claim 1 is characterized in that cold-producing medium comprises hydrocarbon.
7. vapor compression refrigeration system according to claim 1 is characterized in that the pressure of the high-pressure refrigerant of discharging from compressor (10) is equal to or greater than the critical pressure of cold-producing medium.
8. vapor compression refrigeration system according to claim 1 is characterized in that the duration of work at vapor compression refrigeration system, and this vapor compression refrigeration system is configured in ambient air temperature and remains in fact in the environment that is equal to or less than zero degrees celsius.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002134155 | 2002-05-09 | ||
| JP2002134155A JP4016711B2 (en) | 2002-05-09 | 2002-05-09 | Vapor compression refrigerator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1456851A CN1456851A (en) | 2003-11-19 |
| CN1226583C true CN1226583C (en) | 2005-11-09 |
Family
ID=29267738
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN03123602.2A Expired - Fee Related CN1226583C (en) | 2002-05-09 | 2003-05-09 | Vapour compression refrigerating system with jector |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20030209031A1 (en) |
| JP (1) | JP4016711B2 (en) |
| CN (1) | CN1226583C (en) |
| DE (1) | DE10320378A1 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4114544B2 (en) * | 2003-05-28 | 2008-07-09 | 株式会社デンソー | Ejector cycle |
| JP4835296B2 (en) * | 2006-07-18 | 2011-12-14 | 株式会社デンソー | Ejector refrigeration cycle |
| JP2009300027A (en) * | 2008-06-16 | 2009-12-24 | Nippon Soken Inc | Ejector and ejector type refrigerating cycle |
| CN103270379B (en) * | 2011-01-04 | 2016-03-16 | 开利公司 | Injector |
| CN113038787B (en) * | 2020-12-22 | 2022-10-18 | 中科可控信息产业有限公司 | Phase change heat dissipation structure and heat dissipation device |
| CN113701389B (en) * | 2021-04-30 | 2022-11-01 | 中国科学院理化技术研究所 | Carbon dioxide refrigerating system and refrigerator of condensation separation type supersonic ejector |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5520009A (en) * | 1992-08-31 | 1996-05-28 | Rockwool International A/S | Method and apparatus for insulating |
| US5343711A (en) * | 1993-01-04 | 1994-09-06 | Virginia Tech Intellectual Properties, Inc. | Method of reducing flow metastability in an ejector nozzle |
| US5924303A (en) * | 1998-03-09 | 1999-07-20 | California Innovations Inc. | Insulated soft-sided portable case having externally accessible receptacle |
| US20020035845A1 (en) * | 1999-10-22 | 2002-03-28 | David Smolinsky | Heating and refrigeration systems using refrigerant mass flow |
| JP2003002048A (en) * | 2000-08-28 | 2003-01-08 | Denso Corp | Air conditioner for vehicle |
| US6460358B1 (en) * | 2000-11-13 | 2002-10-08 | Thomas H. Hebert | Flash gas and superheat eliminator for evaporators and method therefor |
| US6446461B1 (en) * | 2001-02-20 | 2002-09-10 | David L. Williams, Jr. | Beverage cooler |
| WO2003023296A2 (en) * | 2001-09-11 | 2003-03-20 | Abfalter James M | Portable cooler chest |
-
2002
- 2002-05-09 JP JP2002134155A patent/JP4016711B2/en not_active Expired - Fee Related
-
2003
- 2003-05-07 DE DE10320378A patent/DE10320378A1/en not_active Withdrawn
- 2003-05-08 US US10/431,808 patent/US20030209031A1/en not_active Abandoned
- 2003-05-09 CN CN03123602.2A patent/CN1226583C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JP4016711B2 (en) | 2007-12-05 |
| DE10320378A1 (en) | 2003-11-20 |
| CN1456851A (en) | 2003-11-19 |
| US20030209031A1 (en) | 2003-11-13 |
| JP2003329315A (en) | 2003-11-19 |
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