CN102853578B - Mixed working medium two-stage jet type refrigerating machine - Google Patents
Mixed working medium two-stage jet type refrigerating machine Download PDFInfo
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Abstract
The invention discloses a mixed working medium two-stage jet type refrigerating machine which comprises a throttling element, an evaporator, two ejectors, two condensers, two pumps and two generators. The mixed working medium two-stage jet type refrigerating machine further comprises a low pressure stage condenser for converting a fluid working medium at an outlet of a low pressure stage ejector into gas-liquid mixture and a first gas-liquid separator for separating the gas-liquid mixture into two phases, an air-phase outlet of the first gas-liquid separator is connected with an ejection fluid inlet of a high pressure stage ejector, and a liquid-phase outlet of the first gas-liquid separator is connected with working fluid inlets of a low pressure stage pump, a low pressure stage generator and the low pressure stage ejector sequentially in series. The mixed working medium is utilized, part of a middle pressure working medium at the outlet of the lower pressure stage ejector is congealed and pumped in the low pressure stage generator, load of the high pressure stage ejector is reduced, an integral performance effect of a system is improved, and the mixed working medium two-stage jet type refrigerating machine is good in application prospect.
Description
Technical field
The invention belongs to refrigeration technology field, especially relate to a kind of mixed working fluid two-stage ejector type refrigerating machine.
Background technology
Injector in 1910 first for refrigeration, and be widely used in the air-conditioning refrigeration system of building the thirties in 20th century, but higher by efficiency subsequently, the compacter mechanical compression type refrigeration of equipment replaces, and the after this research work of injector 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 concern again.
Spray type refrigerating technology is a kind of Refrigeration Technique of heat-driven, comparing its major advantage with mechanical compression type Refrigeration Technique is only need to consume little mechanical energy, can directly utilize heat energy as drive energy, have that device structure is simple, volume is little, cost is low, an advantage such as reliable, long service life.
Chinese invention patent ZL200610104934.9, " a kind of self-overlapping refrigerating cycle system with injector " discloses the self-overlapping refrigerating cycle system with injector, comprise the connected compressor of pipeline, condenser, gas-liquid separator, evaporative condenser, evaporimeter and expansion valve, between evaporative condenser and evaporimeter, also have injector.Injector supercharging can improve suction pressure of compressor, reduces pressure ratio, reduces work done during compression.But in the time that the condensation temperature of ejector refrigeration system is higher, single-stage spray type refrigerating is difficult to provide the pressure reduction of condenser and evaporimeter in system.
Although the disclosed refrigeration system of the two-stage steam jet refrigeration system that publication number is CN101832680A is to set up an injector in traditional single-stage injection refrigerating system, pressurization with performance injector to refrigerant vapour, to improve coefficient of refrigerating performance, easily make the load of injector increase but add an injector.And for example Chinese invention patent ZL200910304106.X, " 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 gas ejector outlet is connected with the import of condensation injector injection, although the series connection by two-stage ejector (being divided into hiigh pressure stage and low-pressure stage) can provide larger pressure reduction, but because the flow of hiigh pressure stage is larger, the Energy Efficiency Ratio of system is still very low.
Summary of the invention
The present invention is directed to deficiency and the defect of existing ejector refrigeration system, proposed a kind of mixed working fluid two-stage ejector type refrigerating machine, by reduce the flow of hiigh pressure stage injector and low-pressure stage injector and load and improve the performance of system simultaneously.
A kind of mixed working fluid two-stage ejector type refrigerating machine, comprise low-pressure stage injector and hiigh pressure stage injector, between the working fluid import of the outlet of described hiigh pressure stage injector and hiigh pressure stage injector, be connected with the first loop, the 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; Between the driving fluid import of the outlet of described hiigh pressure stage injector and described low-pressure stage injector, be connected with second servo loop, second servo loop comprises hiigh pressure stage condenser, first throttle element and the evaporimeter of connecting successively with the outlet of hiigh pressure stage injector; Comprise the low-pressure stage condenser that the fluid working substance of the outlet of low-pressure stage injector is converted into gas-liquid mixture, for described gas-liquid mixture being separated into the first gas-liquid separator of two-phase, the gaseous phase outlet of the first gas-liquid separator is connected with the driving fluid import of hiigh pressure stage injector, connect the successively working fluid import of low-pressure stage pump, low-pressure stage generator and low-pressure stage injector of the liquid-phase outlet of the first gas-liquid separator.
In the present invention, the fluid working substance of filling in ejector type refrigerating machine is the zeotrope that two or more working medium mixes, wherein be rich in the saturation pressure of higher boiling working medium under the condensation temperature of low-pressure stage condenser and be greater than and be rich in the saturation pressure of low boiling working fluid under evaporating temperature, be rich in the saturation pressure of low boiling working fluid under the condensation temperature of hiigh pressure stage condenser and be greater than and be rich in the saturation pressure of higher boiling working medium under the condensation temperature of low-pressure stage condenser.The pure working medium of fluid of selecting can be various pure cold-producing mediums, as using R245fa as higher boiling working medium, using R600a as low boiling working fluid.
In the present invention, described intermediate pressure is a certain pressure between evaporating pressure and hiigh pressure stage condensing pressure.
In the present invention, described evaporating temperature, for mixed working fluid, refers to the dew-point temperature of evaporimeter inner refrigerant; For pure refrigerants, refer to the gasification temperature of evaporimeter inner refrigerant.
In the present invention, described condensation temperature, for mixed working fluid, refers to the dew-point temperature of condenser inner refrigerant; For pure refrigerants, refer to the adiabatic condensation temperature of condenser inner refrigerant.
Workflow of the present invention is: after the fluid that is rich in higher boiling working medium absorbs heat in low-pressure stage generator, become gases at high pressure, the fluid that is rich in higher boiling working medium of low-pressure stage generator exports enters the fluid that is rich in low boiling working fluid in low-pressure stage injector injection evaporimeter as working fluid, the fluid that is rich in low boiling working fluid is boosted to intermediate pressure (referred to as middle pressure) by injection, and after mixing with the fluid that is rich in higher boiling working medium in low-pressure stage injector through the heat release of low-pressure stage condenser condenses, fluid-mixing, by partial liquefaction, enters the first gas-liquid separator.The liquid that is rich in higher boiling working medium in the first gas-liquid separator enters low-pressure stage generator by low-pressure stage pump pressurization, and the gas that is rich in low boiling working fluid in the first gas-liquid separator is boosted and passes into the heat release of hiigh pressure stage condenser condenses and become liquid by the fluid injection that is rich in low boiling working fluid of hiigh pressure stage generator exports high pressure.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 is absorbed heat and become gases at high pressure in hiigh pressure stage generator by hiigh pressure stage pump; Another stock-traders' know-how enters evaporator evaporation heat absorption acquisition refrigerating capacity after crossing first throttle element.System completes one action process.The fluid condensation of being rich in higher boiling working medium quilt due to the middle pressure of low-pressure stage injector outlet gets off directly to pump into low-pressure stage generator, reduces flow and the load of hiigh pressure stage injector, thereby plays the effect of the effect that improves entire system performance.
Described high pressure generator and low pressure generator can be by solar energy, motor exhaust, and fuel combustion heat, the external heat sources such as electric current Joule heat drive.
Low-pressure stage condenser and hiigh pressure stage condenser are cooling 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 depending on selected fluid working substance and the operating mode setting.
Described first throttle element, second section fluid element can be selected U-shaped pipe, capillary, the versions such as choke valve.
As preferably, described second servo loop comprises the second gas-liquid separator that hiigh pressure stage condenser fluid working substance is out divided into the second section fluid element of gas-liquid mixture and described gas-liquid mixture is separated into two-phase, and the gaseous phase outlet of the second gas-liquid separator is connected the driving fluid import of described hiigh pressure stage injector after being linked to be a road with the gaseous phase outlet of described the first gas-liquid separator; The liquid-phase outlet of the second gas-liquid separator is connected with described first throttle element.
Adopt after above-mentioned preferred version, the liquid that is rich in low boiling working fluid of hiigh pressure stage condensator outlet enters the second gas-liquid separator after being throttled to intermediate pressure by second section fluid element, the gas that is rich in low boiling working fluid in the second gas-liquid separator is boosted and enters hiigh pressure stage condenser by hiigh pressure stage injector injection, and the liquid that is rich in low boiling working fluid in the second gas-liquid separator enters evaporator evaporation heat absorption and obtains refrigerating capacity after first throttle element.Due under intermediate pressure can not throttling refrigeration the gas that is rich in low boiling working fluid walked by hiigh pressure stage injector injection, reduced flow and the load of low-pressure stage injector, play the effect that improves entire system performance.
More preferred, the present invention includes low-pressure stage regenerator, low-pressure stage regenerator is with two heat exchange pipes of mutually isolating, wherein a heat exchange pipe is the connecting line between low-pressure stage injector and low-pressure stage condenser, and another heat exchange pipe is the connecting line between low-pressure stage pump and low-pressure stage generator.Further, the present invention also can comprise hiigh pressure stage regenerator, hiigh pressure stage regenerator is with two heat exchange pipes of mutually isolating, wherein a heat exchange pipe is the connecting line between hiigh pressure stage injector and hiigh pressure stage condenser, and another heat exchange pipe is the connecting line between hiigh pressure stage pump and hiigh pressure stage generator.
Adopt after above-mentioned preferred version, utilize the fluid working substance of low-pressure stage injector outlet to preheat 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 is rich in low boiling working fluid and preheats hiigh pressure stage pump discharge 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 entire system performance.
As preferably, the first described gas-liquid separator, the version that the second gas-liquid separator adopts rectifier, realize the good separation that is rich in higher boiling working medium and is rich in low boiling working fluid.
The present invention has following beneficial effect:
1. the present invention drives by hiigh pressure stage generator and two thermals source of low-pressure stage generator, without the compressor that utilizes common refrigeration system to use;
2. the gas of gas-liquid separator outlet is different with the flow direction of liquid working substance, in circulation, role is also different, in the present invention, the first gas-liquid separator gas out flows into hiigh pressure stage injector, liquid flows into solution pump (being low-pressure stage pump), improve to reduce the load (reducing the flow of hiigh pressure stage injector) of hiigh pressure stage injector by this, reduce the generation heat of hiigh pressure stage generator, thereby improve system effectiveness.
In sum, compare single-stage ejector refrigeration system, the present invention is owing to adopting two-stage ejector, can adopt one identical or adopt the thermal source of two different temperatures, larger condensing pressure and evaporating pressure pressure reduction can also be provided in addition, can under higher condensation temperature, move; Compare two-stage ejector refrigeration system, the non-azeotropic mixed working medium that utilization of the present invention 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 low-pressure stage generator, reduce the load of hiigh pressure stage injector; Second section fluid element outlet can not be used for the middle pressure Working medium gas of throttling refrigeration by hiigh pressure stage injector injection, reduce the load of low-pressure stage injector, thereby play the effect that improves entire system performance, therefore the present invention can greatly raise the efficiency under identical operating mode.The present invention can be used for improving the performance of various existing ejector refrigeration systems in addition.
Brief description of the drawings
Fig. 1 is the flow chart of one embodiment of the present invention.
Fig. 2 is the flow chart of another embodiment of the present invention.
Fig. 3 is the flow chart of another embodiment of the present invention.
Fig. 4 is the flow chart of existing single-stage ejector refrigeration system.
Fig. 5 is the flow chart of existing two-stage ejector refrigeration system.
Wherein: 1, first throttle element; 2, evaporimeter; 3, low-pressure stage injector; 4, low-pressure stage condenser; 5, the 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 section fluid element; 13, the 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, the first import; 1b, the first outlet; 2a, the second import; 2b, the second outlet; 3a, the first import; 3b, the first outlet; 4a, the second import; 4b, the second outlet.
Detailed description of the invention
Referring to the drawings and specific embodiments, the present invention is described in further detail.
As shown in Figure 1, Fig. 1 is the flow chart of one embodiment of the present invention, the two-stage of mixed working fluid shown in Fig. 1 ejector type refrigerating machine comprises first throttle element 1, evaporimeter 2, low-pressure stage injector 3, low-pressure stage condenser 4, the 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 low-pressure stage condenser 4 of connecting successively, the import of the first gas-liquid separator 5, the liquid-phase outlet of the first gas-liquid separator 5, low-pressure stage pump 8, the working fluid import of low-pressure stage generator 9 and low-pressure stage injector 3, the gaseous phase outlet of the first gas-liquid separator 5 connect successively the driving fluid import of hiigh pressure stage injector 6, 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 successively with the working fluid import of hiigh pressure stage pump 10, hiigh pressure stage generator 11, hiigh pressure stage injector 6, and the second tunnel is connected successively with the driving fluid import of first throttle element 1, evaporimeter 2, low-pressure stage injector 3.
In figure, solid line is the circulation route that is rich in low boiling working fluid, and dotted line is the circulation route that is rich in higher boiling working medium.Be rich in after higher boiling working medium is absorbed heat in low-pressure stage generator 9 and become gases at high pressure, what low-pressure stage generator 9 exported be rich in higher boiling working medium enters the low boiling working fluid that is rich in 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, being rich in higher boiling working medium is liquefied completely, be still gaseous state and be rich in low boiling working fluid, enter the first gas-liquid separator 5.The low boiling working fluid injection that is rich in that low boiling working fluid gas exported high pressure by hiigh pressure stage generator 11 that is rich in that higher boiling worker quality liquid enters in low-pressure stage generator 9, the first gas-liquid separators 5 by low-pressure stage pump 8 pressurization that is rich in the first gas-liquid separator 5 boosts and passes into the 7 condensation heat releases of hiigh pressure stage condenser and become liquid.What hiigh pressure stage condenser 7 exported be rich in low boiling working fluid liquid is divided into two strands, and wherein one is absorbed heat and become gases at high pressure in hiigh pressure stage generator 11 by hiigh pressure stage pump 10; Another stock-traders' know-how enters evaporimeter 2 evaporation endothermics acquisition refrigerating capacitys after crossing first throttle element 1.System completes one action process.The middle pressure exporting due to low-pressure stage injector 3 is rich in higher boiling working medium and is condensed and directly pumps into low-pressure stage generator 9, reduces flow and the load of hiigh pressure stage injector 6, thereby plays the effect that improves entire system performance.Above-mentioned the first gas-liquid separator 5 can select to adopt the version of rectifier.
As shown in Figure 2, the flow chart that Fig. 2 is another embodiment of the present invention.The two-stage of mixed working fluid shown in Fig. 2 ejector type refrigerating machine comprises first throttle element 1, evaporimeter 2, low-pressure stage injector 3, low-pressure stage condenser 4, the 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 section fluid element 12 and the second gas-liquid separator 13, wherein, the outlet of the low-pressure stage injector 3 low-pressure stage condenser 4 of connecting successively, the import of the first gas-liquid separator 5, the liquid-phase outlet of the first gas-liquid separator 5, low-pressure stage pump 8, the working fluid import of low-pressure stage generator 9 and low-pressure stage injector 3, connect the successively driving fluid import of hiigh pressure stage injector 6 of the gaseous phase outlet of the first gas-liquid separator 5, the import of the outlet of hiigh pressure stage injector 6 and 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 and hiigh pressure stage pump 10, hiigh pressure stage generator 11, the working fluid import of hiigh pressure stage injector 6 is connected successively, the second tunnel is connected with the import of the second gas-liquid separator 13, the gaseous phase outlet of the second gas-liquid separator 13 is connected the driving fluid import of hiigh pressure stage injector 6 after being linked to be a road with the gaseous phase outlet of the first gas-liquid separator 5, the liquid-phase outlet of the second gas-liquid separator 13 and first throttle element 1, evaporimeter 2, the driving fluid import of low-pressure stage injector 3 is connected successively.
By present embodiment, (on figure, solid line is the circulation route that is rich in low boiling working fluid, dotted line is the circulation route that is rich in higher boiling working medium), what hiigh pressure stage condenser 7 exported be rich in after low boiling working fluid liquid is throttled to intermediate pressure by second section fluid element 12 enters the second gas-liquid separator 13, in the second gas-liquid separator 13 be rich in low boiling working fluid gas by hiigh pressure stage injector 6 injections boost enter in hiigh pressure stage condenser 7, the second gas-liquid separators 13 be rich in low boiling working fluid liquid after first throttle element 1, enter evaporimeter 2 evaporation endothermics obtain refrigerating capacitys.Due under 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 flow and the load of low-pressure stage injector 3, there is therefore compare embodiment 1 effect that improves better entire system performance.Above-mentioned the 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 present invention.The two-stage of mixed working fluid shown in Fig. 3 ejector type refrigerating machine comprises first throttle element 1, evaporimeter 2, low-pressure stage injector 3, low-pressure stage condenser 4, the 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 section fluid element 12, the second gas-liquid separator 13, low-pressure stage regenerator 14 and hiigh pressure stage regenerator 15, wherein, low-pressure stage regenerator 14 is with two heat exchange pipes of mutually isolating, wherein a heat exchange pipe is the connecting line between low-pressure stage injector 3 and low-pressure stage condenser 4, another heat exchange pipe is the connecting line between low-pressure stage pump 8 and low-pressure stage generator 9.Hiigh pressure stage regenerator 15 is with two heat exchange pipes of mutually isolating, wherein a heat exchange pipe is the connecting line between hiigh pressure stage injector 6 and hiigh pressure stage condenser 7, and another heat exchange pipe is the connecting line between hiigh pressure stage pump 10 and 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, the first gas-liquid separator 5 of the first outlet 1b, low-pressure stage condenser 4, the 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 driving fluid import of the gaseous phase outlet of the first gas-liquid separator 5 and 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 is connected successively, the outlet of hiigh pressure stage condenser 7 is divided into two-way, the first via and hiigh pressure stage pump 10, the second import 4a of hiigh pressure stage regenerator 15, the second outlet 4b of hiigh pressure stage regenerator 15, hiigh pressure stage generator 11, the working fluid import of hiigh pressure stage injector 6 is connected successively, the second tunnel successively with the import of second section fluid element 12, the outlet of second section fluid element 12, the import of the second gas-liquid separator 13 is connected, the gaseous phase outlet of the second gas-liquid separator 13 is connected the driving fluid import of hiigh pressure stage injector 6 after being linked to be a road with the gaseous phase outlet of the first gas-liquid separator 5, the liquid-phase outlet of the second gas-liquid separator 13 and first throttle element 1, evaporimeter 2, the driving fluid import of low-pressure stage injector 3 is connected successively.
By present embodiment, (on figure, solid line is the circulation route that is rich in low boiling working fluid, dotted line is the circulation route that is rich in higher boiling working medium), that can utilize that fluid working substance (comprising the fluid-mixing that is rich in higher boiling working medium and be rich in low boiling working fluid) that low-pressure stage injector 3 exports preheats that low-pressure stage pump 8 exports is rich in higher boiling working medium, the low boiling working fluid that is rich in that utilizes that hiigh pressure stage injector 6 exports preheats the low boiling working fluid that is rich in that hiigh pressure stage pump 10 exports, thereby can reduce the heat that adds of hiigh pressure stage generator 11 and low-pressure stage generator 9, play the effect that improves entire system performance.
Application examples
Referring to Fig. 4, Fig. 4 is a kind of existing single-stage ejector refrigeration system, comprise 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, the wherein road working fluid import of solution pump 19, generator 16 and injector 18 of connecting successively; Another road connect successively first throttle element 1 and evaporimeter 2.
Referring to Fig. 5, Fig. 5 is a kind of existing two-stage ejector refrigeration 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, connect the successively driving fluid import of low-pressure stage injector 21 of the outlet of evaporimeter 2, 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 outlet of the import of condenser 17 and condenser 17, the outlet of condenser 17 is divided into two-way, wherein connect successively solution pump 19 and generator 16 of a road, the outlet of generator 16 is divided into two strands, connect respectively the working fluid import of hiigh pressure stage injector 20 and the working fluid import of low-pressure stage injector 21, another road that condenser 17 exports connect successively first throttle element 1 and evaporimeter 2.In this refrigeration system, fluid working substance is injected into intermediate pressure by low-pressure stage injector 21, and said intermediate pressure is a certain pressure between evaporating pressure and condensing pressure herein.
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 are using R245fa as higher boiling working medium, R600a is as low boiling working fluid, two-stage ejector refrigeration system shown in the injection refrigerating system of single-stage shown in Fig. 4 and Fig. 5 is all taking R245fa or R600a as working medium, and the assumed condition of calculating is as follows: (1) system is in steady-working state; (2) ignore the pressure drop of pipeline and leak heat; (3) for the present embodiment 2 refrigeration machines, the first gas-liquid separator exit gas is approximate pure R600a, and outlet liquid is approximate pure R245fa; (4) evaporating temperature (is the evaporating temperature of working medium in evaporimeter for Fig. 4, system shown in Figure 5 evaporating temperature, for embodiment 2 refrigeration machines, evaporating temperature is the dew-point temperature of working medium in evaporimeter) be 5 DEG C, hiigh pressure stage generator and low-pressure stage generator occurrence temperature are 100 DEG C; (5), for the ejector refrigeration system of two-stage shown in Fig. 5, intermediate pressure is the saturation pressure under the mean temperature of evaporating temperature and condensation temperature; (6) 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 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
cjrrefer to the coefficient of performance of embodiment 2 refrigeration machines, COP
245refer to the coefficient of performance of the single-stage ejector refrigeration system using R245fa as working medium, η
245refer to the increase rate of the relative R245fa of embodiment 2 refrigeration machine as the coefficient of performance of the single-stage ejector refrigeration system of working medium; COP
600refer to the coefficient of performance of the single-stage ejector refrigeration system using R600a as working medium, η
600refer to the increase rate of the relative R600a of embodiment 2 refrigeration machine as the coefficient of performance of the single-stage ejector refrigeration system of working medium; COP '
245refer to the coefficient of performance of the two-stage ejector refrigeration system using R245fa as working medium, η '
245refer to the increase rate of the relative R245fa of embodiment 2 refrigeration machine as the coefficient of performance of the two-stage ejector refrigeration system of working medium; COP '
600refer to the coefficient of performance of the two-stage ejector refrigeration system using R600a as working medium, η '
600refer to the increase rate of the relative R600a of embodiment 2 refrigeration machine as the coefficient of performance of the two-stage ejector refrigeration system of working medium.
As can be seen from Table 1, the coefficient of performance of embodiment 2 refrigeration machines under most design conditions all significantly higher than other ejector refrigeration system.Especially when condensation temperature is during higher than 50 DEG C, other the ejector refrigeration system coefficient of performance is extremely low, almost can not work, and embodiment 2 refrigeration machines still can be under the coefficient of performance of 0.1 left and right reliability service.So can find out the advantage of the relatively aforementioned two kinds of existing ejector refrigeration systems of embodiment 2 refrigeration machines.
Claims (8)
1. a mixed working fluid two-stage ejector type refrigerating machine, comprise low-pressure stage injector (3) and hiigh pressure stage injector (6), between the working fluid import of the outlet of described hiigh pressure stage injector (6) and hiigh pressure stage injector (6), be connected with the first loop, the 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), between the driving fluid import of the outlet of described hiigh pressure stage injector (6) and described low-pressure stage injector (3), be connected with second servo loop, second servo loop comprises the hiigh pressure stage condenser (7) of connecting successively with the outlet of hiigh pressure stage injector (6), first throttle element (1) and evaporimeter (2), it is characterized in that: comprise the low-pressure stage condenser (4) that the fluid working substance of the outlet of low-pressure stage injector (3) is converted into gas-liquid mixture, for described gas-liquid mixture being separated into first gas-liquid separator (5) of two-phase, the gaseous phase outlet of the first gas-liquid separator (5) is connected with the driving fluid import of hiigh pressure stage injector (6), the liquid-phase outlet of the first gas-liquid separator (5) the low-pressure stage pump (8) of connecting successively, the working fluid import of 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: described second servo loop comprises the second gas-liquid separator (13) that hiigh pressure stage condenser (7) fluid working substance is out divided into the second section fluid element (12) of gas-liquid mixture and described gas-liquid mixture is separated into two-phase, the gaseous phase outlet of the second gas-liquid separator (13) is connected the driving fluid import of described hiigh pressure stage injector (6) after being linked to be a road with the gaseous phase outlet of described the first gas-liquid separator (5); The liquid-phase outlet of the second gas-liquid separator (13) is connected with described first throttle element (1).
3. mixed working fluid two-stage ejector type refrigerating machine according to claim 2, it is characterized in that: comprise low-pressure stage regenerator (14), low-pressure stage regenerator (14) is with two heat exchange pipes of mutually isolating, wherein a heat exchange pipe is the connecting line between low-pressure stage injector (3) and low-pressure stage condenser (4), and another heat exchange pipe is the connecting line between low-pressure stage pump (8) and low-pressure stage generator (9).
4. mixed working fluid two-stage ejector type refrigerating machine according to claim 2, it is characterized in that: comprise hiigh pressure stage regenerator (15), hiigh pressure stage regenerator (15) is with two heat exchange pipes of mutually isolating, wherein a heat exchange pipe is the connecting line between hiigh pressure stage injector (6) and hiigh pressure stage condenser (7), and another heat exchange pipe is the connecting line between hiigh pressure stage pump (10) and 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) is with two heat exchange pipes of mutually isolating, wherein a heat exchange pipe is the connecting line between hiigh pressure stage injector (6) and hiigh pressure stage condenser (7), and another heat exchange pipe is the connecting line between hiigh pressure stage pump (10) and hiigh pressure stage generator (11).
6. mixed working fluid two-stage ejector type refrigerating machine according to claim 3, is characterized in that: described the first gas-liquid separator (5), the 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: described the first gas-liquid separator (5), the 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: described the first gas-liquid separator (5), the second gas-liquid separator (13) adopt the version of rectifier.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210116473.9A CN102853578B (en) | 2012-04-19 | 2012-04-19 | Mixed working medium two-stage jet type refrigerating machine |
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| CN104406323B (en) * | 2014-12-16 | 2016-10-12 | 山东大学 | A kind of three grades of ejector refrigeration systems |
| CN104406324B (en) * | 2014-12-16 | 2017-01-25 | 山东大学 | Improved two-stage ejection type refrigerating system |
| CN108397929B (en) * | 2018-02-28 | 2019-02-22 | 中国科学院力学研究所 | A kind of Trans-critical cycle inverse circulation systerm and method |
| 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 |
| CN111397234B (en) * | 2020-03-05 | 2021-07-20 | 浙江大学 | Low-grade heat-driven mixed working medium refrigerating system |
| CN111928522B (en) * | 2020-08-14 | 2021-04-30 | 中国矿业大学 | Injection type refrigerating system capable of recovering condensation heat and method thereof |
| CN113865013B (en) * | 2021-10-28 | 2022-08-23 | 珠海格力电器股份有限公司 | Variable-load adjusting air conditioning system and control method thereof |
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