CN204787383U - From overlapping vapour pressure formula cooling cycle system that contracts - Google Patents
From overlapping vapour pressure formula cooling cycle system that contracts Download PDFInfo
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- CN204787383U CN204787383U CN201520343225.7U CN201520343225U CN204787383U CN 204787383 U CN204787383 U CN 204787383U CN 201520343225 U CN201520343225 U CN 201520343225U CN 204787383 U CN204787383 U CN 204787383U
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Abstract
The utility model discloses a from overlapping vapour compression refrigeration circulation system, including vapour and liquid separator no. 1, evaporation -condensation ware, evaporimeter and expansion valve, wherein, be connected with first sprayer between vapour and liquid separator's no. 1 the saturated refrigerant liquid outlet and the evaporation side entrance of evaporation -condensation ware, be connected with vapour and liquid separator no. 2 between the condensation side export of evaporation -condensation ware and the entry of evaporimeter, be connected with the second sprayer between this vapour and liquid separator's no. 2 entry and the export of the condensation of evaporation -condensation ware side. The beneficial effect of the utility model: for the conventionality from overlapping cooling cycle system, the utility model discloses an adopt two sprayers to replace expansion valve or capillary in the system, fully retrieve throttle process's expansion work to promote the pressure of breathing in of compressor, and then reduced the power consumption of compressor in the circulation, also improved the gas transmission volume of compressor, effectively promoted circulation system's performance.
Description
Technical field
The utility model relates to technical field of refrigeration equipment, specifically, relates to a kind of Auto-cascade cycle steam compressed refrigerating circulating system, especially a kind of two Auto-cascade cycle steam compressed refrigerating circulating system spraying synergy.
Background technology
Auto-cascading refrigeration system a kind of realizes multistage automatic cascade by single compressor, thus obtain the refrigeration system of lower cryogenic temperature, relative to cascade refrigeration system, and structure is simple, cost is low advantage that it has.Auto-cascading refrigeration system has larger operation temperature area, therefore obtains in the field such as general cold, cryotronics, cryogenic medicine, freeze drying and applies widely.In the self-cascade refrigeration system system of routine, usual employing choke valve or capillary as throttle part, because the operating temperature of self-cascade refrigeration system system is larger, so, larger restriction loss can be there is in throttling process, cause the Energy Efficiency Ratio of system lower.Therefore, carry out alternative expansion valve by using injector in self-cascade refrigeration system system or capillary carrys out recovery section expansion work, thus improve the efficiency of circulation.
Emitter construction is simple, with low cost, movement-less part, be suitable for any fluid, at present about the application of injector, great majority utilize the expansion work in injector recovery steam compression type refrigerating, heat pump circulating system throttling process, promote the pressure of inspiration(Pi) of compressor, thus reduce compressor power consumption in circulation, raising compressor displacement, effectively promote circulatory system performance.The method that current injector is applied on auto-cascading refrigeration system also compares shortage, and therefore, the application of injector in self-cascade refrigeration system system has positive meaning.
Utility model content
For the problem in correlation technique, the utility model proposes a kind of Auto-cascade cycle steam compressed refrigerating circulating system, it uses dual jet to substitute expansion valve or capillary, reclaim the expansion work in throttling process, promote the pressure of inspiration(Pi) of compressor, thus reduce the power consumption of compressor in circulation and improve the displacement of compressor, reach the object improving refrigeration system efficiency.
The technical solution of the utility model is achieved in that
A kind of Auto-cascade cycle Vapor Compression Refrigeration Cycle system, comprise the compressor, condenser, gas-liquid separator one, evaporative condenser, evaporimeter and the expansion valve that are connected by pipeline, wherein, the first injector is connected with between the saturated refrigerant liquid outlet of described gas-liquid separator one and the evaporation side entrance of evaporative condenser, be connected with gas-liquid separator two between the condensation side outlet of described evaporative condenser and the entrance of evaporimeter, between the entrance of this gas-liquid separator two and the condensation side of evaporative condenser export, be connected with the second injector;
Wherein, the Working-fluid intaking of described first injector is connected with the saturated refrigerant liquid outlet of described gas-liquid separator one, the operative fluid outlet of described first injector is connected with the evaporation side entrance of evaporative condenser, and the driving fluid entrance of described first injector is connected with the gas vent of the saturated cold-producing medium of described gas-liquid separator two;
Wherein, the Working-fluid intaking of described second injector exports with the condensation side of evaporative condenser and is connected, the operative fluid outlet of described second injector is connected with the entrance of described gas-liquid separator two, and the driving fluid entrance of described second injector is connected with the outlet of evaporimeter.
In addition, in described first injector, the pressure from the saturated liquid cold-producing medium of described gas-liquid separator one is greater than the pressure of the saturated gas cold-producing medium from described gas-liquid separator two.
Further, in described second injector, the pressure from the saturated liquid cold-producing medium of described evaporative condenser is greater than the pressure of the saturated gas cold-producing medium from described evaporimeter.
In such scheme, the cold-producing medium in described first injector and described second injector is non-azeotropic refrigerant.And, described gas-liquid separator one and described first injector form first separation-supercharging-mixing (namely carry out being separated, supercharging and the mixing) unit of Mix refrigerant cycle, the secondary separation-supercharging-mixing of described gas-liquid separator two and described second injector formation Mix refrigerant cycle (namely carry out being separated, supercharging and mixing) unit.
The beneficial effects of the utility model: relative to the self-cascade refrigeration system system of routine, the utility model replaces expansion valve or capillary by adopting two injectors in systems in which, the expansion work of abundant recovery throttling process, thus improve the pressure of inspiration(Pi) of compressor, and then reduce the power consumption of compressor in circulation, also improve the displacement of compressor, effectively improve the performance of the circulatory system.
In addition, the utility model also carries out twice separation and mixing by employing two gas-liquid separators, injector to Mix refrigerant cycle, thus it is higher to make to enter low boiling point refrigerant content in the refrigeration working medium of evaporimeter, realizes lower evaporating temperature and less temperature glide.
Accompanying drawing explanation
In order to be illustrated more clearly in the utility model embodiment or technical scheme of the prior art, be briefly described to the accompanying drawing used required in embodiment below, apparently, accompanying drawing in the following describes is only embodiments more of the present utility model, for those of ordinary skill in the art, under the prerequisite not paying creative work, other accompanying drawing can also be obtained according to these accompanying drawings.
Fig. 1 is the structural representation of the Auto-cascade cycle Vapor Compression Refrigeration Cycle system according to the utility model embodiment;
Fig. 2 is the work pressure-enthalpy diagram of the Auto-cascade cycle Vapor Compression Refrigeration Cycle system according to the utility model embodiment.
In figure:
101, compressor; 102, condenser; 103, gas-liquid separator one; 104, evaporative condenser; 105, gas-liquid separator two; 106, evaporimeter; 107, expansion valve; 108, the first injector; 109, the second injector.
Detailed description of the invention
Below in conjunction with the accompanying drawing in the utility model embodiment, be clearly and completely described the technical scheme in the utility model embodiment, obviously, described embodiment is only the utility model part embodiment, instead of whole embodiments.Based on the embodiment in the utility model, the every other embodiment that those of ordinary skill in the art obtain, all belongs to the scope of the utility model protection.
According to embodiment of the present utility model, provide a kind of Auto-cascade cycle Vapor Compression Refrigeration Cycle system.
As shown in Figure 1, according to the Auto-cascade cycle Vapor Compression Refrigeration Cycle system of the utility model embodiment, comprise the compressor 101 connected by pipeline, condenser 102, gas-liquid separator 1, evaporative condenser 104, gas-liquid separator 2 105, evaporimeter 106, expansion valve 107 and the first injector 108 and the second injector 109, wherein, the outlet of compressor 101 connects the entrance of condenser 102, the outlet of condenser 102 connects the entrance of gas-liquid separator 1, the outlet of gas-liquid separator 1 is divided into two-way: a saturated refrigerant liquid outlet in road connects the Working-fluid intaking of the first injector 108, the saturated refrigerant gas outlet in another road connects the condensation side entrance of evaporative condenser 104, the Working-fluid intaking of condensation side outlet connection second injector 109 of evaporative condenser 104, the operative fluid outlet of the second injector 109 connects the entrance of gas-liquid separator 2 105, the outlet of gas-liquid separator 2 105 is divided into two-way: a saturated refrigerant liquid outlet in road connects the entrance of expansion valve 107, the outlet of expansion valve 107 connects the entrance of evaporimeter 106, the outlet of evaporimeter 106 connects the driving fluid entrance of the second injector 109, the saturated refrigerant gas outlet in another road connects the driving fluid entrance of the first injector 108, the outlet of the first injector 108 connects the evaporation side entrance of evaporative condenser 104, the evaporation side outlet of evaporative condenser 104 connects compressor 101 and exports, complete circulation.
In said system, the first injector 108 and the second injector 109 is adopted to substitute expansion valve or capillary, reclaim the demi-inflation merit of throttling process, and enter the Working-fluid intaking of the first injector 108 as working fluid from the saturated refrigerant liquid of high pressure of gas-liquid separator 1, and injection enters the driving fluid entrance of the first injector 108 from the saturated refrigerant gas of the low pressure of gas-liquid separator 2 105, two fluids mixes and supercharging in the first injector 108; And to enter the Working-fluid intaking of the second injector 109 as working fluid from the high-pressure refrigerant liquid of evaporative condenser 104 condensation side outlet, and injection carrys out the low pressure refrigerant liquid that flash-pot 106 exports enters the driving fluid entrance of the second injector 109, two fluids mix also supercharging in the second injector 109.
In order to better understand said system scheme of the present utility model, below in conjunction with the work pressure-enthalpy diagram (p-h figure) of said system, said system of the present utility model is described in detail.
Fig. 2 is the p-h figure of Auto-cascade cycle Vapor Compression Refrigeration Cycle system of the present utility model, the system work process illustrated is: the superheated refrigerant gas (in figure 2 places) that compressor 101 exports enters in condenser 102 and is condensed into quarter-phase system cold fluid (in figure 3 places), and this two phase refrigerant fluid is divided into two-way in gas-liquid separator 1: a saturated refrigerant liquid in road (in figure 5 places) enters the Working-fluid intaking of the first injector 108 as working fluid, the condensation side cooling that the saturated refrigerant gas in another road (in figure 4 places) enters evaporative condenser 104 becomes saturated or crosses cold refrigerant liquid (in figure 6 places), this is saturated or cross cold refrigerant liquid enters the second injector 109 Working-fluid intaking as working fluid, the two phase refrigerant liquid (in figure 7 places) that second injector 109 exports enters in gas-liquid separator 2 105 and is divided into two-way: a saturated refrigerant liquid in road (in figure 8 places) enters throttling in expansion valve 107 becomes two phase refrigerant fluid (in figure 9 places), this two phase refrigerant fluid enters evaporation in evaporimeter 106 becomes saturated or superheated refrigerant steam (in figure 10 places), this saturated or superheated refrigerant steam is entered the driving fluid entrance of the second injector 109 by injection as driving fluid, the saturated refrigerant gas in another road (in figure 11 places) is entered the driving fluid entrance of the first injector 108 by injection as driving fluid, the evaporation side that the two phase refrigerant liquid (in figure 12 places) that first injector 108 exports enters evaporative condenser 104 flashes to superheated refrigerant steam (in figure 1 place), get back to compressor 101, complete circulation.
As can be seen here, by means of technique scheme of the present utility model, expansion valve or capillary is replaced by adopting two injectors in systems in which, the expansion work of abundant recovery throttling process, thus improve the pressure of inspiration(Pi) of compressor, and then reduce the power consumption of compressor in circulation, also improve the displacement of compressor, effectively improve the performance of the circulatory system.In addition, by adopting two gas-liquid separators, injector carries out twice separation and mixing to Mix refrigerant cycle, thus makes to enter in the refrigeration working medium of evaporimeter that low boiling point refrigerant content can be higher, realizes lower evaporating temperature and less temperature glide.Simultaneously, emitter construction is simple, with low cost, without motion merit, use under being suitable for comprising any fluid of two phase flow, so, said system of the present utility model is a kind of economy, effective, feasible improving countermeasure, effectively can improve the performance of Auto-cascade cycle vapor compression refrigeration system, promote the development of Auto-cascade cycle Vapor Compression Refrigeration Cycle systematic energy-saving technology, bring better economic benefit and social benefit.
The foregoing is only preferred embodiment of the present utility model; not in order to limit the utility model; all within spirit of the present utility model and principle, any amendment done, equivalent replacement, improvement etc., all should be included within protection domain of the present utility model.
Claims (5)
1. an Auto-cascade cycle Vapor Compression Refrigeration Cycle system, comprise the compressor, condenser, gas-liquid separator one, evaporative condenser, evaporimeter and the expansion valve that are connected by pipeline, it is characterized in that, the first injector is connected with between the saturated refrigerant liquid outlet of described gas-liquid separator one and the evaporation side entrance of evaporative condenser, be connected with gas-liquid separator two between the condensation side outlet of described evaporative condenser and the entrance of evaporimeter, the entrance of this gas-liquid separator two is connected the second injector between exporting with the condensation side of evaporative condenser;
Wherein, the Working-fluid intaking of described first injector is connected with the saturated refrigerant liquid outlet of described gas-liquid separator one, the operative fluid outlet of described first injector is connected with the evaporation side entrance of evaporative condenser, and the driving fluid entrance of described first injector is connected with the saturated refrigerant gas outlet of described gas-liquid separator two;
Wherein, the Working-fluid intaking of described second injector exports with the condensation side of evaporative condenser and is connected, the operative fluid outlet of described second injector is connected with the entrance of described gas-liquid separator two, and the driving fluid entrance of described second injector is connected with the outlet of evaporimeter.
2. Auto-cascade cycle Vapor Compression Refrigeration Cycle system according to claim 1, it is characterized in that, in described first injector, the pressure from the saturated liquid cold-producing medium of described gas-liquid separator one is greater than the pressure of the saturated gas cold-producing medium from described gas-liquid separator two.
3. Auto-cascade cycle Vapor Compression Refrigeration Cycle system according to claim 2, it is characterized in that, in described second injector, the pressure from the saturated liquid cold-producing medium of described evaporative condenser is greater than the pressure of the saturated gas cold-producing medium from described evaporimeter.
4. Auto-cascade cycle Vapor Compression Refrigeration Cycle system according to claim 3, is characterized in that, the cold-producing medium in described first injector and described second injector is non-azeotropic refrigerant.
5. Auto-cascade cycle Vapor Compression Refrigeration Cycle system according to claim 4, it is characterized in that, described gas-liquid separator one and described first injector form the first separation-supercharging-mixed cell of Mix refrigerant cycle, and described gas-liquid separator two and described second injector form the secondary separation-supercharging-mixed cell of Mix refrigerant cycle.
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| CN201520343225.7U CN204787383U (en) | 2015-05-25 | 2015-05-25 | From overlapping vapour pressure formula cooling cycle system that contracts |
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| CN201520343225.7U CN204787383U (en) | 2015-05-25 | 2015-05-25 | From overlapping vapour pressure formula cooling cycle system that contracts |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104864622A (en) * | 2015-05-25 | 2015-08-26 | 青岛海尔特种电冰柜有限公司 | Auto-cascade steam compression type refrigeration cycle system |
| 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 |
| CN108679878A (en) * | 2018-04-27 | 2018-10-19 | 西安交通大学 | Using the self-cascade refrigeration system system and refrigerating and circulating method of dual jet synergy |
| CN109312962A (en) * | 2016-06-16 | 2019-02-05 | 株式会社电装 | Refrigerating circulatory device |
| CN113654258A (en) * | 2021-08-12 | 2021-11-16 | 广东工业大学 | Efficient heat pump system and working method thereof |
-
2015
- 2015-05-25 CN CN201520343225.7U patent/CN204787383U/en active Active
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104864622A (en) * | 2015-05-25 | 2015-08-26 | 青岛海尔特种电冰柜有限公司 | Auto-cascade steam compression type refrigeration cycle system |
| CN109312962A (en) * | 2016-06-16 | 2019-02-05 | 株式会社电装 | Refrigerating circulatory device |
| CN109312962B (en) * | 2016-06-16 | 2020-11-10 | 株式会社电装 | Refrigeration cycle device |
| 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 |
| CN106546026B (en) * | 2016-10-25 | 2019-05-10 | 西安交通大学 | Duel-temperature refrigeration cycle system is segregated using the non-azeotropic mixed working medium of injector synergy |
| CN108679878A (en) * | 2018-04-27 | 2018-10-19 | 西安交通大学 | Using the self-cascade refrigeration system system and refrigerating and circulating method of dual jet synergy |
| 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 |
| CN113654258A (en) * | 2021-08-12 | 2021-11-16 | 广东工业大学 | Efficient heat pump system and working method thereof |
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