CN107192153A - Twin-stage sweat cooling system with injector - Google Patents
Twin-stage sweat cooling system with injector Download PDFInfo
- Publication number
- CN107192153A CN107192153A CN201710612006.8A CN201710612006A CN107192153A CN 107192153 A CN107192153 A CN 107192153A CN 201710612006 A CN201710612006 A CN 201710612006A CN 107192153 A CN107192153 A CN 107192153A
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- Prior art keywords
- refrigeration
- gas
- liquid separator
- injector
- valve
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Classifications
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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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
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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
- F25B41/40—Fluid line 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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
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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
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
Abstract
This application discloses a kind of twin-stage sweat cooling system with injector, including：The one-level refrigeration pipe that two ends are connected with compressor and the first gas-liquid separator respectively, there is the first condenser thereon；The cold pipeline of two-stage system, including the first refrigeration branch pipeline and the second refrigeration branch pipeline being arranged in parallel, the two ends of first refrigeration branch pipeline are connected with the first gas-liquid separator and the second gas-liquid separator respectively, and the two ends of the second refrigeration branch pipeline are connected with the first gas-liquid separator and compressor respectively；Three-level refrigeration pipe, including the first refrigeration bye-pass and the second refrigeration bye-pass being arranged in parallel, the first refrigeration bye-pass connect the second gas-liquid separator and injector, and the second refrigeration bye-pass connects the second gas-liquid separator and compressor, and is provided with the second evaporator.In the present invention, realize the recovery of demi-inflation work(and improve efficiency, also reduce the thickness of liquid film and improve condensation efficiency, also improve the operation stability of the second evaporator, realize and each heat exchanger component is regulated and controled.
Description
Technical field
The present invention relates to refrigeration system technical field, more particularly to a kind of twin-stage sweat cooling system with injector.
Background technology
Vapor compression type refrigerating system is mainly made up of the big part of compressor, condenser, evaporator and expansion gear etc. four,
These parts connect into the refrigerating circuit of a closing by pipeline in certain sequence.Refrigerant circulation industrial between four big parts
Make, carry out energy exchange with the external world, reach the purpose of refrigeration.
Traditional sweat cooling system, in the course of the work throttling arrangement can produce expansion work, and these produce it is swollen
Swollen work(can not realize recovery, have impact on the efficiency of sweat cooling system.
In addition in condensation process, steam often condenses into condensate liquid on the wall of condenser and sprawls into liquid film,
And steam condensation releases heat and has to pass through liquid film, but the thermal conductivity of liquid film is poor, has had a strong impact on the transmission of heat, makes cold
The condensation efficiency of condenser is very low.
If at the import of evaporator being gas-liquid two-phase working medium, it will cause evaporator to shake in the course of the work,
Influence safe handling and the life-span of evaporator.
Therefore, the work efficiency of sweat cooling system how is improved, current those skilled in the art is had become and urgently solves
Certainly the problem of.
The content of the invention
In view of this, the invention provides a kind of twin-stage sweat cooling system with injector, by being carried out to its structure
Improve, realize the recovery to demi-inflation work(, so that the efficiency of the twin-stage sweat cooling system with injector is improved, and
Also the formation of condensation water can be reduced, condensation efficiency is improved, also so that whole by way of improving evaporator operation stability
The service behaviour of individual system gets a promotion.
In order to achieve the above object, the present invention provides following technical scheme：
A kind of twin-stage sweat cooling system with injector, including：
The first condenser is provided with one-level refrigeration pipe, the one-level refrigeration pipe and for water conservancy diversion non-azeotropic working medium,
The inlet communication of the outlet of its one end and compressor, the other end and the first gas-liquid separator；
The cold pipeline of two-stage system, the cold pipeline of two-stage system includes the first refrigeration branch pipeline being arranged in parallel and the second refrigeration point
Pipeline；The first refrigeration branch pipeline is rich in low boiling system for the gaseous state that water conservancy diversion is isolated from first gas-liquid separator
Cryogen, its one end is connected with the first outlet of first gas-liquid separator, and the import of the other end and the second gas-liquid separator connects
It is logical, and be provided with the first refrigeration branch pipeline and can adjust the first valve of the non-azeotropic working medium constituent；Institute
State and injector and the first evaporator are disposed with the second refrigeration branch pipeline, and be used for water conservancy diversion from first gas-liquid separator
In the liquid isolated be rich in higher boiling refrigerant, one end of the second refrigeration branch pipeline and first gas-liquid separator
Second outlet is connected, the first inlet communication of the other end and the compressor, and is provided with the second refrigeration branch pipeline
The second valve of the non-azeotropic working medium constituent can be adjusted；
Three-level refrigeration pipe, the three-level refrigeration pipe includes the first refrigeration bye-pass being arranged in parallel and the second refrigeration branch
Pipeline；The first refrigeration bye-pass connects the driving fluid of the first outlet and the injector of second gas-liquid separator
The 3rd valve of the non-azeotropic working medium constituent can be adjusted by being provided with entrance, and the first refrigeration bye-pass；
The second refrigeration bye-pass connects the second import of the second outlet and the compressor of second gas-liquid separator, and
Be provided with the second evaporator and the 4th valve on the second refrigeration bye-pass, the evaporating temperature of second evaporator with it is described
The evaporating temperature of first evaporator is different, and the 4th valve can adjust the constituent of the non-azeotropic working medium.
It is preferred that, in the above-mentioned twin-stage sweat cooling system with injector, the is provided with the first refrigeration branch pipeline
Two condensers and expansion gear, second condenser are set close to first gas-liquid separator, and the expansion gear is close
Second gas-liquid separator is set.
It is preferred that, in the above-mentioned twin-stage sweat cooling system with injector, the expansion gear and the second expansion dress
It is set to choke valve, electric expansion valve or capillary.
It is preferred that, in the above-mentioned twin-stage sweat cooling system with injector, in addition to：
Be arranged in the first refrigeration branch pipeline, and positioned at first gas-liquid separator and second condenser it
Between the first valve, first valve be used for adjust enter described first freeze branch pipeline in it is described rich in low boiling refrigeration
The flow of agent；
It is arranged in the second refrigeration branch pipeline, and positioned between first gas-liquid separator and the injector
Second valve, second valve, which is used to adjusting, to be entered described second and freezes described in branch pipeline rich in higher boiling refrigerant
Flow.
It is preferred that, in the above-mentioned twin-stage sweat cooling system with injector, in addition to：
Be arranged on it is described first refrigeration bye-pass on, for adjust enter described first freeze bye-pass in described in be rich in
3rd valve of low boiling point refrigerant flow；
Be arranged on it is described second refrigeration bye-pass on, for adjust enter described second freeze bye-pass in described in be rich in
4th valve of low boiling point refrigerant flow.
The twin-stage sweat cooling system with injector that the present invention is provided, its refrigerating circuit includes multi-stage refrigerating pipeline, i.e.,
The cold pipeline of one-level refrigeration pipe, two-stage system and three-level refrigeration pipe.Specifically, being provided with the first cooling on one-level refrigeration pipe
Device, and two ends respectively with compressor outlet and the first gas-liquid separator inlet communication, be mainly used in and compressor cooperation
Non-azeotropic working medium is compressed, water conservancy diversion and condensation, condensed non-azeotropic working medium is guided in the first gas-liquid separator；And
The cold pipeline of two-stage system then includes two branch pipelines being arranged in parallel, i.e., the first refrigeration branch pipeline and the second refrigeration branch pipeline, first
Refrigeration branch pipeline one end is connected with the first outlet of the first gas-liquid separator, and the import of the other end and the second gas-liquid separator connects
It is logical, it is mainly used in the gaseous state that water conservancy diversion separates from the first gas-liquid separator and is rich in low boiling point refrigerant, due to enters the
It is gaseous state to be rich in low boiling point refrigerant in one refrigeration branch pipeline, so enabling to the steam quality in the first refrigeration branch pipeline to obtain
Raising has been arrived, (gaseous to be condensed rich in higher boiling refrigerant in the first refrigeration branch pipeline) liquid film is reduced in condensation
Thickness so that the effect and condensation efficiency of condensing heat-exchange are improved；One end of second refrigeration branch pipeline and gas-liquid point
Second outlet from device is connected, the first inlet communication of the other end and compressor, is divided for water conservancy diversion from the first gas-liquid separator
Separate out being rich on higher boiling refrigerant, and the second refrigeration branch pipeline for liquid come and be disposed with injector and the first evaporation
Device so that can enter injector from the working fluid import of injector rich in higher boiling refrigerant, is entered back into the first evaporation
In device, enter finally into compressor；Three-level refrigeration pipe equally includes the first refrigeration bye-pass being arranged in parallel and the second system
Cold bye-pass, the first refrigeration bye-pass connects the first outlet of the second gas-liquid separator and the driving fluid entrance of injector, the
Two refrigeration bye-passes then connect the second outlet of the second gas-liquid separator and the second import of compressor, and in the second refrigeration branch
The second evaporator is additionally provided with pipeline, flow through the first refrigeration branch pipeline enters the second gas-liquid point rich in low boiling point refrigerant
From gas-liquid separation in device, is realized, wherein gas part is entered in the first refrigeration bye-pass, and is finally entered from driving fluid entrance
Enter into injector, so that in injector confluxing for non-azeotrope rich in low boiling point refrigerant and rich in higher boiling refrigerant
Working medium, after being mixed rich in low boiling point refrigerant and rich in higher boiling refrigerant in the presence of injector with boosting, Neng Gouti
The pressure of inspiration(Pi) of high compressor, so as to realize the recovery of part expansion work, makes the efficiency of sweat cooling system be improved, and
Set the second refrigeration branch then to improve the heat transfer effect of whole system, and by setting the second gas-liquid separator, also cause
Second evaporator inlet is pure liquid rich in low boiling point refrigerant, is conducive to the stable operation of the second evaporator, improves steaming
Send out the service behaviour of refrigeration system.In addition, freezing branch pipeline, the second refrigeration branch pipeline, the first refrigeration bye-pass and the first
On two refrigeration bye-passes, the first valve, the second valve, the 3rd valve and the 4th valve are also respectively provided with, and pass through regulation
Each valve can realize the regulation into the non-azeotropic working medium constituent in each pipeline.The band injector that the present invention is provided
Twin-stage sweat cooling system, by the cooperation of multi-stage refrigerating pipeline, injector and non-azeotropic working medium, realize demi-inflation work(
Recovery, improve the efficiency of the twin-stage sweat cooling system with injector, while can also reduce the thickness of liquid film, improve
Condensation efficiency, also so that the service behaviour of whole system is significantly improved, be by improving the operation stability of evaporator
System can adjust the non-azeotropic working medium constituent of each heat exchanger, the Effec-tive Function under various actual conditions.
Brief description of the drawings
In order to illustrate more clearly about the embodiment of the present invention or technical scheme of the prior art, below will be to embodiment or existing
There is the accompanying drawing used required in technology description to be briefly described, it should be apparent that, drawings in the following description are only this
The embodiment of invention, for those of ordinary skill in the art, on the premise of not paying creative work, can also basis
The accompanying drawing of offer obtains other accompanying drawings.
Fig. 1 is the structural representation of the twin-stage sweat cooling system provided in an embodiment of the present invention with injector.
In Fig. 1：
The condensers of 101- first, 102- compressors, the gas-liquid separators of 103- first, the gas-liquid separators of 104- second, 105-
Injector, the evaporators of 106- first, the evaporators of 107- second, the condensers of 108- second, 109- expansion gears, the valves of 110- first
Door, the valves of 111- second, the valves of 112- the 3rd, the valves of 113- the 4th, 114- one-level refrigeration pipes, the cold pipeline of 115- two-stage systems,
The refrigeration branch pipelines of 116- first, the refrigeration branch pipelines of 117- second, 118- three-level refrigeration pipes, the refrigeration bye-passes of 119- first,
The refrigeration bye-passes of 120- second.
Embodiment
The invention provides a kind of twin-stage sweat cooling system with injector, by being improved to its structure, realize
Recovery to demi-inflation work(, so as to improve the efficiency of the twin-stage sweat cooling system with injector, and can also subtract
The wall thickness of liquid film of few condenser, improves condensation efficiency, also so that whole by way of improving evaporator operation stability
The service behaviour of individual system gets a promotion.
Below in conjunction with the accompanying drawing in the embodiment of the present invention, the technical scheme in the embodiment of the present invention is carried out clear, complete
Site preparation is described, it is clear that described embodiment is only a part of embodiment of the invention, rather than whole embodiments.It is based on
Embodiment in the present invention, it is every other that those of ordinary skill in the art are obtained under the premise of creative work is not made
Embodiment, belongs to the scope of protection of the invention.
As shown in figure 1, the twin-stage sweat cooling system provided in an embodiment of the present invention with injector, including：It is provided with
One condenser 101 and two ends respectively with the outlet of compressor 102 and the one-level system of the inlet communication of the first gas-liquid separator 103
Cold pipeline 114, the one-level refrigeration pipe 114 is mainly used in water conservancy diversion non-azeotropic working medium, and (non-azeotropic working medium in the present embodiment is by one
Plant higher boiling refrigerant and a kind of low boiling point refrigerant is mixed)；The cold pipeline 115 of two-stage system, the cold pipeline 115 of the two-stage system is wrapped
The first refrigeration refrigeration branch pipeline 117 of branch pipeline 116 and second being arranged in parallel is included, the first refrigeration branch pipeline 116 therein is used for
Water conservancy diversion separated from the first gas-liquid separator it is gaseous be rich in low boiling point refrigerant, and first refrigeration branch pipeline 116
One end connected with the first outlet of the first gas-liquid separator 103, the inlet communication of the other end and the second gas-liquid separator 104,
It is condensed into when flowing through the second condenser 108 rich in low boiling point refrigerant from gaseous state in liquid, the second refrigeration branch pipeline 117 then successively
The evaporator 106 of injector 105 and first is provided with, the second refrigeration branch pipeline 117 is mainly used in water conservancy diversion from the first gas-liquid separator
In the liquid separated be rich in higher boiling refrigerant, and one end and the first gas-liquid separation of the second refrigeration branch pipeline 117
The second outlet connection of device 103, the first inlet communication of the other end and compressor 102；Three-level refrigeration pipe 118, the three tier structure
Cold pipeline 118 includes the first refrigeration refrigeration bye-pass 120 of bye-pass 119 and second being arranged in parallel, the first refrigeration bye-pass 119
Connect the first outlet of the second gas-liquid separator 104 and the driving fluid entrance of the injector 105, the second refrigeration bye-pass
The second outlet of 120 the second gas-liquid separators 104 of connection and the second import of compressor 102, and the second refrigeration bye-pass 120
On be additionally provided with the second evaporator 107, the evaporating temperature of the second evaporator 107 is different from the evaporating temperature of the first evaporator 106.
The twin-stage sweat cooling system with injector of said structure, non-azeotropic working medium is condensed in the first condenser 101,
Liquid is first condensed into rich in higher boiling refrigerant, rich in low boiling point refrigerant or gaseous state.By the first gas-liquid separator 103
Afterwards, condensed rich in low boiling point refrigerant into the second condenser 108 so that the steam quality for entering the second condenser 108 is obtained
Improve, so as to reduce the thickness that liquid film is produced in condensation process, the effect of condensing heat-exchange is improved.Also, due to spray
The movement-less part of emitter 105, and mixed when rich in low boiling point refrigerant and rich in higher boiling refrigerant in the presence of injector 105
Close with after boosting, the recovery of part expansion work can be realized, improve the pressure of inspiration(Pi) of compressor 102, make sweat cooling system
Efficiency is improved, and by setting the second gas-liquid separator 104, also cause the entrance of the second evaporator 107 is rich in low boiling
Point refrigerant is pure liquid, is conducive to the stable operation of the second evaporator 107, improves the twin-stage sweat cooling system with injector
The service behaviour of system.
For the twin-stage sweat cooling system with injector that further optimisation technique scheme, the present embodiment are provided, first
The second condenser 108 and expansion gear 109 are provided with refrigeration branch pipeline 116, and the second condenser 108 is close to the first gas-liquid
Separator 103 is set, and expansion gear 109 is set close to the second gas-liquid separator 104, and the first evaporator 106 and second steams
The evaporating temperature for sending out device 107 is different, as shown in Figure 1.In the application, the outlet of compressor 102 passes through one-level refrigeration pipe 114 processed
It is connected with the entrance of the first condenser 101, the outlet of the first condenser 101 and the import phase of the side of the first gas-liquid separator 103
Even, the top export (i.e. first outlet) of gas-liquid separator is connected with the import of the second condenser 108, the second condenser 108
Outlet is connected with the import of expansion gear 109, and the import exported then with the second gas-liquid separator 104 of expansion gear 109 is connected,
First refrigeration bye-pass 119 is connected with the driving fluid import of injector 105 so that isolated through the second gas-liquid separator 104
Gaseous state can enter in injector 105 rich in low boiling point refrigerant.From the outlet at bottom of the first gas-liquid separator 103 (i.e.
Second outlet) come out liquid rich in higher boiling refrigerant as working fluid enter injector 105 Working-fluid intaking,
Be rich in low boiling point refrigerant for injection to be gaseous, two kinds of fluids in the presence of the injector 105 mixing with entering the after boosting
One evaporator 106, after being evaporated in the first evaporator 106 so that whole non-azeotropic working mediums is entered with gaseous state presses
First import of contracting machine 102.And the liquid isolated by the second gas-liquid separator 104 is then entered rich in low boiling point refrigerant
Evaporation is realized in second evaporator 107, the second import of compressor 102 is entered by the second refrigeration bye-pass 120 again afterwards
In.This structure forms a kind of circulatory system of the complete synergy of use injector 105 for being applied to two kinds of evaporating temperatures.
The specific work process of the twin-stage sweat cooling system with injector of said structure is：From compressor 102
High pressure superheater non-azeotropic working medium is condensed into the first condenser 101, wherein liquid is condensed into rich in higher boiling refrigerant, rich in low
Boiling point refrigerant or gas, subsequently enter the first gas-liquid separator 103 and carry out gas-liquid separation.Rich in low boiling point refrigerant from
The first outlet of one gas-liquid separator 103 is left, and liquid is condensed into the second condenser 108, is passing through expansion gear 109
After enter in the second gas-liquid separator 104, the gas isolated by the second gas-liquid separator 104 by second refrigeration bye-pass
Enter injector 105 as driving fluid after 120, and the liquid isolated then enters the by first bye-pass 119 that freezes
Heat absorption flashes to steam in two evaporators 107, and final the second import through compressor 102 is returned in compressor 102.Rich in height
Boiling point refrigerant flows out from the second outlet of the first gas-liquid separator 103, under the water conservancy diversion of the second refrigeration branch pipeline 117, as
Working fluid enters injector 105, is rich in low boiling point refrigerant to injection, both discharge injector after mixing and boosting
105, the non-azeotropic working medium being mixed to get enters heat absorption in the first evaporator 106 and flashes to steam, afterwards from compressor 102
First import completes whole circulation into compressor 102.
Specifically, expansion gear 109 is preferably choke valve, electric expansion valve or capillary etc..
The present embodiment positioned at the first gas-liquid separator 103 and second it is also preferred that in the first refrigeration branch pipeline 116, condense
Position between device 108 is provided with the first valve 110, and the gas of the first gas-liquid separator 103 can be adjusted by the first valve 110
The aperture of body outlet (i.e. the first outlet of the first gas-liquid separator 103), so as to realize to entering in the first refrigeration branch pipeline 116
The flow rich in low boiling point refrigerant regulation；In the second refrigeration branch pipeline 117, positioned at the He of the first gas-liquid separator 103
Position between injector 105 is provided with the second valve 111, and second valve 111 can adjust the first gas-liquid separator 103
The aperture of liquid outlet (i.e. the second outlet of the first gas-liquid separator 103), to realize that regulation enters the second refrigeration branch pipeline 117
The flow rich in higher boiling refrigerant.The 3rd valve 112 is provided with the first refrigeration bye-pass 119, passes through the 3rd valve
112 can adjust the aperture of the gas vent (i.e. the first outlet of the second gas-liquid separator 104) of the second gas-liquid separator 104,
Low boiling point refrigerant flow is rich in so as to adjust into the gaseous state in the first refrigeration bye-pass 119；In the second refrigeration bye-pass 120
On, it is provided with the 4th valve 113, the 4th valve on the position between the second gas-liquid separator 104 and the second evaporator 107
Door 113 can adjust opening for liquid outlet (i.e. the second outlet of the second gas-liquid separator 104) of the second gas-liquid separator 104
Degree, so as to adjust flow of the liquid rich in low boiling point refrigerant into the second refrigeration bye-pass 120.Pass through each above-mentioned valve
Setting and cooperation, the constituent for the non-azeotropic mixed working medium for flowing through each heat exchanger can be adjusted so that system is various
Can Effec-tive Function in actual operating mode.
Each part is described by the way of progressive in this specification, what the structure of each part was stressed is
With the difference of existing structure, the entirety and part-structure of the twin-stage sweat cooling system with injector can be above-mentioned by combining
The structure of some and obtain.
The foregoing description of the disclosed embodiments, enables professional and technical personnel in the field to realize or using the present invention.
A variety of modifications to these embodiments will be apparent for those skilled in the art, as defined herein
General Principle can be realized in other embodiments without departing from the spirit or scope of the present invention.Therefore, it is of the invention
The embodiments shown herein is not intended to be limited to, and is to fit to and principles disclosed herein and features of novelty phase one
The most wide scope caused.
Claims (5)
1. a kind of twin-stage sweat cooling system with injector, it is characterised in that including：
The first condenser is provided with one-level refrigeration pipe, the one-level refrigeration pipe and for water conservancy diversion non-azeotropic working medium, one
The inlet communication of end and the outlet of compressor, the other end and the first gas-liquid separator；
The cold pipeline of two-stage system, the cold pipeline of two-stage system includes the first refrigeration branch pipeline being arranged in parallel and the second refrigeration is in charge of
Road；The first refrigeration branch pipeline is freezed for the gaseous state that water conservancy diversion is isolated from first gas-liquid separator rich in low boiling
Agent, its one end is connected with the first outlet of first gas-liquid separator, the inlet communication of the other end and the second gas-liquid separator,
And the first valve of the non-azeotropic working medium constituent can be adjusted by being provided with the first refrigeration branch pipeline；Described
Injector and the first evaporator are disposed with two refrigeration branch pipelines, and is divided for water conservancy diversion from first gas-liquid separator
The liquid separated out is rich in higher boiling refrigerant, one end and the second of first gas-liquid separator of the second refrigeration branch pipeline
Being provided with outlet, the first inlet communication of the other end and the compressor, and the second refrigeration branch pipeline can
Adjust the second valve of the non-azeotropic working medium constituent；
Three-level refrigeration pipe, the three-level refrigeration pipe includes the first refrigeration bye-pass being arranged in parallel and the second refrigeration branch pipe
Road；The first refrigeration bye-pass connects the first outlet of second gas-liquid separator and the driving fluid of the injector enters
The 3rd valve of the non-azeotropic working medium constituent can be adjusted by being provided with mouth, and the first refrigeration bye-pass；Institute
State the second refrigeration bye-pass and connect the second outlet of second gas-liquid separator and the second import of the compressor, and institute
State and the second evaporator and the 4th valve are provided with the second refrigeration bye-pass, the evaporating temperature of second evaporator and described the
The evaporating temperature of one evaporator is different, and the 4th valve can adjust the constituent of the non-azeotropic working medium.
2. the twin-stage sweat cooling system according to claim 1 with injector, it is characterised in that first refrigeration point
The second condenser and expansion gear are provided with pipeline, second condenser is set close to first gas-liquid separator, institute
Expansion gear is stated to set close to second gas-liquid separator.
3. the twin-stage sweat cooling system according to claim 2 with injector, it is characterised in that the expansion gear is
Choke valve, electric expansion valve or capillary.
4. the twin-stage sweat cooling system according to claim 2 with injector, it is characterised in that also include：
It is arranged in the first refrigeration branch pipeline, and positioned between first gas-liquid separator and second condenser
First valve, first valve, which is used to adjusting, to be entered described first and freezes described in branch pipeline rich in low boiling point refrigerant
Flow；
It is arranged in the second refrigeration branch pipeline, and positioned at second between first gas-liquid separator and the injector
Valve, second valve is used to adjust the stream rich in higher boiling refrigerant entered in the described second refrigeration branch pipeline
Amount.
5. the twin-stage sweat cooling system with injector according to any one in claim 1-4, it is characterised in that also
Including：
Be arranged on it is described first refrigeration bye-pass on, for adjust enter described first freeze bye-pass in described in be rich in low boiling
3rd valve of point refrigerant flow；
Be arranged on the second refrigeration bye-pass, for adjust enter described second freeze in bye-pass described in rich in low
4th valve of boiling point refrigerant flow.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710612006.8A CN107192153B (en) | 2017-07-25 | 2017-07-25 | Double-stage evaporation refrigeration system with ejector |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710612006.8A CN107192153B (en) | 2017-07-25 | 2017-07-25 | Double-stage evaporation refrigeration system with ejector |
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| Publication Number | Publication Date |
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| CN107192153A true CN107192153A (en) | 2017-09-22 |
| CN107192153B CN107192153B (en) | 2023-07-28 |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109341124A (en) * | 2018-11-14 | 2019-02-15 | 珠海格力电器股份有限公司 | A kind of mixed working fluid dual temperature circulatory system |
| CN109900004A (en) * | 2019-02-20 | 2019-06-18 | 仲恺农业工程学院 | A kind of adjustable mass dryness fraction refrigeration system of the Two-stage Compression with injector |
| CN110986414A (en) * | 2019-11-25 | 2020-04-10 | 西安交通大学 | Multi-temperature-zone and large-temperature-span heat pump circulating system adopting ejector for increasing efficiency |
| CN111023363A (en) * | 2019-12-17 | 2020-04-17 | 海信（山东）空调有限公司 | Air conditioner and control method |
| CN112815561A (en) * | 2019-10-31 | 2021-05-18 | 广东美的白色家电技术创新中心有限公司 | Refrigeration device |
| WO2021213548A1 (en) * | 2020-06-01 | 2021-10-28 | 青岛经济技术开发区海尔热水器有限公司 | Heat exchange device, water heater, and air conditioner |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01155149A (en) * | 1987-12-10 | 1989-06-19 | Matsushita Electric Ind Co Ltd | Refrigeration cycle device |
| CN102620461A (en) * | 2012-04-19 | 2012-08-01 | 浙江大学宁波理工学院 | Auto-cascade jet type refrigerator |
| CN105546863A (en) * | 2015-12-12 | 2016-05-04 | 西安交通大学 | Auto-cascade single-temperature or double-temperature refrigeration cycle system adopting ejector for synergism |
| CN106546026A (en) * | 2016-10-25 | 2017-03-29 | 西安交通大学 | Using the non-azeotropic mixed working medium fractional condensation Duel-temperature refrigeration cycle system of ejector potentiation |
| CN207230989U (en) * | 2017-07-25 | 2018-04-13 | 广东工业大学 | Spray the dual temperature sweat cooling system of synergy |
-
2017
- 2017-07-25 CN CN201710612006.8A patent/CN107192153B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01155149A (en) * | 1987-12-10 | 1989-06-19 | Matsushita Electric Ind Co Ltd | Refrigeration cycle device |
| CN102620461A (en) * | 2012-04-19 | 2012-08-01 | 浙江大学宁波理工学院 | Auto-cascade jet type refrigerator |
| CN105546863A (en) * | 2015-12-12 | 2016-05-04 | 西安交通大学 | Auto-cascade single-temperature or double-temperature refrigeration cycle system adopting ejector for synergism |
| CN106546026A (en) * | 2016-10-25 | 2017-03-29 | 西安交通大学 | Using the non-azeotropic mixed working medium fractional condensation Duel-temperature refrigeration cycle system of ejector potentiation |
| CN207230989U (en) * | 2017-07-25 | 2018-04-13 | 广东工业大学 | Spray the dual temperature sweat cooling system of synergy |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109341124A (en) * | 2018-11-14 | 2019-02-15 | 珠海格力电器股份有限公司 | A kind of mixed working fluid dual temperature circulatory system |
| CN109900004A (en) * | 2019-02-20 | 2019-06-18 | 仲恺农业工程学院 | A kind of adjustable mass dryness fraction refrigeration system of the Two-stage Compression with injector |
| CN109900004B (en) * | 2019-02-20 | 2024-03-26 | 仲恺农业工程学院 | Two-stage compression adjustable dryness refrigerating system with ejector |
| CN112815561A (en) * | 2019-10-31 | 2021-05-18 | 广东美的白色家电技术创新中心有限公司 | Refrigeration device |
| CN112815561B (en) * | 2019-10-31 | 2022-03-25 | 广东美的白色家电技术创新中心有限公司 | Refrigeration device |
| CN110986414A (en) * | 2019-11-25 | 2020-04-10 | 西安交通大学 | Multi-temperature-zone and large-temperature-span heat pump circulating system adopting ejector for increasing efficiency |
| CN111023363A (en) * | 2019-12-17 | 2020-04-17 | 海信（山东）空调有限公司 | Air conditioner and control method |
| CN111023363B (en) * | 2019-12-17 | 2021-10-29 | 海信（山东）空调有限公司 | Air conditioner and control method |
| WO2021213548A1 (en) * | 2020-06-01 | 2021-10-28 | 青岛经济技术开发区海尔热水器有限公司 | Heat exchange device, water heater, and air conditioner |
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