CN202547181U - Two-stage refrigerant mixture injection type refrigerator - Google Patents
Two-stage refrigerant mixture injection type refrigerator Download PDFInfo
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- CN202547181U CN202547181U CN2012201684071U CN201220168407U CN202547181U CN 202547181 U CN202547181 U CN 202547181U CN 2012201684071 U CN2012201684071 U CN 2012201684071U CN 201220168407 U CN201220168407 U CN 201220168407U CN 202547181 U CN202547181 U CN 202547181U
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- 239000000203 mixture Substances 0.000 title claims abstract description 14
- 238000002347 injection Methods 0.000 title abstract description 19
- 239000007924 injection Substances 0.000 title abstract description 19
- 239000003507 refrigerant Substances 0.000 title abstract description 12
- 239000007788 liquid Substances 0.000 claims abstract description 94
- 239000007791 liquid phase Substances 0.000 claims abstract description 10
- 239000012071 phase Substances 0.000 claims abstract description 4
- 239000012530 fluid Substances 0.000 claims description 101
- 230000008676 import Effects 0.000 claims description 48
- 239000007792 gaseous phase Substances 0.000 claims description 13
- 239000000126 substance Substances 0.000 claims description 10
- 238000005057 refrigeration Methods 0.000 abstract description 31
- 230000000694 effects Effects 0.000 abstract description 9
- 238000009835 boiling Methods 0.000 description 54
- 239000007921 spray Substances 0.000 description 25
- 238000009833 condensation Methods 0.000 description 23
- 230000005494 condensation Effects 0.000 description 23
- 239000007789 gas Substances 0.000 description 16
- 238000001704 evaporation Methods 0.000 description 14
- MSSNHSVIGIHOJA-UHFFFAOYSA-N pentafluoropropane Chemical compound FC(F)CC(F)(F)F MSSNHSVIGIHOJA-UHFFFAOYSA-N 0.000 description 8
- 239000000243 solution Substances 0.000 description 6
- 238000000034 method Methods 0.000 description 5
- 230000009102 absorption Effects 0.000 description 4
- 238000010521 absorption reaction Methods 0.000 description 4
- 230000008020 evaporation Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 238000002156 mixing Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000002309 gasification Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000009897 systematic effect Effects 0.000 description 1
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Abstract
The utility model discloses a two-stage refrigerant mixture injection type refrigerator which comprises a throttling element, an evaporator, two injectors, two condensers, two pumps, two generators, a low-pressure condenser and a first gas-liquid separator. The low-pressure condenser is used for converting refrigerant liquid of an outlet of the low-pressure injector into gas and liquid mixture; the first gas-liquid separator is used for separating the gas and liquid mixture into two phases; a gas-phase outlet of the first gas-liquid separator is connected with a injected liquid inlet of the high-pressure injector; and a liquid-phase outlet of the first gas-liquid separator is sequentially serially connected with working liquid inlets of the low-pressure pump, the low-pressure generator and the low-pressure injector. Medium-pressure refrigerant of the outlet of the low-pressure injector is partially condensed and then is directly pumped into the low-pressure generator, and load of the high-pressure injector is reduced, so that an effect of increasing the integral performance of a system is achieved. The two-stage refrigerant mixture injection type refrigeration has a good application prospect.
Description
Technical field
The utility model belongs to refrigeration technology field, especially relates to a kind of mixed working fluid two-stage ejector type refrigerating machine.
Background technology
Injector was used for refrigeration first in 1910; And extensively apply to the air-conditioning refrigeration system of building the thirties in 20th century; But higher by efficient subsequently, the compacter mechanical compression type refrigeration of equipment replaces, and the research work of injector after this stays cool always.Along with the appearance of energy crisis and the raising of people's awareness of saving energy, spray type refrigerating has obtained people's attention again.
The spray type refrigerating technology is the Refrigeration Technique that a kind of heat energy drives; Comparing its major advantage with the mechanical compression type Refrigeration Technique is only to need to consume mechanical energy seldom; Can directly utilize heat energy, have that device structure is simple, volume is little, cost is low, an advantage such as reliable, long service life as drive energy.
Chinese invention patent ZL200610104934.9; " a kind of self-overlapping refrigerating cycle system with injector " discloses the self-overlapping refrigerating cycle system of band injector; Comprise compressor, condenser, gas-liquid separator, evaporative condenser, evaporimeter and expansion valve that pipeline links to each other, also have injector between evaporative condenser and the evaporimeter.The injector supercharging can improve compressor air suction pressure, reduces pressure ratio, reduces work done during compression.But when the condensation temperature of spray type refrigerating system was higher, the single-stage spray type refrigerating was difficult to provide the pressure reduction of condenser and evaporimeter in the system.
Though publication number is the disclosed refrigeration system of the two-stage steam jet refrigeration system of CN101832680A is in traditional single-stage injection refrigerating system, to set up an injector; With the pressurization of performance injector to refrigerant vapour; To improve coefficient of refrigerating performance, the load of injector is increased but add an injector.Chinese invention patent ZL200910304106.X and for example; " a kind of auto-cascade injection low-temperature refrigeration circulating device " discloses a kind of auto-cascade injection low-temperature refrigeration circulating device; Comprise generator, gas ejector, working medium pump, condenser, gas-liquid separator, evaporator unit and condensation injector; Wherein the gas ejector outlet links to each other with the import of condensation injector injection; Though the series connection through two-stage ejector (being divided into hiigh pressure stage and low-pressure stage) can provide bigger pressure reduction, because the flow of hiigh pressure stage is bigger, the Energy Efficiency Ratio of system is still very low.
The utility model content
The utility model has proposed a kind of mixed working fluid two-stage ejector type refrigerating machine to the deficiency and the defective of existing spray type refrigerating system, improves the performance of system through flow and the load that reduces hiigh pressure stage injector and low-pressure stage injector simultaneously.
A kind of mixed working fluid two-stage ejector type refrigerating machine; Comprise low-pressure stage injector and hiigh pressure stage injector; Be connected with first loop between the working fluid import of the outlet of said hiigh pressure stage injector and hiigh pressure stage injector, first loop comprises hiigh pressure stage condenser, hiigh pressure stage pump and the hiigh pressure stage generator of connecting successively with the outlet of hiigh pressure stage injector; Be connected with second loop between the driving fluid import of the outlet of said hiigh pressure stage injector and said low-pressure stage injector, second loop comprises hiigh pressure stage condenser, first throttle element and the evaporimeter of connecting successively with the outlet of hiigh pressure stage injector; Comprise that the fluid working substance with the outlet of low-pressure stage injector is converted into the low-pressure stage condenser of gas-liquid mixture; Be used for said gas-liquid mixture is separated into first gas-liquid separator of two phases; The gaseous phase outlet of first gas-liquid separator links to each other with the driving fluid import of hiigh pressure stage injector, and the liquid phase of first gas-liquid separator exports the working fluid import of connect successively low-pressure stage pump, low-pressure stage generator and low-pressure stage injector.
In the utility model; The zeotrope that the fluid working substance of filling in the ejector type refrigerating machine mixes for two or more working medium; Wherein be rich in higher boiling working medium at the saturation pressure under the condensation temperature of low-pressure stage condenser greater than being rich in the saturation pressure of low boiling working fluid under evaporating temperature, be rich in low boiling working fluid at the saturation pressure under the condensation temperature of hiigh pressure stage condenser greater than being rich in the saturation pressure of higher boiling working medium under the condensation temperature of low-pressure stage condenser.The pure working medium of the fluid of selecting for use can be various pure cold-producing mediums, as with R245fa as higher boiling working medium, with R600a as low boiling working fluid.
In the utility model, described intermediate pressure is a certain pressure between evaporating pressure and hiigh pressure stage condensing pressure.
In the utility model, described evaporating temperature for mixed working fluid, refers to the dew-point temperature of evaporimeter inner refrigerant; For pure matter cold-producing medium, refer to the gasification temperature of evaporimeter inner refrigerant.
In the utility model, described condensation temperature for mixed working fluid, refers to the dew-point temperature of condenser inner refrigerant; For pure matter cold-producing medium, refer to the adiabatic condensation temperature of condenser inner refrigerant.
The workflow of the utility model is: become gases at high pressure after the fluid that is rich in higher boiling working medium absorbs heat in the low-pressure stage generator; The fluid that is rich in higher boiling working medium of low-pressure stage generator exports gets into the fluid that is rich in low boiling working fluid in the low-pressure stage injector injection evaporimeter as working fluid; The fluid that is rich in low boiling working fluid is boosted to intermediate pressure (abbreviating middle pressure as) by injection; And in the low-pressure stage injector with after the fluid that is rich in higher boiling working medium mixes through the heat release of low-pressure stage condenser condenses; Fluid-mixing is got into first gas-liquid separator by partial liquefaction.The liquid that is rich in higher boiling working medium in first gas-liquid separator gets into the low-pressure stage generator through low-pressure stage pump pressurization, and the gas that is rich in low boiling working fluid in first gas-liquid separator is boosted by the fluid injection that is rich in low boiling working fluid of hiigh pressure stage generator exports high pressure and feeds the heat release of hiigh pressure stage condenser condenses and become liquid.The fluid body that is rich in low boiling working fluid of hiigh pressure stage condensator outlet is divided into two strands, and wherein one absorbs heat in the hiigh pressure stage generator through the hiigh pressure stage pump becomes gases at high pressure; Another stock-traders' know-how gets into evaporator evaporation heat absorption acquisition refrigerating capacity after crossing the first throttle element.System accomplishes the one action process.Get off directly to pump into the low-pressure stage generator because the middle pressure of low-pressure stage injector outlet is rich in the fluid condensation of higher boiling working medium quilt, reduce the flow and the load of hiigh pressure stage injector, thereby play the effect of the effect that improves the entire system performance.
Said high pressure generator and low pressure generator can be by solar energy, motor exhaust, and fuel combustion heat, external heat sources such as electric current Joule heat drive.
Low-pressure stage condenser and hiigh pressure stage condenser are cooled off by extraneous low-temperature receiver.The condensation temperature of the condensation temperature of low-pressure stage condenser and hiigh pressure stage condenser can be identical also can be different, specifically look the fluid working substance of being selected for use and decide with the operating mode that sets.
Said first throttle element, second restricting element can be selected U type pipe, capillary, versions such as choke valve.
As preferably; Said second loop comprises that the fluid working substance that the hiigh pressure stage condenser is come out is divided into second restricting element of gas-liquid mixture and said gas-liquid mixture is separated into two mutually second gas-liquid separators, and the gaseous phase outlet of second gas-liquid separator is linked to be the driving fluid import that is connected described hiigh pressure stage injector after a tunnel with the gaseous phase outlet of said first gas-liquid separator; The liquid phase outlet of second gas-liquid separator is connected with said first throttle element.
After adopting above-mentioned preferred version; The liquid that is rich in low boiling working fluid of hiigh pressure stage condensator outlet gets into second gas-liquid separator after being throttled to intermediate pressure by second restricting element; The gas that is rich in low boiling working fluid in second gas-liquid separator is boosted by hiigh pressure stage injector injection and gets into the hiigh pressure stage condenser, gets into the evaporator evaporation heat absorption behind the liquid process first throttle element that is rich in low boiling working fluid in second gas-liquid separator and obtains refrigerating capacity.Since intermediate pressure down can not throttling refrigeration the gas that is rich in low boiling working fluid walked by hiigh pressure stage injector injection, reduced the flow and the load of low-pressure stage injector, play the effect of raising entire system performance.
More preferred; The utility model comprises the low-pressure stage regenerator; The low-pressure stage regenerator has two heat exchange pipes of isolating each other; Wherein a heat exchange pipe is the connecting line between low-pressure stage injector and the low-pressure stage condenser, and another heat exchange pipe is the connecting line between low-pressure stage pump and the low-pressure stage generator.Further; The utility model also can comprise the hiigh pressure stage regenerator; The hiigh pressure stage regenerator has two heat exchange pipes of isolating each other; Wherein a heat exchange pipe is the connecting line between hiigh pressure stage injector and the hiigh pressure stage condenser, and another heat exchange pipe is the connecting line between hiigh pressure stage pump and the hiigh pressure stage generator.
After adopting above-mentioned preferred version; The fluid working substance that utilizes the low-pressure stage injector to export preheats the fluid that is rich in higher boiling working medium of low-pressure stage pump discharge; Utilize the fluid that is rich in low boiling working fluid that low boiling working fluid preheats the hiigh pressure stage pump discharge that is rich in of hiigh pressure stage injector outlet; Thereby can reduce the heat that adds of hiigh pressure stage generator and low-pressure stage generator, play the effect that improves the entire system performance.
As preferably, described first gas-liquid separator, second gas-liquid separator adopt the version of rectifier, realize being rich in higher boiling working medium and the good separation that is rich in low boiling working fluid.
The utlity model has following beneficial effect:
1. the utility model drives through hiigh pressure stage generator and two thermals source of low-pressure stage generator, need not to utilize the employed compressor of common refrigeration system;
2. the flow direction of the gas of gas-liquid separator outlet and liquid working substance is different; Role is also different in circulation; The gas that first gas-liquid separator comes out in the utility model flows into the hiigh pressure stage injector, and liquid flows into solution pump (being the low-pressure stage pump), improves the load (promptly reducing the flow of hiigh pressure stage injector) that reduces the hiigh pressure stage injector through this; Reduce the generation heat of hiigh pressure stage generator, thereby improve system effectiveness.
In sum; Compare single-stage spray type refrigerating system, the utility model is owing to adopt two-stage ejector, can adopt one identical or adopt the thermal source of two different temperatures; Bigger condensing pressure and evaporating pressure pressure reduction can also be provided in addition, can under higher condensation temperature, move; Compare two-stage spray type refrigerating system; The non-azeotropic mixed working medium that the utility model utilization is mixed by two or more pure matter; Make the middle pressure working medium partial condensation of low-pressure stage injector outlet get off directly to pump into the low-pressure stage generator, reduce the load of hiigh pressure stage injector; Second restricting element outlet can not be used for the middle pressure Working medium gas of throttling refrigeration by hiigh pressure stage injector injection; Reduced the load of low-pressure stage injector; Thereby play the effect that improves the entire system performance, so the utility model can be raised the efficiency greatly under identical operating mode.The utility model can be used for improving the performance of various existing spray type refrigerating system in addition.
Description of drawings
Fig. 1 is the flow chart of a kind of embodiment of the utility model.
Fig. 2 is the flow chart of the another kind of embodiment of the utility model.
Fig. 3 is the flow chart of another embodiment of the utility model.
Fig. 4 is the flow chart of existing single-stage spray type refrigerating system.
Fig. 5 is the flow chart of existing two-stage spray type refrigerating system.
Wherein: 1, first throttle element; 2, evaporimeter; 3, low-pressure stage injector; 4, low-pressure stage condenser; 5, first gas-liquid separator; 6, hiigh pressure stage injector; 7, hiigh pressure stage condenser; 8, low-pressure stage pump; 9, low-pressure stage generator; 10, hiigh pressure stage pump; 11, hiigh pressure stage generator; 12, second restricting element; 13, second gas-liquid separator; 14, low-pressure stage regenerator; 15, hiigh pressure stage regenerator; 16, generator; 17, condenser; 18, injector; 19, solution pump; 20, hiigh pressure stage injector; 21, low-pressure stage injector; 1a, first import; 1b, first outlet; 2a, second import; 2b, second outlet; 3a, first import; 3b, first outlet; 4a, second import; 4b, second outlet.
The specific embodiment
Followingly the utility model is described in further detail with reference to accompanying drawing and specific embodiment.
As shown in Figure 1; Fig. 1 is the flow chart of a kind of embodiment of the utility model; Mixed working fluid two-stage ejector type refrigerating machine shown in Figure 1 comprises first throttle element 1, evaporimeter 2, low-pressure stage injector 3, low-pressure stage condenser 4, first gas-liquid separator 5, hiigh pressure stage injector 6, hiigh pressure stage condenser 7, low-pressure stage pump 8, low-pressure stage generator 9, hiigh pressure stage pump 10 and hiigh pressure stage generator 11; Wherein, the outlet of the low-pressure stage injector 3 working fluid import of liquid phase outlet, low-pressure stage pump 8, low-pressure stage generator 9 and low-pressure stage injector 3 of import, first gas-liquid separator 5 of low-pressure stage condenser 4, first gas-liquid separator 5 of connecting successively; The gaseous phase outlet of first gas-liquid separator 5 connect successively the driving fluid import of hiigh pressure stage injector 6, the outlet and the hiigh pressure stage condenser 7 of hiigh pressure stage injector 6; The outlet of hiigh pressure stage condenser 7 is divided into two-way (being the first via and the second tunnel); The first via is connected with the working fluid import of hiigh pressure stage pump 10, hiigh pressure stage generator 11, hiigh pressure stage injector 6 successively, and the second the tunnel is connected with the driving fluid import of first throttle element 1, evaporimeter 2, low-pressure stage injector 3 successively.
Solid line is the circulation route that is rich in low boiling working fluid among the figure, and dotted line is the circulation route that is rich in higher boiling working medium.Being rich in becomes gases at high pressure after higher boiling working medium is absorbed heat in low-pressure stage generator 9; The higher boiling working medium that is rich in of low-pressure stage generator 9 outlets gets into the low boiling working fluid that is rich in the low-pressure stage injector 3 injection evaporimeters 2 as working fluid; Be rich in low boiling working fluid and boosted to intermediate pressure by injection; And in low-pressure stage injector 3 be rich in higher boiling working medium and mix after through the 4 condensation heat releases of low-pressure stage condenser; Be rich in higher boiling working medium by liquefaction fully, and be rich in low boiling working fluid, get into first gas-liquid separator 5 still for gaseous state.The higher boiling worker quality liquid that is rich in first gas-liquid separator 5 is boosted and feeds the 7 condensation heat releases of hiigh pressure stage condenser and become liquid by the low boiling working fluid injection that is rich in of hiigh pressure stage generator 11 outlet high pressure through the low boiling working fluid gas that is rich in that low-pressure stage pump 8 pressurization gets in low-pressure stage generators 9, the first gas-liquid separators 5.The low boiling working fluid liquid that is rich in of hiigh pressure stage condenser 7 outlets is divided into two strands, and wherein one absorbs heat in hiigh pressure stage generator 11 through hiigh pressure stage pump 10 becomes gases at high pressure; Another stock-traders' know-how is crossed first throttle element 1 back and is got into evaporimeter 2 evaporation heat absorption acquisition refrigerating capacitys.System accomplishes the one action process.Because the middle pressure of low-pressure stage injector 3 outlet is rich in higher boiling working medium and is condensed and directly pumps into low-pressure stage generator 9, reduces the flow and the load of hiigh pressure stage injector 6, thereby plays the effect that improves the entire system performance.Above-mentioned first gas-liquid separator 5 can select to adopt the version of rectifier.
As shown in Figure 2, Fig. 2 is the flow chart of the another kind of embodiment of the utility model.Mixed working fluid two-stage ejector type refrigerating machine shown in Figure 2 comprises first throttle element 1, evaporimeter 2, low-pressure stage injector 3, low-pressure stage condenser 4, first gas-liquid separator 5, hiigh pressure stage injector 6, hiigh pressure stage condenser 7, low-pressure stage pump 8, low-pressure stage generator 9, hiigh pressure stage pump 10, hiigh pressure stage generator 11, second restricting element 12 and second gas-liquid separator 13; Wherein, the outlet of the low-pressure stage injector 3 working fluid import of liquid phase outlet, low-pressure stage pump 8, low-pressure stage generator 9 and low-pressure stage injector 3 of import, first gas-liquid separator 5 of low-pressure stage condenser 4, first gas-liquid separator 5 of connecting successively; The gaseous phase outlet of first gas-liquid separator 5 connect successively the driving fluid import of hiigh pressure stage injector 6, the outlet of hiigh pressure stage injector 6 and the import of hiigh pressure stage condenser 7; The outlet of hiigh pressure stage condenser 7 is divided into two-way (being the first via and the second tunnel); The first via is connected with the working fluid import of hiigh pressure stage pump 10, hiigh pressure stage generator 11, hiigh pressure stage injector 6 successively; The second the tunnel links to each other with the import of second gas-liquid separator 13; The gaseous phase outlet of second gas-liquid separator 13 is linked to be the driving fluid import that is connected hiigh pressure stage injector 6 after a tunnel with the gaseous phase outlet of first gas-liquid separator 5, and the liquid phase outlet of second gas-liquid separator 13 is connected with the driving fluid import of first throttle element 1, evaporimeter 2, low-pressure stage injector 3 successively.
(solid line is the circulation route that is rich in low boiling working fluid on the figure through this embodiment; Dotted line is the circulation route that is rich in higher boiling working medium); Being rich in of hiigh pressure stage condenser 7 outlets gets into second gas-liquid separator 13 after low boiling working fluid liquid is throttled to intermediate pressure by second restricting element 12; The low boiling working fluid gas that is rich in second gas-liquid separator 13 is got into evaporimeter 2 evaporation heat absorptions through first throttle element 1 back and obtains refrigerating capacitys by the hiigh pressure stage injector 6 injections low boiling working fluid liquid that is rich in that gets in hiigh pressure stage condenser 7, the second gas-liquid separators 13 that boosts.Since under the intermediate pressure can not throttling refrigeration the low boiling working fluid gas that is rich in walked by hiigh pressure stage injector 6 injections, reduced the flow and the load of low-pressure stage injector 3, have the effect that improves the entire system performance better so compare embodiment 1.Above-mentioned second gas-liquid separator 13 can select to adopt the version of rectifier
As shown in Figure 3, Fig. 3 is the flow chart of another embodiment of the utility model.Mixed working fluid two-stage ejector type refrigerating machine shown in Figure 3 comprises first throttle element 1, evaporimeter 2, low-pressure stage injector 3, low-pressure stage condenser 4, first gas-liquid separator 5, hiigh pressure stage injector 6, hiigh pressure stage condenser 7, low-pressure stage pump 8, low-pressure stage generator 9, hiigh pressure stage pump 10, hiigh pressure stage generator 11, second restricting element 12, second gas-liquid separator 13, low-pressure stage regenerator 14 and hiigh pressure stage regenerator 15; Wherein, Low-pressure stage regenerator 14 has two heat exchange pipes of isolating each other; Wherein a heat exchange pipe is the connecting line between low-pressure stage injector 3 and the low-pressure stage condenser 4, and another heat exchange pipe is the connecting line between low-pressure stage pump 8 and the low-pressure stage generator 9.Hiigh pressure stage regenerator 15 has two heat exchange pipes of isolating each other; Wherein a heat exchange pipe is the connecting line between hiigh pressure stage injector 6 and the hiigh pressure stage condenser 7, and another heat exchange pipe is the connecting line between hiigh pressure stage pump 10 and the hiigh pressure stage generator 11.Connect the successively working fluid import of liquid phase outlet, low-pressure stage pump 8, low-pressure stage generator 9 and low-pressure stage injector 3 of import, first gas-liquid separator 5 of the first outlet 1b, low-pressure stage condenser 4, first gas-liquid separator 5 of the first import 1a, low-pressure stage regenerator 14 of low-pressure stage regenerator 14 of the outlet of low-pressure stage injector 3; The gaseous phase outlet of first gas-liquid separator 5 is connected with the driving fluid import of hiigh pressure stage injector 6, the outlet of hiigh pressure stage injector 6, the first import 3a of hiigh pressure stage regenerator 15, the first outlet 3b of hiigh pressure stage regenerator 15, the import of hiigh pressure stage condenser 7 successively; The outlet of hiigh pressure stage condenser 7 is divided into two-way; The working fluid import of the second outlet 4b of the second import 4a of the first via and hiigh pressure stage pump 10, hiigh pressure stage regenerator 15, hiigh pressure stage regenerator 15, hiigh pressure stage generator 11, hiigh pressure stage injector 6 is connected successively; The second the tunnel links to each other with the import of second restricting element 12, the outlet of second restricting element 12, the import of second gas-liquid separator 13 successively; The gaseous phase outlet of second gas-liquid separator 13 is linked to be the driving fluid import that is connected hiigh pressure stage injector 6 after a tunnel with the gaseous phase outlet of first gas-liquid separator 5, and the liquid phase outlet of second gas-liquid separator 13 is connected with the driving fluid import of first throttle element 1, evaporimeter 2, low-pressure stage injector 3 successively.
(solid line is the circulation route that is rich in low boiling working fluid on the figure through this embodiment; Dotted line is the circulation route that is rich in higher boiling working medium); The fluid working substance (comprising the fluid-mixing that is rich in higher boiling working medium and is rich in low boiling working fluid) of low-pressure stage injector capable of using 3 outlets preheats that low-pressure stage pump 8 exports is rich in higher boiling working medium; Utilize the low boiling working fluid that is rich in that low boiling working fluid preheats 10 outlets of hiigh pressure stage pump that is rich in of hiigh pressure stage injector 6 outlets; Thereby can reduce the heat that adds of hiigh pressure stage generator 11 and low-pressure stage generator 9, play the effect that improves the entire system performance.
Application examples
Referring to Fig. 4; Fig. 4 is an a kind of existing single-stage spray type refrigerating system, comprises first throttle element 1, evaporimeter 2, solution pump 19, generator 16, condenser 17 and injector 18, wherein; The outlet of evaporimeter 2 connects the driving fluid import of injector 18; The outlet of injector 18 connects the import of condenser 17, and the outlet of condenser 17 is divided into two-way, wherein one the tunnel connect solution pump 19, generator 16 and injector 18 successively the working fluid import; Another road connect successively first throttle element 1 and evaporimeter 2.
Referring to Fig. 5; Fig. 5 is an a kind of existing two-stage spray type refrigerating system; Comprise first throttle element 1, evaporimeter 2, low-pressure stage injector 21, hiigh pressure stage injector 20, condenser 17, solution pump 19 and generator 16; Wherein, The outlet of evaporimeter 2 connect successively the driving fluid import of low-pressure stage injector 21, the outlet of low-pressure stage injector 21, the driving fluid import of hiigh pressure stage injector 20, the outlet of hiigh pressure stage injector 20, the import of condenser 17 and the outlet of condenser 17, the outlet of condenser 17 is divided into two-way, wherein one tunnel connect successively solution pump 19 and generator 16; The outlet of generator 16 is divided into two strands, connects the working fluid import of hiigh pressure stage injector 20 and the working fluid import of low-pressure stage injector 21 respectively; Another road of condenser 17 outlet connect successively first throttle element 1 and evaporimeter 2.In this refrigeration system, low-pressure stage injector 21 is injected into intermediate pressure with fluid working substance, and said here intermediate pressure is a certain pressure between evaporating pressure and condensing pressure.
Following comparative example's 2 refrigeration machines, Fig. 4 and system shown in Figure 5 are carried out analog computation; Wherein embodiment 2 refrigeration machines with R245fa as higher boiling working medium; R600a is as low boiling working fluid; Single-stage injection refrigerating system shown in Figure 4 and two-stage spray type refrigerating shown in Figure 5 system are working medium with R245fa or R600a all, and the assumed condition of calculating is following: (1) system is in steady-working state; (2) pressure drop of ignoring pipeline with leak heat; (3) for present embodiment 2 refrigeration machines, the first gas-liquid separator exit gas is approximate pure R600a, and outlet liquid is approximate pure R245fa; (4) (for Fig. 4, system shown in Figure 5 evaporating temperature is the evaporating temperature of working medium in the evaporimeter to evaporating temperature; For embodiment 2 refrigeration machines; Evaporating temperature is the dew-point temperature of working medium in the evaporimeter) be 5 ℃, hiigh pressure stage generator and low-pressure stage generator occurrence temperature are 100 ℃; (5) for two-stage spray type refrigerating shown in Figure 5 system, intermediate pressure is the saturation pressure under the mean temperature of evaporating temperature and condensation temperature; (6) the low-pressure stage condenser is identical with the condensation temperature of hiigh pressure stage condenser.
Table 1 embodiment 2 refrigeration machines and Fig. 4, the performance comparison of Fig. 5 refrigeration system under different condensation temperatures
T in the table 1
cRefer to that (for Fig. 4, system shown in Figure 5, condensation temperature is the adiabatic condensation temperature of condenser 17 inner refrigerants to condensation temperature; For the refrigeration machine of embodiment 2, condensation temperature is the dew-point temperature of the inner refrigerant of hiigh pressure stage condenser or low-pressure stage condenser), COP
CjrThe coefficient of performance that refers to embodiment 2 refrigeration machines, COP
245Finger is with the coefficient of performance of R245fa as the single-stage spray type refrigerating system of working medium, η
245Refer to the increase rate of the relative R245fa of embodiment 2 refrigeration machines as the coefficient of performance of the single-stage spray type refrigerating system of working medium; COP
600Finger is with the coefficient of performance of R600a as the single-stage spray type refrigerating system of working medium, η
600Refer to the increase rate of the relative R600a of embodiment 2 refrigeration machines as the coefficient of performance of the single-stage spray type refrigerating system of working medium; COP '
245Finger is with the coefficient of performance of R245fa as the two-stage spray type refrigerating system of working medium, η '
245Refer to the increase rate of the relative R245fa of embodiment 2 refrigeration machines as the coefficient of performance of the two-stage spray type refrigerating system of working medium; COP '
600Finger is with the coefficient of performance of R600a as the two-stage spray type refrigerating system of working medium, η '
600Refer to the increase rate of the relative R600a of embodiment 2 refrigeration machines as the coefficient of performance of the two-stage spray type refrigerating system of working medium.
Can find out that from table 1 coefficient of performance of embodiment 2 refrigeration machines all significantly is higher than other spray type refrigerating system under the overwhelming majority's design condition.Especially when condensation temperature was higher than 50 ℃, other spray type refrigerating systematic function coefficient was extremely low, almost can not work, and embodiment 2 refrigeration machines still can be under the coefficient of performance about 0.1 reliability service.So can find out the advantage of the aforementioned relatively two kinds of existing spray type refrigerating systems of embodiment 2 refrigeration machines.
Claims (8)
1. mixed working fluid two-stage ejector type refrigerating machine; Comprise low-pressure stage injector (3) and hiigh pressure stage injector (6); Be connected with first loop between the working fluid import of the outlet of said hiigh pressure stage injector (6) and hiigh pressure stage injector (6), first loop comprises hiigh pressure stage condenser (7), hiigh pressure stage pump (10) and the hiigh pressure stage generator (11) of connecting successively with the outlet of hiigh pressure stage injector (6); Be connected with second loop between the driving fluid import of the outlet of said hiigh pressure stage injector (6) and said low-pressure stage injector (3); Second loop comprises hiigh pressure stage condenser (7), first throttle element (1) and the evaporimeter (2) of connecting successively with the outlet of hiigh pressure stage injector (6); It is characterized in that: comprise that the fluid working substance with the outlet of low-pressure stage injector (3) is converted into the low-pressure stage condenser (4) of gas-liquid mixture; Be used for said gas-liquid mixture is separated into first gas-liquid separator (5) of two phases; The gaseous phase outlet of first gas-liquid separator (5) links to each other with the driving fluid import of hiigh pressure stage injector (6), and the liquid phase of first gas-liquid separator (5) exports the working fluid import of connect successively low-pressure stage pump (8), low-pressure stage generator (9) and low-pressure stage injector (3).
2. mixed working fluid two-stage ejector type refrigerating machine according to claim 1; It is characterized in that: said second loop comprises that the fluid working substance that hiigh pressure stage condenser (7) is come out is divided into second restricting element (12) of gas-liquid mixture and said gas-liquid mixture is separated into two mutually second gas-liquid separators (13), and the gaseous phase outlet of second gas-liquid separator (13) is linked to be the driving fluid import that is connected described hiigh pressure stage injector (6) after a tunnel with the gaseous phase outlet of said first gas-liquid separator (5); The liquid phase outlet of second gas-liquid separator (13) is connected with said first throttle element (1).
3. mixed working fluid two-stage ejector type refrigerating machine according to claim 1 and 2; It is characterized in that: comprise low-pressure stage regenerator (14); Low-pressure stage regenerator (14) has two heat exchange pipes of isolating each other; Wherein a heat exchange pipe is the connecting line between low-pressure stage injector (3) and the low-pressure stage condenser (4), and another heat exchange pipe is the connecting line between low-pressure stage pump (8) and the low-pressure stage generator (9).
4. mixed working fluid two-stage ejector type refrigerating machine according to claim 1 and 2; It is characterized in that: comprise hiigh pressure stage regenerator (15); Hiigh pressure stage regenerator (15) has two heat exchange pipes of isolating each other; Wherein a heat exchange pipe is the connecting line between hiigh pressure stage injector (6) and the hiigh pressure stage condenser (7), and another heat exchange pipe is the connecting line between hiigh pressure stage pump (10) and the hiigh pressure stage generator (11).
5. mixed working fluid two-stage ejector type refrigerating machine according to claim 3; It is characterized in that: comprise hiigh pressure stage regenerator (15); Hiigh pressure stage regenerator (15) has two heat exchange pipes of isolating each other; Wherein a heat exchange pipe is the connecting line between hiigh pressure stage injector (6) and the hiigh pressure stage condenser (7), and another heat exchange pipe is the connecting line between hiigh pressure stage pump (10) and the hiigh pressure stage generator (11).
6. mixed working fluid two-stage ejector type refrigerating machine according to claim 3 is characterized in that: said first gas-liquid separator (5), second gas-liquid separator (13) adopt the version of rectifier.
7. mixed working fluid two-stage ejector type refrigerating machine according to claim 4 is characterized in that: said first gas-liquid separator (5), second gas-liquid separator (13) adopt the version of rectifier
8. mixed working fluid two-stage ejector type refrigerating machine according to claim 5 is characterized in that: said first gas-liquid separator (5), second gas-liquid separator (13) adopt the version of rectifier.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012201684071U CN202547181U (en) | 2012-04-19 | 2012-04-19 | Two-stage refrigerant mixture injection type refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012201684071U CN202547181U (en) | 2012-04-19 | 2012-04-19 | Two-stage refrigerant mixture injection type refrigerator |
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| CN202547181U true CN202547181U (en) | 2012-11-21 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2012201684071U Expired - Lifetime CN202547181U (en) | 2012-04-19 | 2012-04-19 | Two-stage refrigerant mixture injection type refrigerator |
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| CN (1) | CN202547181U (en) |
Cited By (2)
| 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 |
| CN111397234A (en) * | 2020-03-05 | 2020-07-10 | 浙江大学 | Low-grade heat-driven mixed working medium refrigerating system |
-
2012
- 2012-04-19 CN CN2012201684071U patent/CN202547181U/en not_active Expired - Lifetime
Cited By (4)
| 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 |
| CN111397234A (en) * | 2020-03-05 | 2020-07-10 | 浙江大学 | Low-grade heat-driven mixed working medium refrigerating system |
| CN111397234B (en) * | 2020-03-05 | 2021-07-20 | 浙江大学 | Low-grade heat-driven mixed working medium refrigerating system |
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