CN101592412B - Adjustable multi-temperature refrigeration device - Google Patents
Adjustable multi-temperature refrigeration device Download PDFInfo
- Publication number
- CN101592412B CN101592412B CN2009100321374A CN200910032137A CN101592412B CN 101592412 B CN101592412 B CN 101592412B CN 2009100321374 A CN2009100321374 A CN 2009100321374A CN 200910032137 A CN200910032137 A CN 200910032137A CN 101592412 B CN101592412 B CN 101592412B
- Authority
- CN
- China
- Prior art keywords
- temperature
- refrigeration
- refrigerant
- regenerator
- condenser
- Prior art date
Links
- 238000005057 refrigeration Methods 0.000 title claims abstract description 48
- 239000003507 refrigerants Substances 0.000 claims abstract description 65
- 238000001704 evaporation Methods 0.000 claims abstract description 39
- 239000007788 liquids Substances 0.000 claims abstract description 25
- 230000000875 corresponding Effects 0.000 claims abstract description 7
- 238000000034 methods Methods 0.000 claims abstract description 7
- 239000003570 air Substances 0.000 claims abstract description 5
- 238000009833 condensation Methods 0.000 claims description 26
- 230000005494 condensation Effects 0.000 claims description 26
- 238000009835 boiling Methods 0.000 claims description 19
- 239000012071 phases Substances 0.000 claims description 18
- 239000000203 mixtures Substances 0.000 claims description 17
- 239000006200 vaporizer Substances 0.000 claims description 15
- 238000001816 cooling Methods 0.000 claims description 13
- 239000007791 liquid phases Substances 0.000 claims description 11
- 239000011901 water Substances 0.000 claims description 8
- 230000011218 segmentation Effects 0.000 claims description 6
- 239000004215 Carbon black (E152) Substances 0.000 claims description 4
- 150000002430 hydrocarbons Chemical class 0.000 claims description 4
- QGZKDVFQNNGYKY-UHFFFAOYSA-N ammonia Chemical compound data:image/svg+xml;base64,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 data:image/svg+xml;base64,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 N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 claims description 2
- 238000010438 heat treatment Methods 0.000 claims description 2
- 239000011257 shell materials Substances 0.000 claims description 2
- 150000002894 organic compounds Chemical class 0.000 claims 1
- 238000007906 compression Methods 0.000 abstract description 9
- 238000005516 engineering processes Methods 0.000 abstract description 6
- 238000004378 air conditioning Methods 0.000 abstract 1
- 230000001276 controlling effects Effects 0.000 abstract 1
- 230000002950 deficient Effects 0.000 description 5
- 230000002427 irreversible Effects 0.000 description 5
- 230000001131 transforming Effects 0.000 description 4
- 238000010586 diagrams Methods 0.000 description 3
- 230000001105 regulatory Effects 0.000 description 3
- 238000004821 distillation Methods 0.000 description 2
- 238000007710 freezing Methods 0.000 description 2
- 239000007789 gases Substances 0.000 description 2
- 239000003643 water by type Substances 0.000 description 2
- 208000008454 Hyperhidrosis Diseases 0.000 description 1
- 210000004243 Sweat Anatomy 0.000 description 1
- 230000003416 augmentation Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000009408 flooring Methods 0.000 description 1
- 150000002484 inorganic compounds Chemical class 0.000 description 1
- 229910010272 inorganic materials Inorganic materials 0.000 description 1
- 238000002360 preparation methods Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000035900 sweating Effects 0.000 description 1
- 239000011701 zinc Substances 0.000 description 1
Classifications
-
- Y02P20/124—
Abstract
Description
Technical field
The present invention relates to a kind of compression refrigerating system with several evaporation circuits, be particularly related to and a kind of mixed non-azeotropic refrigerant carried out the compression refrigerating system that segmentation condensation and proportioning realize temperature at different levels and the adjustable many temperature refrigeration of refrigerating capacity, belong to refrigeration technology field.
Background technology
Current society needs many temperature cooling in many instances, but existing vapor-compression refrigerant cycle can only realize single-system and single temperature refrigeration, system has only a pressure of inspiration(Pi), kind of refrigeration cycle based on pure working medium cold-producing medium can only provide an evaporating temperature usually, under single temperature, provide refrigerating capacity, can not satisfy the demand of many temperature refrigeration.Refrigeration industry lacks the technology of many temperature of unit kind of refrigeration cycle aspect at present, and the demand in reply market adopts the technical finesse of some compromises on the engineering.Such as, in the HVAC technology of novel radiation end (ceiling radiation or flooring radiation), needing the fresh air supply system simultaneously, new blower fan group needs about 7 ℃ of chilled water supply temperatures, to satisfy the dehumidifying requirement to air; And for fear of surface sweating, the terminal chilled water that needs of radiation is about 18～20 ℃, at new wind and terminal employing of radiation two methods of overlapping different units are installed respectively on the engineering at present, satisfy the requirement of two kinds of different temperatures chilled waters, also there is the defective that two groups of chilled waters are separate, can not adjust mutually in this method except cost is higher.Refrigerator and for example, two temperature refrigerator (freezing, refrigeration) and three temperature refrigerators (freezing, fresh-keeping, refrigeration) are arranged, freezer temperature requires between-18 ℃, fresh-keeping chamber requires-7 ℃, refrigerating chamber requires 5 ℃, and the refrigerator technology adopts the refrigerating capacity that the method for refrigerant superheat is obtained higher evaporating temperature at present.These existing methods have reduced the efficient of compression set, have introduced bigger heat transfer temperature difference, cause very big irreversible heat transfer loss; Simultaneously, the refrigerant loop string being aligned of each operating room, the each several part refrigerating capacity influences each other, and can not adapt to the requirement that refrigerating capacity changes.Be based upon the Refrigeration Technique on single temperature kind of refrigeration cycle in a word, can not satisfy the demand of many temperature refrigeration,, have the defective of aspects such as cost height, COP is low, the cooling amount does not match its place that is applied in many temperature refrigeration.
Utilize the automatic cascade principle of non-azeotropic mixed working medium, can set up the kind of refrigeration cycle of the many temperature of a machine.But, up to the present, non-azeotropic mixed working medium automatic cascade formula refrigerating circulatory device is mainly used in-60 ℃～-200 ℃ low temperature field, its objective is in order to obtain maximum cooling capacity and refrigerating efficiency, high-purity ground separation efficient that major technique is embodied in to the minimum boiling point component in the target low district.Automatic cascade is only required a cryogenic temperature (temperature range), and the refrigerating capacity of high boiling component just is used for the minimum boiling point component in the condenser system, need externally not provide extra refrigerating capacity in medium temperature.Therefore this device surface needs further improvement to the needs of many temperature cooling.
In order to realize the kind of refrigeration cycle of the many temperature of non-azeotropic working medium one machine, can select the working medium of different pressures curve to form the non-azeotropic mixed working medium system, adopt a compression set to carry out single stage compress, when condensation, carry out the superposition type evaporative condenser, mixed working fluid is condensed into a plurality of parts according to the boiling point characteristic, contain the refrigerating capacity that the high part of higher boiling molecular concentration can be used to produce higher cryogenic temperature, contain the high part of low boiling concentration and be used to produce the low temperature refrigerating capacity.Like this can be according to the different demands of cryogenic temperature, overlapping is condensed into a plurality of condensate liquids that contain the different boiling different proportion, satisfies the requirement of many temperature kind of refrigeration cycle.In addition, utilize non-azeotropic refrigerant to have the characteristics of phase transformation slip temperature, can also be by methods such as augmentation of heat transfers, reduce the heat transfer temperature difference in the heat exchanger, and make whole diabatic process keep approximately equalised heat transfer temperature difference, and reduce irreversible heat transfer loss, improve the COP of system.
There has been similar patent in many temperature of single stage compress refrigeration system for using mixed non-azeotropic refrigerant.But the system that disclosed patent and the present invention propose exists than big difference, and some also exists obvious defects to need to improve, such as:
Among the granted patent CN 2667412Y disclosed " the how warm unit vapor compression type refrigerator of a kind of unit ", adopt the method for distillation or rectifying " mix refrigerant to be separated and all liquefaction successively ", each component in the mix refrigerant is separated into one pack system working medium successively carries out sweat cooling respectively, this method has been ignored the advantage that mixed non-azeotropic refrigerant has the phase transformation slip temperature, can increase the heat transfer temperature difference in the heat exchanger, therefore the reduction heat exchanger efficiency uses complicated distillation or rectifying device that mix refrigerant is separated successively and whole liquefaction there is no need fully; In addition, in its disclosed device specific embodiment, adopt the mode of evaporimeter and condenser/evaporator series connection, use the cold-producing medium overheated or that part is overheated of evaporator outlet that the low boiling gaseous refrigerant is carried out condensation, because the refrigerating capacity overheated or cold-producing medium that part is overheated is limited, therefore the mode of this series connection is difficult to the effective condensation of realization to the low boiling gaseous refrigerant, thereby can reduce system effectiveness.
Among the publication number CN 101025312A disclosed " preparation method with how warm refrigeration machine of variable evaporating temperature ", only can realize " wherein the one-level evaporating temperature can be adjusted according to customer requirements ", the flexibility of system and economy are not high; Simultaneously, the adjusting of its evaporating temperature is by using the three-way flowrate distributing valve to connect certain one-level
(high temperature or low temperature) evaporator outlet and another level (low temperature or high temperature) evaporator inlet are realized, because the cold-producing medium of evaporator outlet is overheated gas or the overheated gas-liquid mixture of part, assignment of traffic for gas-liquid mixture is to be difficult to realize, and the liquid refrigerant of overheated gas with another grade evaporator inlet mixed, be very little to the regulating action of evaporating temperature; Secondly, because cold-producing medium has increased the flow process of an evaporimeter, the refrigerant pressure of high temperature (or low temperature) evaporator outlet is the inlet pressure that is lower than another grade evaporimeter, therefore only rely on triple valve also can't realize the assignment of traffic of cold-producing medium, can occur because there being pressure reduction on the contrary with its literary composition in the alleged opposite flow direction, the reliability and the actuality of system all have problems.
Summary of the invention
Technical problem: the purpose of this invention is to provide a kind of temperature at different levels and refrigerating capacity adjustable multi-temperature refrigeration device based on non-azeotropic mixed working medium, realize the refrigeration system of the many temperature of a machine, utilize the automatic cascade principle of non-azeotropic mixed working medium, the cost height that uses two cover units or utilize refrigerant superheat to provide the two temperature refrigerating capacity to exist is provided, COP is low, the defective of aspects such as the cooling amount does not match, solving traditional non-azeotropic mixed working medium automatic cascade formula refrigerating circulatory device simultaneously can only provide the shortcoming of refrigerating capacity under a cryogenic temperature, in addition, improving the two parts that use evaporation and condensation series connection to occur in existing many temperature Refrigeration Technique pins down mutually, regulating power difference or only can realize the single-stage adjustment, can not make full use of non-azeotropic mixed working medium slip temperature or the like defective.
Technical scheme: adjustable multi-temperature refrigeration device of the present invention comprises compressor, condenser, gas-liquid separator, regenerator, triple valve, throttling expansion device, high-temperature evaporator, evaporative condenser, cryogenic vaporizer; Between the import of each evaporation circuit and outlet, regenerator is set; The evaporimeter in high temperature evaporation loop and evaporative condenser parallel connection; Before the throttling expansion device of high-temperature evaporator and cryogenic vaporizer, triple valve is set respectively; Device uses binary or polynary mixed non-azeotropic refrigerant, adopts the mode of segmentation condensation, and condensation goes out the mix refrigerant of multiply variable concentrations, satisfies the requirement of cryogenic temperatures at different levels and refrigerating capacity; By introducing the concentration that liquid refrigerant on a certain proportion of other cryogenic temperatures changes mix refrigerant at the corresponding levels, realize adjusting to cryogenic temperature at the corresponding levels; Utilize the slip temperature of mixed non-azeotropic refrigerant simultaneously,, reduce heat transfer temperature difference, reduce the irreversible heat transfer loss in the heat exchanger, improve refrigerating efficiency by the optimal design of heat exchanger.
The adjustable multi-temperature refrigeration device that the present invention announces, use the separate unit compressor that mix refrigerant is compressed, the mix refrigerant of HTHP is disposed to condenser by compressor outlet, be condensed into gas-liquid two-phase working medium therein, in gas-liquid separator, be condensed into subsequently and contain the more liquid phase refrigerant of high boiling component and contain the more vapor phase refrigerant of low boiling component by segmentation; Two parts cold-producing medium enters two evaporation circuits respectively: liquid phase refrigerant is divided into two parts again after by first regenerator, a part is through first triple valve, entering high-temperature evaporator evaporation after the throttling expansion provides refrigerating capacity QH, another part to enter evaporative condenser behind the throttling expansion device vapor phase refrigerant is wherein carried out condensation; Vapor phase refrigerant enters the liquid phase refrigerant condensation wherein of evaporative condenser quilt, afterwards through second regenerator, second triple valve, enters the cryogenic vaporizer evaporation after the throttling refrigerating capacity QL is provided.Reach overheated by first regenerator after the refrigerant mixed of coming out from high-temperature evaporator and evaporative condenser, the cold-producing medium that comes out from cryogenic vaporizer reaches overheated by second regenerator, this two parts superheated refrigerant is mixed into compressor subsequently, the next circulation of beginning.
This apparatus features is that also high-temperature evaporator in the high temperature evaporation loop and evaporative condenser can use an evaporative condenser refrigerator to replace; Simultaneously, when cooling loads at different levels do not need to regulate cryogenic temperature and refrigerating capacity than stablizing, can save the triple valve between the double flash evaporation loop; When two above evaporating temperatures of needs, can realize many temperature refrigeration by increasing the intergrade evaporation circuit; On the basis of these variations, can form various system pattern, make system flexible and changeable, reduce investment outlay.
In this device, condenser can use but be not limited to following form: water cooled condenser, air cooled condenser, evaporative condenser; High-temperature evaporator (or evaporative condenser refrigerator) and cryogenic vaporizer can use but be not limited to following form: shell and tube evaporator, bushing type evaporimeter, water tank type evaporimeter, cooling coil, fan coil; The throttling expansion device can use but be not limited to following form: heating power expansion valve, electric expansion valve, capillary-compensated device; The employed mixed working fluid of system can require to adopt corresponding pure working medium to carry out proportioning according to the different application of device, working medium can be selected for use but be not limited to following kind: hydrocarbon refrigerant, halogenate hydrocarbon refrigerant, ammonia, water, CO 2, the inorganic compound cold-producing medium.
Beneficial effect:
1, the present invention uses the separate unit compressor to carry out the single-stage steam compression cycle, by the non-azeotropic working medium fractional condensaion being become the multiply working medium in different evaporating temperatures interval, produces the refrigerating capacity under a plurality of cryogenic temperatures simultaneously, can satisfy the demand of many temperature cooling.
2, the present invention adopts the form of evaporimeter and condenser parallel connection in the high temperature evaporation loop, can distribute cold-producing medium according to high temperature cooling load and cryogenic condensation load, avoid evaporimeter and the condensation number deficiency of condenser series connection generation and the defective of very flexible.
3, the present invention is provided with triple valve connection double flash evaporation loop before the throttling expansion device, can carry out Flow-rate adjustment to the cold-producing medium of different boiling, according to payload and load temperature, proportioning goes out the mix refrigerant of variable concentrations and different temperatures on loops at different levels, by the optimal design of heat exchanger, can make full use of the slip temperature of mixed non-azeotropic refrigerant, reduce the heat transfer temperature difference of heat exchanger, reduce irreversible loss, improve system effectiveness.
4, each evaporation circuit of the present invention all is provided with regenerator, can not only utilize the residue cold of evaporator outlet cold-producing medium to improve system effectiveness, and can improve the compressor inlet refrigerant condition, improves system reliability.
5, the mixed non-azeotropic refrigerant of the present invention's use can require according to the different application to device to adopt different component and concentration proportioning, can reach best system effectiveness.
Description of drawings
Fig. 1 is the system diagram of basic two temperature refrigerating plant of the present invention.
Fig. 2, Fig. 3, Fig. 4 are the system diagram of three kinds of different device patterns of two temperature refrigerating plant of the present invention.
Fig. 5 is the system diagram of multi-temperature refrigeration device of the present invention.
The specific embodiment
Embodiment 1, referring to Fig. 1.Comprise compressor 1, condenser 2, gas-liquid separator 3, evaporative condenser 4, cryogenic vaporizer 5, first regenerator 6, second regenerator 7, first throttle expansion gear 8, the second throttling expansion device 9, first triple valve 10, second triple valve 11, the 3rd throttling expansion device 12, high-temperature evaporator 13.Condenser 2 is with the HTHP mix refrigerant partial condensation of compressor 1 outlet and discharge condensation heat QC, and gained gas-liquid two-phase cold-producing medium enters in the gas-liquid separator 3 and is condensed into two parts by segmentation: contain the more liquid phase refrigerant of high boiling component and contain the more vapor phase refrigerant of low boiling component.Wherein liquid phase refrigerant enters the high temperature evaporation loop by the first output 3a, cross through regenerator and to be divided into two parts after cold again: a part enters high-temperature evaporator 13 through first triple valve 10 and the 3rd throttling expansion device 12 and evaporate under higher temperature refrigerating capacity QH externally is provided, and another part passes through first throttle expansion gear 8 and enters 4 pairs of evaporative condensers and contain the more vapor phase refrigerant of low boiling component and carry out condensation; Vapor phase refrigerant is entered the evaporative condenser 4 in high temperature evaporation loop by the second output 3b, enter after the condensation therein second regenerator 7 produced cold, with after second triple valve 11 and the second throttling expansion device 9 enter cryogenic vaporizer 5 evaporates at a lower temperature refrigerating capacity QL externally is provided.
High-temperature liquid-phase cold-producing medium of separating from gas-liquid separator 3 and the low temperature liquid phase cold-producing medium of crossing after cold through second regenerator 7 can carry out Flow-rate adjustment by first triple valve 10 and second triple valve 11, requirement according to corresponding refrigerating capacity and cryogenic temperature, hybrid refrigeration agent concentration and the flow that enters in high-temperature evaporator 13 and the cryogenic vaporizer 5 is optimized proportioning, thereby can utilize the phase transformation slip temperature of mixed non-azeotropic refrigerant, reduce heat transfer temperature difference, improve system effectiveness;
Embodiment 2, referring to Fig. 2.Be with the different of embodiment 1, from the first output 3a of gas-liquid separator 3 output contain the many liquid phase refrigerants of high boiling component first regenerator 6, cross cold after, through first triple valve 10 and first throttle expansion gear 8, enter evaporative condenser 4, cold-producing medium evaporates condensation when refrigerating capacity QH externally is provided therein and contains the many vapor phase refrigerant of low boiling component from the second output 3b output of gas-liquid separator 3.Use evaporative condenser 4 has replaced high-temperature evaporator and the evaporative condenser among the embodiment 1 in this system, evaporative condenser 4 possesses simultaneously externally provides refrigerating capacity and to two functions of vapor phase refrigerant condensation, and saved a throttling expansion device, therefore can reduce equipment volume, save cost of equipment.
Embodiment 3, referring to Fig. 3.Little at cooling load and variations in temperature, when evaporating temperatures at different levels and refrigerating capacity do not need to regulate, can remove the triple valve that is provided with on the double flash evaporation loop on the basis of embodiment 1, should determine the component and the concentration of cold-producing medium this moment according to the application requirements of refrigerating plant.Simultaneously, still can control the component that enters mix refrigerant in the evaporation circuits at different levels,, reduce irreversible heat transfer loss to make full use of the phase transformation slip temperature of mixed non-azeotropic refrigerant by the partial condensation amount in the control condenser 2.
Embodiment 4, referring to Fig. 4.Do not need the situation of regulating for temperature at different levels, can on the basis of embodiment 3, further use the evaporative condenser refrigerator to replace high-temperature evaporator and evaporative condenser, can save cost of equipment, reduce equipment volume.
Embodiment 5, referring to Fig. 5.On the basis of two temperature refrigeration system, can realize many temperature refrigeration system by evaporation circuit in the middle of increasing.In many temperature refrigeration system, middle evaporation circuit Z1 comprises first order gas-liquid separator 3-1 and output 3a-1,3b-1, evaporative condenser 4-1 in the middle of the first order, regenerator 6-1 in the middle of the first order, first order first throttle expansion gear 8-1, the first order second throttling expansion device 10-1, cold-producing medium evaporate in first order central evaporator 11-1 externally provides refrigerating capacity Q1, the composition of other middle evaporation circuit Z2......Zn at different levels and the like, refrigerating capacity Q2......Qn can externally be provided.In many temperature refrigeration system, can increase the interstage flow adjusting device equally, realize adjusting to cryogenic temperatures at different levels and refrigerating capacity.
Claims (4)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100321374A CN101592412B (en) | 2009-07-01 | 2009-07-01 | Adjustable multi-temperature refrigeration device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100321374A CN101592412B (en) | 2009-07-01 | 2009-07-01 | Adjustable multi-temperature refrigeration device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101592412A CN101592412A (en) | 2009-12-02 |
| CN101592412B true CN101592412B (en) | 2011-05-18 |
Family
ID=41407201
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009100321374A CN101592412B (en) | 2009-07-01 | 2009-07-01 | Adjustable multi-temperature refrigeration device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101592412B (en) |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101852503A (en) * | 2010-05-31 | 2010-10-06 | 西安交通大学 | Multi-temperature refrigerator |
| CN101968243B (en) * | 2010-09-21 | 2012-11-28 | 东南大学 | Air source heat pump device capable of simultaneously preparing double-temperature water and driving method thereof |
| CN102003827B (en) * | 2010-11-15 | 2012-02-08 | 思安新能源股份有限公司 | Absorption type power and refrigeration cogeneration circulatory system and absorption type power and refrigeration cogeneration method |
| CN103238031B (en) * | 2010-12-16 | 2016-11-16 | 松下电器产业株式会社 | Chiller and the air conditioner with this chiller |
| CN102147163B (en) * | 2011-03-28 | 2012-11-14 | Tcl空调器(中山)有限公司 | All-weather refrigerating plant and refrigerating mode control method thereof |
| CN102331040B (en) * | 2011-08-05 | 2013-08-07 | 海尔集团公司 | Freon-free direct-current frequency conversion air conditioner and control method |
| CN103673368B (en) * | 2013-12-27 | 2016-04-13 | 天津商业大学 | The folding type cooling system of adjustable compressor air suction temperature |
| CN105202791A (en) * | 2015-09-09 | 2015-12-30 | 江苏宝奥兰空调设备有限公司 | Refrigeration system and method |
| CN105865066A (en) * | 2016-06-29 | 2016-08-17 | 湖南亚华乳业有限公司 | Combined-type raw milk fast cooling system based on non-azeotropic mixtures |
| CN106546024A (en) * | 2016-10-27 | 2017-03-29 | 青岛海尔特种电冰柜有限公司 | Separating refrigerating device |
| CN107521698B (en) * | 2017-07-28 | 2020-04-21 | 中国航空工业集团公司西安飞机设计研究所 | Environment control system waste heat refrigerating device |
| CN108895736B (en) * | 2018-04-02 | 2020-05-01 | 合肥华凌股份有限公司 | Supercooling circulation system control method, supercooling circulation system and refrigerator |
| CN108895693A (en) * | 2018-05-21 | 2018-11-27 | 福建工程学院 | A kind of dual temperature low temp area refrigerator refrigeration system |
| CN109059342B (en) * | 2018-06-21 | 2020-08-04 | 冰轮环境技术股份有限公司 | Low-temperature refrigeration and high-temperature heat supply comprehensive supply system |
| CN111237934A (en) * | 2020-02-29 | 2020-06-05 | 上海弗有冷热控制技术有限公司 | Energy-saving method applied to temperature and humidity control of air conditioner enthalpy difference laboratory |
-
2009
- 2009-07-01 CN CN2009100321374A patent/CN101592412B/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| CN101592412A (en) | 2009-12-02 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR101155494B1 (en) | Heat pump | |
| US3675441A (en) | Two stage refrigeration plant having a plurality of first stage refrigeration systems | |
| US6519967B1 (en) | Arrangement for cascade refrigeration system | |
| CN101084409B (en) | Efficient heat exchanger for refrigeration process | |
| CN103062851B (en) | Air-conditioning system and dehumanization method thereof | |
| JP3102651U (en) | Refrigerator refrigerator with two evaporators | |
| ES2443645T3 (en) | Air conditioner and air conditioner heat source unit | |
| KR100958399B1 (en) | Hvac system with powered subcooler | |
| KR101203579B1 (en) | Speed heating apparatus with air conditioner and Control process of the same | |
| CN103743150B (en) | Absorption compression type automatic-overlapping refrigerating system and use method | |
| CN101240962B (en) | Carbon dioxide heat pump control method based on pressure-temperature | |
| US7032411B2 (en) | Integrated dual circuit evaporator | |
| KR101343711B1 (en) | Air conditioning／hotwater supply system and heat pump unit | |
| CN103154637B (en) | Aircondition | |
| CN100538205C (en) | Preparation method with how warm refrigeration machine of variable evaporating temperature | |
| CN203203199U (en) | Air conditioning device | |
| US20020194857A1 (en) | Multiform gas heat pump type air conditioning system | |
| JP2004183913A (en) | Air conditioner | |
| CN101691960B (en) | Three-pipe heating and reclaiming air-conditioning system | |
| CN102301189B (en) | Air Conditioner And Method Of Returning Refrigerating Machine Oil | |
| CN101762109A (en) | Ejector-type refrigerant cycle device | |
| KR20120045916A (en) | Heat pump type speed heating apparatus | |
| Ko et al. | The selection of volume ratio of two-stage rotary compressor and its effects on air-to-water heat pump with flash tank cycle | |
| CN101446455B (en) | Method for preparing multi-temperature refrigerator with variable evaporation temperature | |
| CN102734971B (en) | Refrigeration device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| EXPY | Termination of patent right or utility model | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110518 Termination date: 20140701 |