CN103808101B - A kind of two injection for two temperature refrigerator and the double back heat integration synergism refrigerating circulatory system - Google Patents
A kind of two injection for two temperature refrigerator and the double back heat integration synergism refrigerating circulatory system Download PDFInfo
- Publication number
- CN103808101B CN103808101B CN201410040517.3A CN201410040517A CN103808101B CN 103808101 B CN103808101 B CN 103808101B CN 201410040517 A CN201410040517 A CN 201410040517A CN 103808101 B CN103808101 B CN 103808101B
- Authority
- CN
- China
- Prior art keywords
- regenerator
- outlet
- injector
- breathing
- air
- 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.)
- Active
Links
- 238000002347 injection Methods 0.000 title claims abstract description 27
- 239000007924 injection Substances 0.000 title claims abstract description 27
- 230000010354 integration Effects 0.000 title claims abstract description 13
- 239000007788 liquid Substances 0.000 claims abstract description 42
- 239000000203 mixture Substances 0.000 claims abstract description 4
- 239000003507 refrigerant Substances 0.000 claims description 65
- 239000012530 fluid Substances 0.000 claims description 30
- 238000001816 cooling Methods 0.000 claims description 27
- 229920006395 saturated elastomer Polymers 0.000 claims description 22
- 239000011555 saturated liquid Substances 0.000 claims description 12
- 238000010521 absorption reaction Methods 0.000 claims description 11
- 238000002156 mixing Methods 0.000 claims description 6
- 238000010438 heat treatment Methods 0.000 claims description 5
- 238000000034 method Methods 0.000 abstract description 31
- 238000005057 refrigeration Methods 0.000 abstract description 18
- 238000005516 engineering process Methods 0.000 description 8
- 238000001704 evaporation Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 238000004134 energy conservation Methods 0.000 description 4
- 238000011161 development Methods 0.000 description 3
- 230000009977 dual effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000007599 discharging Methods 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 238000000605 extraction Methods 0.000 description 2
- 230000002427 irreversible effect Effects 0.000 description 2
- 238000011084 recovery Methods 0.000 description 2
- 239000007921 spray Substances 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000009897 systematic effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000001035 drying Methods 0.000 description 1
- 238000001914 filtration Methods 0.000 description 1
- 239000012774 insulation material Substances 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 238000012827 research and development Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 210000004243 sweat Anatomy 0.000 description 1
- 230000002195 synergetic effect Effects 0.000 description 1
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
-
- 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
- F25B2341/0015—Ejectors not being used as compression device using two or more ejectors
-
- 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)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Sorption Type Refrigeration Machines (AREA)
Abstract
The invention discloses a kind of two injection for two temperature refrigerator and the double back heat integration synergism refrigerating circulatory system, it is characterized in that, its composition comprises: compressor, exhaust regenerator, condenser, air-breathing regenerator, the first capillary, the second capillary, refrigerator evaporator, the first injector, the second injector, freezer evaporator and gas-liquid separator.The present invention fully can reclaim and utilize the expansion work in throttling process and available energy, significantly promotes and improve efficiency and the performance of two warm Refrigeration Cycle of Refrigerator system.
Description
Technical field
The invention belongs to refrigerator refrigeration technology field, be specifically related to a kind of two injection for two temperature refrigerator and the double back heat integration synergism refrigerating circulatory system.
Background technology
There is deep reform in current household electrical appliances market, energy-saving, intellectuality, personalized product become the main trend of industry development.Wherein, the refrigerator power-saving technology energy-conservation important theme with environmental protection of field of household appliances just.Through research and development in recent years, the power-saving technology of refrigerator there has also been significant progress, is included in many-sided power-economizing method and the technology such as insulation material, door seal, compressor, condenser, cooling cycle system, control system.
At present, what household refrigeration deep freezer mainly adopted is traditional steam compressed refrigerating circulating system, comprises compressor, condenser, device for drying and filtering, capillary, refrigerating chamber and refrigerating chamber two evaporimeters.During refrigeration system work, by capillary to cold-producing medium throttling action, through the cold-producing medium sweat cooling effect of two evaporimeters, achieve refrigerating chamber and refrigerating chamber temperature requirement separately.
But capillary-compensated process has larger irreversible loss, make cooling cycle system efficiency relatively low.Although existing researcher proposes and injector is introduced Vapor Compression Refrigeration Cycle both at home and abroad, form compression/injecting type hybrid refrigeration cycle and be applied to the two warm refrigerator of refrigerating.In these compression/injecting type hybrid refrigeration cycle schemes, mainly include compression/injecting type hybrid refrigeration cycle and other similar fashion of two-storage temperature refrigerator refrigerating chamber and freezer evaporator series and parallel connections.But, in these endless form, employing be that single injector realizes reclaiming the demi-inflation merit of throttling process, thus improve in systematic function limited in one's ability.In addition, in traditional steam compressed refrigerating circulating system, although additionally use compressor air suction backheat to improve the performance of cooling cycle system, most of available energy is still had to be underutilized.
Summary of the invention
The present invention is the weak point solving the existence of above-mentioned prior art, a kind of economy is provided, effective, feasible sprays the cooling cycle system with double back heat integration synergy for the two of two temperature refrigerator, fully can reclaim and utilize the expansion work in throttling process and available energy, significantly promoting and improve efficiency and the performance of two warm Refrigeration Cycle of Refrigerator system.
For achieving the above object, the technical solution adopted in the present invention is:
The present invention is a kind of, and to spray with the feature of the cooling cycle system of double back heat integration synergy for two temperature refrigerator two be that its composition comprises: compressor, be vented regenerator, condenser, air-breathing regenerator, the first capillary, the second capillary, refrigerator evaporator, the first injector, the second injector, freezer evaporator and gas-liquid separator;
The zone of heat liberation entrance of the outlet of described compressor, the zone of heat liberation of exhaust regenerator, condenser, air-breathing regenerator is arranged in series successively; The zone of heat liberation outlet of described air-breathing regenerator is divided into two-way;
One tunnel is connected with the entrance of described refrigerator evaporator after the first capillary, and the outlet of institute's refrigerator evaporator is connected with the nozzle entrance of the first injector after the cold fluid pass of described exhaust regenerator;
Another road is directly connected with the nozzle entrance of described second injector; The outlet of described second injector and being connected by injection refrigerant inlet of the first injector;
The described outlet of the first injector is connected with the entrance of gas-liquid separator; The outlet of described gas-liquid separator is divided into saturated gaseous state refrigerant outlet and saturated liquid refrigerant outlet;
Described saturated gaseous state refrigerant outlet is connected with the entrance of compressor after the cold fluid pass of described air-breathing regenerator;
Described saturated liquid refrigerant outlet is connected with the entrance of freezer evaporator after the second capillary, the outlet of described freezer evaporator and being connected by injection refrigerant inlet of described second injector.
The two injection that the present invention is used for two warm refrigerator is also with the feature of the cooling cycle system of double back heat integration synergy:
The low-temp low-pressure gaseous refrigerant of described freezer evaporator outlet is carried out the high pressure sub-cooled liquid refrigerant injection of the zone of heat liberation outlet of Self inhaling regenerator in the second injector, mixes after supercharging becomes gas-liquid two-phase cold-producing medium and draw in the second injector;
The gas-liquid two-phase cold-producing medium of described second injector outlet by the overheated gaseous refrigerant injection of the cold fluid pass outlet from exhaust regenerator, mixes after supercharging becomes gas-liquid two-phase cold-producing medium and enters gas-liquid separator in the first injector in the first injector.
The overheated gaseous refrigerant of HTHP of described compressor outlet enters exhaust regenerator by the zone of heat liberation entrance being vented regenerator, is exported draw and enter condenser in exhaust regenerator after heat release cooling by the zone of heat liberation of exhaust regenerator;
The saturated gaseous refrigerant that refrigerator evaporator exports enters exhaust regenerator by the cold fluid pass entrance being vented regenerator, and in exhaust regenerator, heat absorption is drawn by the cold fluid pass outlet of exhaust regenerator and entered the nozzle entrance of the first injector after heating up.
The saturated liquid refrigerant of high pressure of condensator outlet enters air-breathing regenerator by the zone of heat liberation entrance of air-breathing regenerator, is exported draw in air-breathing regenerator after heat release cooling by the zone of heat liberation of air-breathing regenerator; The saturated gaseous refrigerant of the saturated gaseous state refrigerant outlet of gas-liquid separator enters air-breathing regenerator by the cold fluid pass entrance of air-breathing regenerator, and in air-breathing regenerator, heat absorption is drawn by the cold fluid pass outlet of air-breathing regenerator and entered compressor after heating up.
Compared with the injector synergy circulatory system of routine, beneficial effect of the present invention is embodied in:
1, the present invention utilizes the dual jet of reasonable Arrangement fully to reclaim the expansion work of two-way cold-producing medium throttling process in refrigeration system, significantly promotes suction pressure of compressor thus reduces the power consumption of compressor in circulation and improve the displacement of compressor; And utilize compressor air-discharging backheat mode to reclaim the available energy of the high temperature refrigerant superheated vapor that compressor is discharged, improve the boosting effect of injector and the refrigerating efficiency of the circulatory system further; Refrigerating chamber and freezer evaporator can also be realized maintain different evaporating temperatures and freeze simultaneously simultaneously, thus effectively improve the performance of two warm Refrigeration Cycle of Refrigerator system.
2, the present invention effectively overcomes the irreversible loss of capillary-compensated process, make full use of the available expansion work in the throttling process of cold-producing medium, by the demi-inflation merit adopting additional injector to reclaim throttling process in traditional vapor compression type refrigerating system, the refrigeration performance of refrigeration system is improved, thus realizes energy-saving and emission-reduction.
3, the present invention has fully excavated the huge recovery potentiality of the expansion work of cold-producing medium throttling process in two-storage temperature refrigerator refrigeration system, utilizes dual jet and reasonably arranges, strengthens the recovery of expansion work, makes the refrigerating efficiency of cooling cycle system be improved further.
4, the present invention adopts compressor air-discharging backheat and is combined with dual jet, the refrigeration performance of cooling cycle system is made to be significantly improved further, in traditional steam compressed refrigerating circulating system, the refrigerant superheat steam that compressor is discharged still has utilizable available energy because its temperature is higher, particularly under higher ambient temperature conditions, therefore, by two injection and double back heat integration synergistic manner, maximally utilise the available energy in steam compressed refrigerating circulating system, reach better energy-saving effect, positive impetus is had to the development of the two warm refrigerator product power-saving technology of refrigerating.
5, the present invention effectively can improve two warm Refrigeration Cycle of Refrigerator systematic function, advance the development of household electric refrigerator product power-saving technology, improve the energy-conservation and Environmental Protection Level of refrigerator, promote that China's refrigerator product is in the leading position of global refrigerator industry field of energy-saving technology, and promote refrigerator product competitiveness in the international market, and then produce huge economic benefit and positive social benefit.
Accompanying drawing explanation
Fig. 1 is cooling cycle system schematic diagram of the present invention;
Fig. 2 is that the present invention is vented regenerator schematic diagram;
Fig. 3 is air-breathing regenerator schematic diagram of the present invention;
Fig. 4 is the pressure-enthalpy diagram (p-h figure) of the cooling cycle system course of work of the present invention;
Number in the figure: 105 first capillaries; 111 second capillaries; 107 first injectors; 108 second injectors; 110 gas-liquid separators; The zone of heat liberation entrance of 112 exhaust regenerators; The zone of heat liberation outlet of 113 exhaust regenerators; The cold fluid pass entrance of 114 exhaust regenerators; The cold fluid pass outlet of 115 exhaust regenerators; The zone of heat liberation entrance of 116 air-breathing regenerators; The zone of heat liberation outlet of 117 air-breathing regenerators; The cold fluid pass entrance of 118 air-breathing regenerators; The cold fluid pass outlet of 119 air-breathing regenerators.
Detailed description of the invention
As shown in Figure 1, a kind of two injection for two temperature refrigerator comprises with the composition of the cooling cycle system of double back heat integration synergy: compressor, be vented regenerator, condenser, air-breathing regenerator, the first capillary 105, second capillary 111, refrigerator evaporator, the first injector 107, second injector 108, freezer evaporator and gas-liquid separator 110;
The zone of heat liberation entrance of the outlet of compressor, the zone of heat liberation of exhaust regenerator, condenser, air-breathing regenerator is arranged in series successively; The zone of heat liberation outlet of air-breathing regenerator is divided into two-way;
One tunnel is connected with the entrance of refrigerator evaporator after the first capillary 105, and the outlet of institute's refrigerator evaporator is connected with the nozzle entrance of the first injector 107 after being vented the cold fluid pass of regenerator;
Another road is directly connected with the nozzle entrance of the second injector 108; The outlet of the second injector 108 and being connected by injection refrigerant inlet of the first injector 107;
The outlet of the first injector 107 is connected with the entrance of gas-liquid separator 110; The outlet of gas-liquid separator 110 is divided into saturated gaseous state refrigerant outlet and saturated liquid refrigerant outlet;
Saturated gaseous state refrigerant outlet is connected with the entrance of compressor after the cold fluid pass of air-breathing regenerator;
Saturated liquid refrigerant outlet is connected with the entrance of freezer evaporator after the second capillary 111, the outlet of freezer evaporator and being connected by injection refrigerant inlet of the second injector 108.
The saturated gaseous refrigerant of low-temp low-pressure of freezer evaporator outlet is carried out the high pressure sub-cooled liquid refrigerant injection of the zone of heat liberation outlet 117 of Self inhaling regenerator in the second injector 108, mixes after supercharging becomes gas-liquid two-phase cold-producing medium and draw in the second injector 108.The height carrying out the zone of heat liberation outlet 117 of Self inhaling regenerator in second injector 108 presses through cold gaseous refrigerant pressure and is greater than pressure from freezer evaporator saturated gaseous refrigerant out.
The gas-liquid two-phase cold-producing medium that second injector 108 exports by the overheated gaseous refrigerant injection of the cold fluid pass outlet 115 from exhaust regenerator, mixes after supercharging becomes gas-liquid two-phase cold-producing medium and enters gas-liquid separator 110 in the first injector 107 in the first injector 107.The pressure from the second injector 108 gas-liquid two-phase cold-producing medium is out greater than from the overheated gaseous refrigerant pressure of the cold fluid pass outlet 115 of exhaust regenerator in first injector 107.
As shown in Figure 2, it is double pipe heat exchanger that the present invention is vented regenerator, the overheated gaseous refrigerant of HTHP of compressor outlet enters exhaust regenerator by the zone of heat liberation entrance 112 being vented regenerator, exports 113 draw and enter condenser in exhaust regenerator after heat release cooling by the zone of heat liberation of exhaust regenerator;
The saturated gaseous refrigerant of refrigerator evaporator outlet enters exhaust regenerator by the cold fluid pass entrance 114 being vented regenerator, exports 115 draw and enter the nozzle entrance of the first injector 107 in exhaust regenerator after heat absorption intensification by the cold fluid pass of exhaust regenerator.
As shown in Figure 3, air-breathing regenerator of the present invention is double pipe heat exchanger, the saturated liquid refrigerant of high pressure of condensator outlet enters air-breathing regenerator by the zone of heat liberation entrance 116 of air-breathing regenerator, exports 117 draw in air-breathing regenerator after heat release cooling by the zone of heat liberation of air-breathing regenerator; The saturated gaseous refrigerant of the saturated gaseous state refrigerant outlet of gas-liquid separator 110 enters air-breathing regenerator by the cold fluid pass entrance 118 of air-breathing regenerator, and in air-breathing regenerator, heat absorption is drawn by the cold fluid pass outlet 119 of air-breathing regenerator and entered compressor after heating up.
As shown in Figure 4, cooling cycle system overall work process of the present invention is: in gas-liquid separator 110, isolated saturated gaseous refrigerant enters heat absorption intensification (in figure 11-1 process) in air-breathing regenerator by the cold fluid pass entrance 118 of air-breathing regenerator becomes overheated gaseous refrigerant, overheated gaseous refrigerant is become by compression boosting intensification after overheated gaseous refrigerant enters compressor, (in figure 1-2 process), the overheated gaseous refrigerant of HTHP of compressor outlet is entered in exhaust regenerator by the zone of heat liberation entrance 112 being vented regenerator and enters condenser after heat release cooling (in figure 2-3 process), release heat within the condenser further and become the saturated liquid refrigerant of high pressure (in figure 3-4 process), the saturated liquid refrigerant of high pressure is entered after heat release cooling becomes high pressure sub-cooled liquid refrigerant (in figure 4-5 process) in air-breathing regenerator by the zone of heat liberation entrance 116 of air-breathing regenerator and is divided into two-way, one road high pressure sub-cooled liquid refrigerant as the injection cold-producing medium of the second injector 108 directly enter in the nozzle of the second injector 108, the static energy of self is converted into kinetic energy while become high velocity, low pressure cold-producing medium (in figure 5-5 ' process), the saturated gaseous refrigerant of low-temp low-pressure of the second injector 108 jet expansion high velocity, low pressure cold-producing medium injection freezer evaporator outlet, and in the mixing chamber of the second injector 108 after mixing (in figure 5 ' (13)-14 ' process), diffuser supercharging (in figure 14 '-14 process) through the second injector 108 becomes gas-liquid two-phase cold-producing medium and exports extraction by the second injector 108, another road high pressure sub-cooled liquid refrigerant enters the first capillary 105 and carries out entering refrigerator evaporator after throttling realizes step-down cooling (in figure 5-6 process), in refrigerator evaporator, heat absorption evaporation realizes refrigeration object (in figure 6-7 process), the saturated gaseous refrigerant of refrigerator evaporator outlet enters heat absorption intensification (in figure 7-8 process) in exhaust regenerator by the cold fluid pass entrance 114 being vented regenerator becomes overheated gaseous refrigerant, this overheated gaseous refrigerant as the injection cold-producing medium of the first injector 107 enter in the nozzle of the first injector 107, the static energy of self is converted into kinetic energy while become high velocity, low pressure cold-producing medium (in figure 8-8 ' process), the gas-liquid two-phase cold-producing medium of high velocity, low pressure cold-producing medium injection second injector 108 outlet of the first injector 107 jet expansion, and mixing (in figure 8 ' (14)-9 ' process) becomes gas-liquid two-phase cold-producing medium by the diffuser supercharging (in figure 9 '-9 process) of the first injector 107 and exports extraction by the first injector 107 in the mixing chamber of the first injector 107, the gas-liquid two-phase cold-producing medium that first injector 107 exports enters gas-liquid separator 110 and carries out gas-liquid separation (in figure 9-10 (11) process), wherein the isolated saturated gaseous refrigerant of gas-liquid separator 110 enters air-breathing regenerator by the cold fluid pass entrance 118 of air-breathing regenerator, in air-breathing regenerator, heat absorption heats up after (in figure 11-1 process) becomes overheated gaseous refrigerant and is drawn by the cold fluid pass outlet 119 of air-breathing regenerator and entered compressor, the isolated saturated liquid refrigerant of gas-liquid separator 110 realizes refrigeration object (in figure 12-13 process) by entering freezer evaporator heat absorption evaporation after (in figure 10-12 process) after the second capillary 111 step-down cooling, the saturated gaseous refrigerant of low-temp low-pressure that freezer evaporator 109 exports enters the second injector 108 as by injection cold-producing medium, more than complete whole cyclic process.
Having five different operating pressures in whole system On The Cycle Working Process of the present invention, is the condensing pressure of condenser, the evaporating pressure of refrigerator evaporator, the pressure of inspiration(Pi) of compressor, the outlet pressure of the second injector 108 and the evaporating pressure of freezer evaporator successively.Wherein the evaporating pressure of the condensing pressure of condenser, the evaporating pressure of refrigerator evaporator and freezer evaporator determined by the work operating mode of the circulatory system, and this depends on again cryogenic temperature requirement and air ambient temperature; The pressure of inspiration(Pi) of compressor determined by the conservation of mass, the conservation of momentum and the energy conservation relation in the operating characteristic of the first injector 107, circulation; The outlet pressure of the second injector 108 determined by the conservation of mass, the conservation of momentum and the energy conservation relation in the operating characteristic of the second injector 108, circulation.
Claims (4)
1. one kind is sprayed the cooling cycle system with double back heat integration synergy for the two of two temperature refrigerator, it is characterized in that, its composition comprises: compressor, exhaust regenerator, condenser, air-breathing regenerator, the first capillary (105), the second capillary (111), refrigerator evaporator, the first injector (107), the second injector (108), freezer evaporator and gas-liquid separator (110);
The zone of heat liberation entrance of the outlet of described compressor, the zone of heat liberation of exhaust regenerator, condenser, air-breathing regenerator is arranged in series successively; The zone of heat liberation outlet of described air-breathing regenerator is divided into two-way;
One tunnel is connected with the entrance of described refrigerator evaporator after the first capillary (105), and the outlet of institute's refrigerator evaporator is connected with the nozzle entrance of the first injector (107) after the cold fluid pass of described exhaust regenerator;
Another road is directly connected with the nozzle entrance of described second injector (108); The outlet of described second injector (108) and being connected by injection refrigerant inlet of the first injector (107);
The outlet of described first injector (107) is connected with the entrance of gas-liquid separator (110); The outlet of described gas-liquid separator (110) is divided into saturated gaseous state refrigerant outlet and saturated liquid refrigerant outlet;
Described saturated gaseous state refrigerant outlet is connected with the entrance of compressor after the cold fluid pass of described air-breathing regenerator;
Described saturated liquid refrigerant outlet is connected with the entrance of freezer evaporator after the second capillary (111), the outlet of described freezer evaporator and being connected by injection refrigerant inlet of described second injector (108).
2. according to claim 1 for two injection of two temperature refrigerator and the cooling cycle system of double back heat integration synergy, it is characterized in that: the low-temp low-pressure gaseous refrigerant of described freezer evaporator outlet is carried out the high pressure sub-cooled liquid refrigerant injection of the zone of heat liberation outlet of Self inhaling regenerator in the second injector (108), draws after in the second injector (108), mixing supercharging becomes gas-liquid two-phase cold-producing medium;
The gas-liquid two-phase cold-producing medium that described second injector (108) exports by the overheated gaseous refrigerant injection of the cold fluid pass outlet from exhaust regenerator, enters gas-liquid separator (110) after mixing supercharging becomes gas-liquid two-phase cold-producing medium in the first injector (107) in the first injector (107).
3. according to claim 1 for two injection of two temperature refrigerator and the cooling cycle system of double back heat integration synergy, it is characterized in that: the overheated gaseous refrigerant of HTHP of described compressor outlet enters exhaust regenerator by the zone of heat liberation entrance being vented regenerator, exported by the zone of heat liberation of exhaust regenerator after heat release cooling in exhaust regenerator and draw and enter condenser;
The saturated gaseous refrigerant that refrigerator evaporator exports enters exhaust regenerator by the cold fluid pass entrance being vented regenerator, and in exhaust regenerator, heat absorption is drawn by the cold fluid pass outlet of exhaust regenerator and entered the nozzle entrance of the first injector (107) after heating up.
4. according to claim 1 for two injection of two temperature refrigerator and the cooling cycle system of double back heat integration synergy, it is characterized in that: the saturated liquid refrigerant of high pressure of condensator outlet enters air-breathing regenerator by the zone of heat liberation entrance of air-breathing regenerator, exported by the zone of heat liberation of air-breathing regenerator after heat release cooling in air-breathing regenerator and draw; The saturated gaseous refrigerant of the saturated gaseous state refrigerant outlet of gas-liquid separator (110) enters air-breathing regenerator by the cold fluid pass entrance of air-breathing regenerator, and in air-breathing regenerator, heat absorption is drawn by the cold fluid pass outlet of air-breathing regenerator and entered compressor after heating up.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410040517.3A CN103808101B (en) | 2014-01-27 | 2014-01-27 | A kind of two injection for two temperature refrigerator and the double back heat integration synergism refrigerating circulatory system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410040517.3A CN103808101B (en) | 2014-01-27 | 2014-01-27 | A kind of two injection for two temperature refrigerator and the double back heat integration synergism refrigerating circulatory system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103808101A CN103808101A (en) | 2014-05-21 |
| CN103808101B true CN103808101B (en) | 2015-12-02 |
Family
ID=50705231
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410040517.3A Active CN103808101B (en) | 2014-01-27 | 2014-01-27 | A kind of two injection for two temperature refrigerator and the double back heat integration synergism refrigerating circulatory system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103808101B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP4186725A1 (en) * | 2021-11-24 | 2023-05-31 | Volkswagen Ag | Air conditioning assembly with controlled ejector |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104676939B (en) * | 2015-02-25 | 2016-08-17 | 山东大学 | A kind of refrigerator car waste heat driven double evaporators ejector refrigeration system |
| CN108106047B (en) * | 2017-12-15 | 2019-12-17 | 山东大学 | CO with ejector2dual temperature refrigeration system, method and application thereof |
| CN108144818A (en) * | 2018-01-29 | 2018-06-12 | 同济大学 | A kind of lithium battery gravure coater drying system using multiple heat pump |
| CN108344195A (en) * | 2018-04-20 | 2018-07-31 | 天津商业大学 | Recycle the one machine dual temperature refrigeration system of two level injection of expansion work |
| CN108679878B (en) * | 2018-04-27 | 2020-04-10 | 西安交通大学 | Self-cascade refrigeration cycle system and refrigeration cycle method for increasing efficiency by adopting double ejectors |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2916521Y (en) * | 2006-06-23 | 2007-06-27 | 中南大学 | Ejector type refrigerating machine |
| CN102374694B (en) * | 2011-07-11 | 2013-06-19 | 中国科学院广州能源研究所 | CO2 multi-stage ejecting circulation heat pump/air conditioner system |
| JP5805567B2 (en) * | 2012-03-23 | 2015-11-04 | サンデンホールディングス株式会社 | Refrigeration cycle and refrigeration showcase |
| CN103148629B (en) * | 2013-02-28 | 2014-12-24 | 西安交通大学 | Gas-liquid phase ejector synergy refrigeration system for double temperature direct cooling-type refrigerator |
| CN203672022U (en) * | 2014-01-27 | 2014-06-25 | 合肥美菱股份有限公司 | Double-injection and double-heat-regeneration combined synergistic refrigerating cycle system for dual-temperature refrigerator |
-
2014
- 2014-01-27 CN CN201410040517.3A patent/CN103808101B/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP4186725A1 (en) * | 2021-11-24 | 2023-05-31 | Volkswagen Ag | Air conditioning assembly with controlled ejector |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103808101A (en) | 2014-05-21 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103148629B (en) | Gas-liquid phase ejector synergy refrigeration system for double temperature direct cooling-type refrigerator | |
| CN103808101B (en) | A kind of two injection for two temperature refrigerator and the double back heat integration synergism refrigerating circulatory system | |
| CN102563945B (en) | Refrigeration circulating system with double-stage-injection ejector | |
| CN101949611B (en) | Low-grade heat energy auxiliary-drive composite low-temperature refrigerating system | |
| CN110345690B (en) | Double-ejector synergistic refrigeration cycle system for double-temperature refrigerator and working method | |
| CN103954061B (en) | The one-stage steam compressed formula circulatory system of cold synergy crossed by a kind of injector | |
| CN105546863B (en) | A kind of Auto-cascade cycle list temperature or Duel-temperature refrigeration cycle system using injector synergy | |
| CN102778076B (en) | Novel compression/injection mixed refrigerating cyclic system used for double-temperature refrigerator | |
| CN103759449B (en) | The two-stage steam compression type circulatory system of dual jet synergy | |
| CN103776189B (en) | Tonifying Qi for the band injector of heat pump assembly increases enthalpy type heat pump circulating system | |
| CN103512257B (en) | For the non-azeotrope hydrocarbon mixture self-cascade refrigeration system system of two temperature refrigerator | |
| CN208920650U (en) | A kind of refrigeration system | |
| CN102042721A (en) | Synergy type steam compression heat pump circulating system of ejector | |
| CN109737639A (en) | The steam compressed mixed refrigeration systems of injection-and its course of work of solar energy auxiliary | |
| CN104949372B (en) | New type of compression secondary injection refrigeration system with gas-liquid separator | |
| CN102384604B (en) | Double-temperature-heat-source injection-type refrigeration system | |
| CN203672022U (en) | Double-injection and double-heat-regeneration combined synergistic refrigerating cycle system for dual-temperature refrigerator | |
| CN103615824B (en) | A kind of many warm areas cold acquisition methods and device reclaiming driving based on expansion work | |
| CN104792054A (en) | Ejector enhanced auto-cascade steam compressing type refrigeration cycle system | |
| CN101776347A (en) | Absorption type refrigerating unit with pressure recovery part | |
| CN201463399U (en) | Heat pump absorption type refrigeration system for refrigerator | |
| CN102679618A (en) | Solar energy driven jetting type refrigerating system | |
| CN103175333B (en) | Central air-conditioning combined solar injection refrigerating system | |
| CN106247657A (en) | A kind of carbon dioxide refrigerator refrigeration system | |
| CN201844611U (en) | Energy-saving deep 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 | ||
| CP03 | Change of name, title or address | ||
| CP03 | Change of name, title or address |
Address after: 230601 No. 2163 Lianhua Road, Hefei economic and Technological Development Zone, Anhui Patentee after: Changhong MeiLing Limited by Share Ltd Address before: 230061 No. 2163 Lianhua Road, Hefei economic and Technological Development Zone, Anhui Patentee before: Hefei Meiling Co., Ltd. |