CN102384604A - Double-temperature-heat-source injection-type refrigeration system - Google Patents

Double-temperature-heat-source injection-type refrigeration system Download PDF

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Publication number
CN102384604A
CN102384604A CN2011103296812A CN201110329681A CN102384604A CN 102384604 A CN102384604 A CN 102384604A CN 2011103296812 A CN2011103296812 A CN 2011103296812A CN 201110329681 A CN201110329681 A CN 201110329681A CN 102384604 A CN102384604 A CN 102384604A
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China
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outlet
injector
links
generator
condenser
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CN2011103296812A
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CN102384604B (en
Inventor
王林
谈莹莹
崔晓龙
王江丽
梁坤峰
段丽平
张敏慧
马爱华
王雨
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Henan University of Science and Technology
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Henan University of Science and Technology
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Priority to CN 201110329681 priority Critical patent/CN102384604B/en
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Abstract

The invention relates to a double-temperature-heat-source injection-type refrigeration system. The working temperature of a first generator is higher than that of a second generator; the steam outlet of the first generator is connected with the working fluid inlet of a first injector; the outlet of the first injector is connected with the refrigerant inlet of a condenser; the refrigerant outlet of the condenser is divided into three ways, one way is connected with the inlet of the first generator through a first working medium pump, another way is connected with the refrigerant inlet of an evaporator through a first throttling valve, and the third way is connected with the low-pressure inlet of a condensation evaporator through a second throttling valve; the low-pressure outlet of the condensation evaporator is connected with the driving fluid inlet of the first injector; the steam outlet of a second generator is connected with the working fluid inlet of a second injector; the outlet of the second injector is divided into two ways, one way is connected with the driving fluid inlet of the first injector, and another way is connected with the high-pressure inlet of the condensation evaporator; and the high-pressure outlet of the condensation evaporator is connected with the inlet of the second generator through a second working medium pump.

Description

Two warm source spray type refrigerating system
Technical field
The present invention relates to a kind of cooling cycle system, relate in particular to a kind of two warm source spray type refrigerating system that utilizes low-grade energies such as solar energy or waste heat.
Background technology
The jet refrigeration circulation system adopts water, ammonia, HF class, HFC class or HCFC class etc. as refrigeration working medium, and jet refrigeration circulation and the maximum difference of mechanical compression refrigeration circulation are to replace compressor with injector, produce high steam through the low-temperature heat source heating from the condenser liquid working substance; Utilize the injector injection to come the low-pressure steam of flash-pot and be compressed into elevated pressures steam,, except that working medium circulating pump, do not have other moving component for gaseous working medium condensation under higher temperature creates conditions; Circular flow is safeguarded few; The high-grade mechanical energy consumption is few, especially with regard to freon class working medium, only needs 60 ℃ low-temperature heat source just can drive periodic duty; Unique advantage with low-grade low-temperature energy sources such as utilizing solar energy, underground heat, waste heat of plant, used heat; Be that a kind of the utilization hanged down the comparatively desirable refrigeration modes that enthalpy energy obtains refrigeration, yet the cryogenic temperature that the conventional spray kind of refrigeration cycle can be obtained is higher; Common more than 0 ℃; Limited by the injector compression ratio, condenser can not obtain the too big condensing agent of pressure, causes through the temperature of the cold-producing medium behind the condenser higher relatively; The cryogenic temperature that will obtain-10 ℃ through evaporimeter almost is impossible, receives than limitations thereby make the conventional spray refrigeration machine use.
Summary of the invention
The two warm source spray type refrigerating system that the object of the present invention is to provide that a kind of system pressure ratio is big, cryogenic temperature is low.
For realizing above-mentioned purpose; The present invention adopts following technical scheme: a kind of two warm source spray type refrigerating system, comprise first generator and second generator, and the operating temperature of first generator is higher than the operating temperature of second generator; The steam (vapor) outlet of first generator links to each other with the working fluid import of first injector; The outlet of first injector links to each other with the refrigerant inlet of condenser, and the refrigerant outlet of condenser is divided into three the tunnel, and first working medium pump of wherein leading up to links to each other with the import of first generator; Another road links to each other with the refrigerant inlet of evaporimeter through the first throttle valve; Third Road links to each other with the low pressure inlet of condenser/evaporator through second choke valve, and the low tension outlet of condenser/evaporator links to each other with the driving fluid import of first injector, and the steam (vapor) outlet of second generator links to each other with the working fluid import of second injector; The outlet of second injector is divided into two-way; Wherein one the tunnel links to each other with the driving fluid import of first injector, and another road links to each other with the high-pressure inlet of condenser/evaporator, and the high-pressure outlet of condenser/evaporator links to each other with the import of second generator through second working medium pump.
The outlet of described second injector links to each other with the driving fluid import of first injector through control valve.
Be provided with first regenerator between the outlet of described first injector and the refrigerant inlet of condenser and between the import of the first working medium delivery side of pump and first generator; The outlet of first injector links to each other with first medium channel of the refrigerant inlet of condenser through first regenerator, and the import of the first working medium delivery side of pump and first generator links to each other through second medium channel of first regenerator.
Be provided with second regenerator between the refrigerant outlet of described condenser and the first throttle valve and between the import of the high-pressure outlet of condenser/evaporator and second working medium pump; The refrigerant outlet of condenser links to each other with first medium channel of first throttle valve through second regenerator, and the import of the high-pressure outlet of condenser/evaporator and second working medium pump links to each other through second medium channel of second regenerator.
Be provided with the 3rd regenerator between the outlet of first medium channel of described second regenerator and the first throttle valve and between the driving fluid import of the refrigerant outlet of evaporimeter and second injector; The outlet of first medium channel of second regenerator links to each other with first medium channel of first throttle valve through the 3rd regenerator, and the driving fluid import of the refrigerant outlet of evaporimeter and second injector links to each other through second medium channel of the 3rd regenerator.
The working medium of described two warm source spray type refrigerating system is a kind of or three's among R600a, R600, the R134a combination.
The steam that second generator of the present invention produces comes the steam of flash-pot as the working fluid injection of second injector; The driving fluid import that gets into first injector through the part in the fluid of second injector increase is gone into first generator from the steam ejection of first generator; Steam from second generator passes through the pressure of second injector for the steam of the driving fluid import of entering first injector; The steam pressure at the jet exit place that wins is increased; Improved the pressure ratio of whole system, thereby can reduce the cryogenic temperature of evaporimeter, so that obtain being lower than the getable cryogenic temperature of jet refrigeration circulation system of the prior art.
The outlet of second injector of the present invention links to each other with the driving fluid import of first injector through control valve; Control valve can be adjusted the Fluid Volume of the driving fluid import that flows into first injector; Make the working medium balance of the circulatory system of the circulatory system and second generator of the generator of winning, make system works under optimum state.
Description of drawings
Fig. 1 is the structural representation of the embodiment of the invention 1;
Fig. 2 is the structural representation of the embodiment of the invention 2.
The specific embodiment
A kind of two warm sources spray type refrigerating system implementation example 1; In Fig. 1; The steam (vapor) outlet of its first generator 1 links to each other with the working fluid import of first injector 2, and the outlet of first injector 2 links to each other with the refrigerant inlet of condenser 3, and the refrigerant outlet of condenser 3 is divided into three the tunnel; Wherein one the tunnel links to each other with the import of first working medium pump 4; The outlet of first working medium pump 4 links to each other with the import of first generator 1, and another road links to each other with the refrigerant inlet of evaporimeter 6 through first throttle valve 5, and Third Road links to each other with the low pressure inlet of condenser/evaporator 8 through second choke valve 7; The low tension outlet of condenser/evaporator 8 links to each other with the driving fluid import of first injector 2; The steam (vapor) outlet of second generator 10 links to each other with the working fluid import of second injector 9, and the outlet of second injector 9 is divided into two-way, links to each other with the driving fluid import of first injector 2 after wherein one tunnel process control valve 14 and the low tension outlet of condenser/evaporator 8 converge; Another road links to each other with the high-pressure inlet of condenser/evaporator 8, and the high-pressure outlet of condenser/evaporator 8 links to each other with the import of second generator 10 through second working medium pump 11.
First generator is stretched out at the two ends that are provided with first heating tube, 12, the first heating tubes 12 in first generator 1, and in use, the two ends of first heating tube 12 import and export of thermal source respectively link to each other, and is the cold-producing medium heating of first generator 1.
First generator is stretched out at the two ends that are provided with second heating tube, 13, the second heating tubes 13 in second generator 10, and in use, the two ends of second heating tube 13 import and export of thermal source respectively link to each other, and is the cold-producing medium heating of second generator 10.
The operating temperature of first generator 1 is higher than the operating temperature of second generator; First generator, 1 required occurrence temperature is 80 ℃~100 ℃; The required occurrence temperature of second generator is 60 ℃~80 ℃; The refrigeration system of present embodiment has the potentiality of effectively utilizing solar energy or low grade residual heat, and application prospect is good.First generator and second generator add heat can be provided by low-grade heat sources such as solar energy, geothermal energy, industrial exhaust heat or used heat.
The outlet elder generation of second injector 9 in the present embodiment together links to each other with the driving fluid import of first injector 2 after converging with the low tension outlet of condenser/evaporator 8 again, and the outlet of second injector 9 also can directly link to each other with the driving fluid import of first injector 2.
The outlet of second injector in the present embodiment links to each other with the driving fluid import of first injector through control valve, when the working medium collimation of system is less demanding, also can not be provided with.
The working medium of the two warm source spray type refrigerating system in the present embodiment can be a kind of among R600a, R600, the R134a, also can be the combination of these three kinds of working medium.
A kind of two warm sources spray type refrigerating system implementation example 2; In Fig. 2; The difference of present embodiment and embodiment 1 is: be provided with first regenerator 15 between the refrigerant inlet of the outlet of first injector 2 and condenser 3 and between the import of the outlet of first working medium pump 4 and first generator 1; The refrigerant inlet of the outlet of first injector 2 and condenser 3 links to each other through first medium channel of first regenerator 15; The import of the outlet of first working medium pump 4 and first generator 1 links to each other through second medium channel of first regenerator 15; That is to say; The import of first medium channel of first regenerator 15 links to each other with the outlet of first injector 2 and the refrigerant inlet of condenser 3 respectively with outlet, and the import of second medium channel of first regenerator 15 links to each other with the outlet of first working medium pump 4 and the import of first generator 1 respectively with outlet;
Be provided with second regenerator 16 between the refrigerant outlet of condenser 3 and the first throttle valve 5 and between the import of the high-pressure outlet of condenser/evaporator 8 and second working medium pump 11; The refrigerant outlet of condenser 3 links to each other with first medium channel of first throttle valve 5 through second regenerator 16; The import of the high-pressure outlet of condenser/evaporator 8 and second working medium pump 11 links to each other through second medium channel of second regenerator 16; That is to say; The import of first medium channel of second regenerator 16 links to each other with first throttle valve 5 with the refrigerant outlet of condenser 3 respectively with outlet, and the import of second medium channel of second regenerator 16 links to each other with the high-pressure outlet of condenser/evaporator 8 and the import of second working medium pump 11 respectively with outlet;
Be provided with the 3rd regenerator 17 between the outlet of first medium channel of second regenerator 16 and the first throttle valve 5 and between the driving fluid import of the refrigerant outlet of evaporimeter 6 and second injector 9; The outlet of first medium channel of second regenerator 16 links to each other with first medium channel of first throttle valve 5 through the 3rd regenerator 17; The driving fluid import of the refrigerant outlet of evaporimeter 6 and second injector 9 links to each other through second medium channel of the 3rd regenerator 17; That is to say; The import of first medium channel of the 3rd regenerator 17 links to each other with first throttle valve 5 with the outlet of first medium channel of second regenerator 16 respectively with outlet, and the import of second medium channel of the 3rd regenerator 17 links to each other with the refrigerant outlet of evaporimeter 6 and the driving fluid import of second injector 9 respectively with exporting.
Be provided with three regenerators in the present embodiment, in other embodiment, can one or two be set selectively.
Present and cold-producing medium R600a is the course of work that example is explained two warm sources spray type refrigerating system implementation example.Liquid refrigerant R600a is vaporized into 80 ℃ of-100 ℃ of steam at first generator 1 by 12 heating of first heating tube; Get into the steam of 2 injection second injector, 9 outlets of first injector and the outlet of condenser/evaporator 8 low-pressure channels as working fluid from the refrigerant vapour of first generator 1; Mix pressurization through first injector 2; The refrigerant vapour of first injector, 2 outlets (the about 0.4MPa of pressure~0.5MPa) get into condenser 3 to be condensed into liquid refrigerant; The liquid refrigerant of condenser 3 outlets is divided into three branch roads; Wherein one cold-producing medium is sent into first generator 1 through the pressurization of first working medium pump 4 and is heated again and is vaporized into high pressure refrigerant vapor; The cold-producing medium of second branch road becomes the lower temperature refrigeration agent through the 7 throttling step-downs of second choke valve; The low-pressure side passage that gets into condenser/evaporator 8 is then vaporized with the gaseous refrigerant heat exchange of the high-pressure side passage that coagulates evaporimeter 8; The refrigerant vapour of the low-pressure side channel outlet of condenser/evaporator 8 is aspirated to be got in first injector 2, and the cold-producing medium of the 3rd branch road becomes low-temperature refrigerant and gets into evaporimeter 6 through the 5 throttling step-downs of first throttle valve realizes cryogenic refrigeration, and the refrigerant vapour of evaporimeter 6 outlets is got in second injector 9 by the intermediate pressure refrigerant steam ejection from second generator 10; Liquid refrigerant R600a is vaporized into 60 ℃ of-80 ℃ of steam at second generator 10 by 13 heating of second heating tube; The middle compacting refrigerant vapour of second generator, 10 outlets gets into the refrigerant vapour of second injector, 9 injection evaporimeters, 6 outlets as working fluid; Mix pressurization through second injector 9; The refrigerant vapour (the about 0.2MPa of pressure) of second injector, 9 outlets is divided into two, and wherein a branch road refrigerant vapour is got in first injector 9 by the high steam suction from first generator 1 through control valve 14; The second branch road cold-producing medium gets into condenser/evaporator 8 high-pressure side channel condensings and becomes liquid refrigerant; Send into second generator 10 through 11 pressurizations of second working medium pump then and be vaporized into middle refrigerant vapour of pressing by secondary heater 13 heating again, so far, accomplish a complete cycle process.
In the middle of above-mentioned circulation, the working medium between the import of the working medium between the refrigerant outlet of condenser 3 and the first throttle valve 5 and the high-pressure outlet of condenser/evaporator 8 and second working medium pump 11 is through 15 heat exchange of first regenerator; Working medium between the import of the working medium between the refrigerant outlet of condenser 3 and the first throttle valve 5 and the high-pressure outlet of condenser/evaporator 8 and second working medium pump 11 is through 16 heat exchange of second regenerator; Working medium between the driving fluid import of the outlet of first medium channel of second regenerator 16 and the refrigerant outlet of working medium between the first throttle valve 5 and evaporimeter 6 and second injector 9 is through 17 heat exchange of the 3rd regenerator.
Occurrence temperature at first generator 1 is 80 ℃~100 ℃, and when the occurrence temperature of second generator was 60 ℃~80 ℃, above-mentioned two warm source spray type refrigerating system can obtain the cryogenic temperature of-5 ℃~-20 ℃ of scopes.

Claims (6)

1. two warm source spray type refrigerating system; It is characterized in that: comprise first generator and second generator; The operating temperature of first generator is higher than the operating temperature of second generator, and the steam (vapor) outlet of first generator links to each other with the working fluid import of first injector, and the outlet of first injector links to each other with the refrigerant inlet of condenser; The refrigerant outlet of condenser is divided into three the tunnel; First working medium pump of wherein leading up to links to each other with the import of first generator, and another road links to each other with the refrigerant inlet of evaporimeter through the first throttle valve, and Third Road links to each other with the low pressure inlet of condenser/evaporator through second choke valve; The low tension outlet of condenser/evaporator links to each other with the driving fluid import of first injector; The steam (vapor) outlet of second generator links to each other with the working fluid import of second injector, and the outlet of second injector is divided into two-way, and wherein one the tunnel links to each other with the driving fluid import of first injector; Another road links to each other with the high-pressure inlet of condenser/evaporator, and the high-pressure outlet of condenser/evaporator links to each other with the import of second generator through second working medium pump.
2. two warm source according to claim 1 spray type refrigerating system, it is characterized in that: the outlet of described second injector links to each other with the driving fluid import of first injector through control valve.
3. two warm source according to claim 2 spray type refrigerating system; It is characterized in that: be provided with first regenerator between the outlet of described first injector and the refrigerant inlet of condenser and between the import of the first working medium delivery side of pump and first generator; The outlet of first injector links to each other with first medium channel of the refrigerant inlet of condenser through first regenerator, and the import of the first working medium delivery side of pump and first generator links to each other through second medium channel of first regenerator.
4. according to claim 1 or 2 or 3 described two warm source spray type refrigerating systems; It is characterized in that: be provided with second regenerator between the refrigerant outlet of described condenser and the first throttle valve and between the import of the high-pressure outlet of condenser/evaporator and second working medium pump; The refrigerant outlet of condenser links to each other with first medium channel of first throttle valve through second regenerator, and the import of the high-pressure outlet of condenser/evaporator and second working medium pump links to each other through second medium channel of second regenerator.
5. two warm source according to claim 4 spray type refrigerating system; It is characterized in that: be provided with the 3rd regenerator between the outlet of first medium channel of described second regenerator and the first throttle valve and between the driving fluid import of the refrigerant outlet of evaporimeter and second injector; The outlet of first medium channel of second regenerator links to each other with first medium channel of first throttle valve through the 3rd regenerator, and the driving fluid import of the refrigerant outlet of evaporimeter and second injector links to each other through second medium channel of the 3rd regenerator.
6. two warm source according to claim 1 spray type refrigerating system is characterized in that: the working medium of described two warm source spray type refrigerating system is a kind of or three's among R600a, R600, the R134a combination.
CN 201110329681 2011-10-26 2011-10-26 Double-temperature-heat-source injection-type refrigeration system Expired - Fee Related CN102384604B (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102654326A (en) * 2012-05-28 2012-09-05 中国矿业大学 Double-injection refrigeration device synergized by gas-liquid ejector
CN102853578A (en) * 2012-04-19 2013-01-02 浙江大学 Mixed working medium two-stage jet type refrigerating machine
CN104676946A (en) * 2015-02-03 2015-06-03 北京建筑大学 Two-stage ejection heat exchange unit and operating mode thereof
CN105546871A (en) * 2015-12-16 2016-05-04 山东大学 Waste-heat-drive drainage and injection type refrigerating system for refrigerator car
CN107062684A (en) * 2017-05-27 2017-08-18 山东大学 One kind is without pump ejector refrigeration system and refrigerating method

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU1116277A2 (en) * 1978-10-24 1984-09-30 Одесский Завод Сельскохозяйственного Машиностроения Им.Октябрьской Революции Steam ejector freon refrigerating machine
JP2005172314A (en) * 2003-12-09 2005-06-30 Osaka Gas Co Ltd Refrigeration unit
CN101464070A (en) * 2009-01-04 2009-06-24 河南科技大学 Injection type low-temperature refrigerator
CN201828083U (en) * 2010-09-06 2011-05-11 中能东讯新能源科技(大连)有限公司 Waste-heat injecting refrigerator using R236FA as refrigerant
JP2011094814A (en) * 2009-10-27 2011-05-12 Mitsubishi Electric Corp Refrigerating cycle device and refrigerant compressing method
CN202284866U (en) * 2011-10-26 2012-06-27 河南科技大学 Double-temperature heat source spray type refrigeration system

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU1116277A2 (en) * 1978-10-24 1984-09-30 Одесский Завод Сельскохозяйственного Машиностроения Им.Октябрьской Революции Steam ejector freon refrigerating machine
JP2005172314A (en) * 2003-12-09 2005-06-30 Osaka Gas Co Ltd Refrigeration unit
CN101464070A (en) * 2009-01-04 2009-06-24 河南科技大学 Injection type low-temperature refrigerator
JP2011094814A (en) * 2009-10-27 2011-05-12 Mitsubishi Electric Corp Refrigerating cycle device and refrigerant compressing method
CN201828083U (en) * 2010-09-06 2011-05-11 中能东讯新能源科技(大连)有限公司 Waste-heat injecting refrigerator using R236FA as refrigerant
CN202284866U (en) * 2011-10-26 2012-06-27 河南科技大学 Double-temperature heat source spray type refrigeration system

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
张博等: "低品位余热源新型双喷射式制冷系统研究", 《大连理工大学学报》 *
张博等: "新型太阳能双喷射制冷系统的理论研究", 《太阳能学报》 *

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102853578A (en) * 2012-04-19 2013-01-02 浙江大学 Mixed working medium two-stage jet type refrigerating machine
CN102853578B (en) * 2012-04-19 2014-06-25 浙江大学 Mixed working medium two-stage jet type refrigerating machine
CN102654326A (en) * 2012-05-28 2012-09-05 中国矿业大学 Double-injection refrigeration device synergized by gas-liquid ejector
CN102654326B (en) * 2012-05-28 2013-12-11 中国矿业大学 Double-injection refrigeration device synergized by gas-liquid ejector
CN104676946A (en) * 2015-02-03 2015-06-03 北京建筑大学 Two-stage ejection heat exchange unit and operating mode thereof
CN105546871A (en) * 2015-12-16 2016-05-04 山东大学 Waste-heat-drive drainage and injection type refrigerating system for refrigerator car
CN107062684A (en) * 2017-05-27 2017-08-18 山东大学 One kind is without pump ejector refrigeration system and refrigerating method
CN107062684B (en) * 2017-05-27 2019-10-29 山东大学 It is a kind of without pump ejector refrigeration system and refrigerating method

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