CN102620461A - Auto-cascade jet type refrigerator - Google Patents
Auto-cascade jet type refrigerator Download PDFInfo
- Publication number
- CN102620461A CN102620461A CN201210116545XA CN201210116545A CN102620461A CN 102620461 A CN102620461 A CN 102620461A CN 201210116545X A CN201210116545X A CN 201210116545XA CN 201210116545 A CN201210116545 A CN 201210116545A CN 102620461 A CN102620461 A CN 102620461A
- Authority
- CN
- China
- Prior art keywords
- working medium
- condenser
- communicated
- injector
- pipeline
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Landscapes
- Jet Pumps And Other Pumps (AREA)
Abstract
The invention discloses an auto-cascade jet type refrigerator, which comprises a first throttling element, an evaporator, a first jet, a first condenser, a first circulating pump, a first generator, a first gas-liquid separator, a second throttling element and an evaporator condenser; the first jet is sequentially connected in series with the first condenser, the first gas-liquid separator, the first circulating pump and the first generator to form a loop; the evaporator condenser, the first throttling element and the evaporator are sequentially connected in series between the gas phase outlet of the first gas-liquid separator and the first jet; and the second throttling element and the evaporator condenser are sequentially connected in series between the liquid phase outlet of the first gas-liquid separator and the first jet. The invention breaks through the constraint of the traditional idea, and adopts the method of auto-cascade to decrease the compression ratio to be reached by a refrigeration system in order to solve the problem that the jet coefficient is abruptly decreased after the difference between the backpressure and jet pressure of the jet exceeds a certain value, and the auto-cascade jet type refrigerator can utilize the jet type refrigeration technology to achieve low refrigeration temperature.
Description
Technical field
The invention belongs to refrigeration technology field, especially relate to a kind of auto-cascade injection formula refrigeration machine.
Background technology
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.Spray type refrigerating is a kind of refrigeration modes that utilizes low-grade energy to drive, and can effectively utilize regenerative resource such as solar energy, underground heat and industrial exhaust heat, used heat; The employed refrigeration working medium of spray type refrigerating mainly is water, hydrocarbon or hydrogen fluorohydrocarbon class cold-producing medium, can avoid the use of the CFCs or the HCFCs class refrigeration working medium that damage the ozone layer.
Because the injector compression ratio is less in the conventional spray refrigeration machine; The cooling medium that is difficult to reach condenser is when chilling temperature is higher; The requirement of required condensing pressure, so cryogenic temperature is higher, this weakness was once once causing spray type refrigerating almost to be absorbed the replacement fully of formula refrigeration; In addition, research shows that jet coefficient will sharply descend after the difference of injector back pressure and injection pressure surpasses certain numerical value, this means that conventional spray formula refrigeration is difficult to realize lower cryogenic temperature.
For solving the problems of the technologies described above; Publication number is that the patent documentation of CN102155815A discloses a kind of steam jet refrigerating system based on two-fluid; Comprise rectifying column, superheater, gas ejector, evaporimeter, choke valve, subcooler, condenser, liquid pump and regenerator, described steam generator comprises rectifying column and superheater; Be provided with regenerator between described steam generator and the liquid pump, be provided with subcooler between steam generator and the choke valve.This device has realized that injector working fluid and driving fluid are two kinds of different types of fluids in the jet refrigeration circulation; And the members such as recycling, twin-stage ejector refrigeration, superheater and regenerator through waste heat; Improved the efficient of system; Thereby realize energy-conservationly, this device is simple, safe and reliable, has remarkable economical and social benefit.It is separator that but above-mentioned refrigeration system adopts rectifying column, complex structure, and operating cost is high.
Summary of the invention
The present invention is directed to the deficiency and the defective of prior art, proposed a kind of auto-cascade injection formula refrigeration machine, utilize method, reduce the required compression ratio that reaches of refrigeration system, improve ejector efficiency, make system can realize lower cryogenic temperature from overlapping.
A kind of auto-cascade injection formula refrigeration machine comprises first throttle element, evaporimeter, first injector, first condenser, first circulating pump, first generator, first gas-liquid separator, second restricting element and condenser/evaporator;
The Working-fluid intaking of described first injector is communicated with the sender property outlet of first generator, and the driving fluid inlet is communicated with the sender property outlet of evaporimeter and the cold working medium pipe outlet of condenser/evaporator, and jet exit is communicated with the working medium inlet of first condenser;
The working medium inlet of described first gas-liquid separator is communicated with the sender property outlet of first condenser; The gaseous working medium outlet is communicated with the hot working fluid entrance of condenser/evaporator; The liquid refrigerant outlet is communicated with the working medium inlet of first circulating pump and second restricting element respectively; The sender property outlet of first circulating pump is communicated with the working medium inlet of first generator, and the sender property outlet of second restricting element is communicated with the cold working medium entrance of condenser/evaporator;
The working medium inlet of described evaporimeter is communicated with the sender property outlet of first throttle element, and the working medium inlet of first throttle element is communicated with the hot working fluid pipe outlet of condenser/evaporator.
The fluid working substance of filling in the above-mentioned auto-cascade injection formula refrigeration machine is to contain the zeotrope that two or more pure working medium mixes, and wherein is rich in the saturation temperature of higher boiling working medium under evaporating pressure and is lower than and is rich in the saturation temperature of low boiling working fluid under condensing pressure.Under the preferable case, can also adopt and contain the zeotrope that pure working medium mixes more than three kinds or three kinds.The pure working medium of the fluid of selecting for use can be various pure cold-producing mediums.
The workflow of above-mentioned auto-cascade injection formula refrigeration machine is: being rich in high boiling working medium is become gases at high pressure after the external heat source heating in first generator; The high boiling Working medium gas that is rich in of the sender property outlet of first generator gets into first injector as working fluid; Injection comes the lower boiling working medium of being rich in of flash-pot and from the high boiling working medium of being rich in of condenser/evaporator; Mist is boosted by injection and reaches condensing pressure, and gets into the first condenser heat release; Fluid mixture by partial liquefaction after, gas-liquid mixture gets into first gas-liquid separator, a part that wherein is rich in the liquid phase fluid of higher boiling working medium is got back to first generator through after first circulating pump pressurization; Another part is rich in high boiling working medium liquid phase fluid and gets into condenser/evaporator evaporation heat absorption after through second restricting element, gets back to first injector then; The remaining gaseous fluid that is rich in low boiling working fluid is cooled in condenser/evaporator and is liquid in first gas-liquid separator; And through getting into evaporator evaporation heat absorption acquisition refrigeration behind the first throttle element; Get back to first injector then, system accomplishes the one action process.Owing to adopt method from overlapping, reduced the required pressure ratio that reaches of injector, can improve the coefficient of performance of system, and make system can obtain lower cryogenic temperature.
Refrigeration performance for further increase system.A kind of optimized technical scheme is: the pipeline between described first injector and first condenser is provided with second injector; The Working-fluid intaking of described second injector is communicated with the sender property outlet of first generator, and the driving fluid inlet is communicated with the jet exit of first injector, and jet exit is communicated with the working medium inlet of first condenser.At this moment, the high boiling Working medium gas that is rich in of first generator exports gets into first injector and second injector respectively as working fluid; Come the lower boiling working medium of being rich in of flash-pot and from the high boiling working medium of being rich in of condenser/evaporator; In first injector, being boosted by injection reaches intermediate pressure, and gets into second injector and continue to be boosted by injection and reach condensing pressure and get into first condenser.Owing to adopt two stages of compression, increased the accessible compression ratio of system, make refrigeration system can obtain lower cryogenic temperature.
Utilize when realizing many thermals source, as optimized technical scheme, also comprise the 3rd restricting element, the pipeline between described first injector and first condenser is provided with the 3rd injector; Be provided with the pipeline that is communicated with between the Working-fluid intaking of described the 3rd injector and the first circulating pump sender property outlet, this pipeline is provided with second generator; The Working-fluid intaking of described the 3rd injector is communicated with the sender property outlet of second generator, and the driving fluid inlet is communicated with the jet exit of first injector, and jet exit is communicated with the working medium inlet of first condenser; On the pipeline between the sender property outlet that the 3rd restricting element is located at pipeline or first circulating pump between the working medium inlet of sender property outlet and first generator of first circulating pump enters the mouth with the working medium of second generator.In the above-mentioned preferred version, system can utilize the different thermals source heating of two kinds of temperature levels simultaneously, realizes the classification utilization of different grade thermals source, and through the circulation coupling, utilizes when realizing many thermals source.The 3rd restricting element is introduced, and makes that adopting this structure can only utilize a circulating pump is that the generator of two pressure positions provides liquid simultaneously, reduces the initial cost of equipment.
For improving the overall performance of system, another kind of optimized technical scheme is: the pipeline between the driving fluid inlet of the sender property outlet of described evaporimeter and first injector is provided with the 4th injector, second condenser, second gas-liquid separator, second circulating pump and the 3rd generator; The Working-fluid intaking of described the 4th injector is communicated with the sender property outlet of the 3rd generator; The driving fluid inlet is communicated with the sender property outlet of evaporimeter and the cold working medium pipe outlet of condenser/evaporator respectively, and jet exit is communicated with the working medium inlet of second condenser; The working medium inlet of described second gas-liquid separator is communicated with the sender property outlet of second condenser; The gaseous working medium outlet is communicated with the driving fluid inlet of first injector; The liquid refrigerant outlet is communicated with second circulating pump working medium inlet, and the sender property outlet of second circulating pump is communicated with the working medium inlet of the 3rd generator.In this optimized technical scheme; The fluid working substance of filling in the auto-cascade injection formula refrigeration machine is the zeotrope that working medium mixes more than three kinds or three kinds; Wherein being rich in the saturation temperature of mid-boiling point working medium under evaporating pressure is lower than and is rich in the saturation temperature of low boiling working fluid under condensing pressure; Be rich in mid-boiling point working medium at the saturation pressure under the first condenser condenses temperature greater than being rich in the saturation pressure of higher boiling working medium under the second condenser condenses temperature, be rich in the saturation pressure of higher boiling working medium under the second condenser condenses temperature greater than being rich in the saturation pressure of low boiling working fluid under evaporating temperature.The pure working medium of the fluid of selecting for use can be various pure cold-producing mediums.
Above-mentioned to select working medium mixture more than three kinds or three kinds for use be that the workflow of the auto-cascade injection formula refrigeration machine of fluid working substance is: being rich in high boiling working medium is become gases at high pressure after the external heat source heating in the 3rd generator; The high boiling Working medium gas that is rich in of the 3rd generator exports gets into the 4th injector as working fluid; Injection comes the lower boiling working medium of being rich in of flash-pot and from the working medium that is rich in mid-boiling point of condenser/evaporator; Mist is boosted by injection and reaches intermediate pressure, and gets into the second condenser heat release; Fluid mixture by partial liquefaction after, gas-liquid mixture gets into second gas-liquid separator, wherein be rich in higher boiling working medium liquid phase fluid pass through get back to the 3rd generator after second circulating pump pressurization; The remaining gaseous fluid that is rich in low boiling working fluid and mid-boiling point working medium gets into first injector and continues to be boosted by injection in second gas-liquid separator, gets into the first condenser heat release after reaching condensing pressure; Fluid-mixing by partial liquefaction after; Gas-liquid mixture gets into first gas-liquid separator; A part that wherein is rich in the liquid phase fluid of mid-boiling point working medium is got back to first generator through after first circulating pump pressurization; And in first generator, be heated as gases at high pressure by external heat source, get into first injector as working fluid; The working medium liquid phase fluid that another part is rich in mid-boiling point gets into condenser/evaporator evaporation heat absorption after through the first throttle element, gets back to the 4th injector then; The remaining gaseous fluid that is rich in low boiling working fluid is cooled in condenser/evaporator and is liquid in first gas-liquid separator; And through getting into evaporator evaporation heat absorption acquisition refrigeration behind the first throttle element; Get back to the 4th injector then, system accomplishes the one action process.Because the middle pressure of the 4th injector outlet is rich in high boiling working medium and is condensed and directly pumps into the 3rd generator, reduces the flow and the load of the 4th injector, thereby plays the effect of the effect that improves the entire system performance.For improving the refrigeration performance of refrigeration machine of the present invention, as further optimized technical scheme, described first gas-liquid separator and second gas-liquid separator are rectifying column.At this moment, the setting of rectifying column makes and realizes being rich in mid-boiling point working medium and the good separation that is rich in low boiling working fluid in the gas-liquid separator of winning; In second gas-liquid separator, realize: liquid phase is for being rich in higher boiling working medium, and gas phase is not for containing or contain the higher boiling working medium of very small amount.Improved the hot property in the refrigeration machine.
For further reducing energy loss; A kind of optimized technical scheme is: the pipeline between the driving fluid inlet of the sender property outlet of described evaporimeter and first injector is pipeline I; Pipeline between the working medium inlet of condenser/evaporator hot working fluid pipe outlet and first throttle element is pipeline II, utilizes regenerator to carry out heat exchange between pipeline I and the pipeline II; Regenerator has two heat exchange pipes of isolating each other, and wherein a heat exchange pipe is the connecting line between the evaporimeter and first injector, and another pipeline is the connecting line between condenser/evaporator and the first throttle element.The inlet of cold working medium pipeline is communicated with the sender property outlet of evaporimeter in the described regenerator; The outlet of cold working medium pipeline is communicated with the driving fluid inlet of first injector; The hot working fluid entrance is communicated with condenser/evaporator hot working fluid pipe outlet, and the hot working fluid pipe outlet is communicated with the working medium inlet of first throttle element.At this moment, evaporator outlet be rich in low boiling working fluid to condenser/evaporator outlet be rich in the low boiling working fluid precooling after get into first injector again.Because the low boiling working fluid that is rich in of condenser/evaporator outlet is crossed and is got into evaporimeter through the first throttle element again after cold, has reduced restriction loss, thereby has played the effect that improves the entire system performance.For improving heat exchange efficiency, preferred as further, hot working fluid pipeline and the reverse layout of cold working medium pipeline in the described regenerator.
Be to improve heat exchange efficiency, hot working fluid pipeline in the condenser/evaporator described in above-mentioned each technical scheme and cold working medium pipeline be optional selects reverse layout.
Auto-cascade injection formula refrigeration machine of the present invention utilizes the method from overlapping, reduces the required compression ratio that reaches of refrigeration system, improves ejector efficiency, makes system can realize lower cryogenic temperature; And the present invention can be used for improving various existing spray type refrigerating system to improve its refrigeration performance.
Description of drawings
Fig. 1 is the system flow chart of one embodiment of the present invention.
Fig. 2 is the system flow chart of second kind of embodiment of the present invention.
Fig. 3 is the system flow chart of the third embodiment of the present invention.
Fig. 4 is the system flow chart of the 4th kind of embodiment of the present invention.
Fig. 5 is the system flow chart of the 5th kind of embodiment of the present invention.
Fig. 6 is the system flow chart of the 6th kind of embodiment of the present invention.
Wherein: 1, first throttle element; 2, evaporimeter; 3, first injector; 4, first condenser; 5, first gas-liquid separator; 6, second restricting element; 7, condenser/evaporator; 8, first circulating pump; 9, first generator; 10, second injector; 11, the 3rd restricting element; 12, second generator; 13, the 3rd injector; 15, the 4th injector; 16, second condenser; 17, second gas-liquid separator; 18, second circulating pump; 19, the 3rd generator; 20, regenerator.
The specific embodiment
Followingly the present invention is described in further detail with reference to accompanying drawing and specific embodiment.
As shown in Figure 1, a kind of auto-cascade injection formula refrigeration machine comprises first throttle element 1, evaporimeter 2, first injector 3, first condenser 4, first gas-liquid separator 5, second restricting element 6, condenser/evaporator 7, first circulating pump 8, first generator 9.First injector 3 is connected and is constituted the loop with first condenser 4, first gas-liquid separator 5, first circulating pump 8, first generator 9 successively; Outlet of the gaseous working medium of first gas- liquid separator 5 and 3 of first injectors connect successively condenser/evaporator 7, first throttle element 1, evaporimeter 2; Connect successively between the outlet of the liquid refrigerant of first gas-liquid separator 5 and first injector 3 second restricting element 6, condenser/evaporator 7.
Specifically be connected to: the Working-fluid intaking of first injector 3 is communicated with the sender property outlet of first generator 9; The driving fluid inlet of first injector 3 is communicated with the sender property outlet of evaporimeter 2 and the cold working medium pipe outlet of condenser/evaporator 7, and the jet exit of first injector 3 is communicated with the working medium inlet of first condenser 4; The working medium inlet of first gas-liquid separator 3 is communicated with the sender property outlet of first condenser 4; The gaseous working medium outlet of first gas-liquid separator 3 is communicated with the hot working fluid entrance of condenser/evaporator 7; The liquid refrigerant outlet of first gas-liquid separator 3 is communicated with the working medium inlet of first circulating pump 8 and second restricting element 6 respectively; The sender property outlet of first circulating pump 8 is communicated with the working medium inlet of first generator 9, and the sender property outlet of second restricting element 6 is communicated with the cold working medium entrance of condenser/evaporator 7; The working medium inlet of evaporimeter 2 is communicated with the sender property outlet of first throttle element 1, and the working medium inlet of first throttle element 1 is communicated with the hot working fluid pipe outlet of condenser/evaporator 7; The cold working medium pipe outlet of condenser/evaporator 7 is communicated with the driving fluid of first injector 3 inlet.
The zeotrope that the fluid working substance of filling in the ejector type refrigerating machine mixes for two or more working medium wherein is rich in the saturation temperature of higher boiling working medium under evaporating pressure and is lower than and is rich in the saturation temperature of low boiling working fluid under condensing pressure.The pure working medium of the fluid of selecting for use can be various pure cold-producing mediums, as with R134a as higher boiling working medium, R32 is as low boiling working fluid.
The working medium workflow is: being rich in high boiling working medium is become gases at high pressure after the external heat source heating in first generator 9; The high boiling Working medium gas that is rich in of the sender property outlet of first generator 9 gets into first injector 3 as working fluid; Injection comes the lower boiling working medium of being rich in of flash-pot 2 and from the high boiling working medium of being rich in of condenser/evaporator 7; Mist is boosted by injection and reaches condensing pressure, and gets into 4 heat releases of first condenser; Fluid mixture by partial liquefaction after, gas-liquid mixture gets into first gas-liquid separator 5, the part of liquid phase fluid that wherein is rich in higher boiling working medium is got back to first generator 9 after through the pressurization of first circulating pump 8; Another part is rich in high boiling working medium liquid phase fluid and gets into condenser/evaporator 7 evaporation heat absorptions through second restricting element, 6 backs, gets back to first injector 3 then; The remaining gaseous fluid that is rich in low boiling working fluid is cooled in condenser/evaporator 7 and is liquid in first gas-liquid separator 5; And process first throttle element 1 back gets into evaporimeter 2 evaporation heat absorption acquisition refrigeration; Get back to first injector 3 then, system accomplishes the one action process.Owing to adopt method from overlapping, reduced the required pressure ratio that reaches of injector, can improve the coefficient of performance of system, and make system can obtain lower cryogenic temperature.
In the above-mentioned embodiment, the first throttle element 1 and second restricting element 6 can be selected choke valve or capillary; First gas-liquid separator 5 can be selected rectifying column; First injector 2 is gas-gas blowout love dart; Waste hot gas, solar energy or geothermal energy that the driving heat source of generator 9 can select engine to discharge; First condenser 4 can be selected common double pipe heat exchanger, plate type heat exchanger, nest plate type heat exchanger or light pipe immersion heat exchanger with evaporimeter 2; Hot working fluid pipeline and cold working medium pipeline in the condenser/evaporator 7 also can be selected reverse layout, to improve heat exchange efficiency.
This embodiment is the improvement of on embodiment 1 basis, carrying out, and is as shown in Figure 2, on the basis of system shown in Figure 1, is connected with condenser 4 after first injector 3 and the series connection of second injector 10 again.Between the Working-fluid intaking of the outlet of first generator 9 and second injector 10 pipeline that is connected is arranged.
Specifically be connected to: the pipeline between first injector 3 and first condenser 4 is provided with second injector 10; The Working-fluid intaking of second injector 10 is communicated with the sender property outlet of first generator 9, and the driving fluid inlet of second injector 10 is communicated with the jet exit of first injector 3, and the jet exit of second injector 10 is communicated with the working medium inlet of first condenser 4.Remaining part connects with embodiment 1.
Compare with embodiment 1 that the difference of working medium workflow is among this embodiment, the high boiling Working medium gas that is rich in of first generator, 9 outlets gets into first injector 3 and second injector 10 respectively as working fluid; Come the lower boiling working medium of being rich in of flash-pot 2 and from the high boiling working medium of being rich in of condenser/evaporator 7; In first injector 3, being boosted by injection reaches intermediate pressure, and gets into second injector 10 and continue to be boosted by injection and reach condensing pressure and get into first condenser 4.Owing to adopt two stages of compression, increased the compression ratio that system can reach, make refrigeration system can obtain lower cryogenic temperature.
As shown in Figure 3, this embodiment is the improvement of on embodiment 1 basis, carrying out, connect successively between the Working-fluid intaking of the outlet of first circulating pump 8 and the 3rd injector 13 the 3rd restricting element 11 and second generator 12.
Specifically be connected to: the Working-fluid intaking of the 3rd injector 13 is communicated with the sender property outlet of second generator 12; The driving fluid inlet of the 3rd injector 13 is communicated with the jet exit of first injector 3, and the jet exit of the 3rd injector 13 is communicated with the working medium inlet of first condenser 4; The 3rd restricting element 11 is located on the pipeline between the working medium inlet of sender property outlet and second generator 12 of first circulating pump 8.Remaining part connects with embodiment 1.
Compare with embodiment 1 that the difference of working medium workflow is among this embodiment: the partially liq of first circulating pump, 8 outlets directly gets into first generator 9; In first generator 9, by becoming gases at high pressure after the heating of outside high temperature heat source, and get into first injector 3 as working fluid; Another part liquid gets into second generators 12 through the 3rd restricting element 11 back, in second generator 12, by becoming gases at high pressure after the outside low-temperature heat source heating, and gets into the 3rd injector 13 as working fluid.This system can utilize the different thermals source heating of two kinds of temperature levels simultaneously, realizes the classification utilization of different grade thermals source, and through the circulation coupling, utilizes when realizing many thermals source.The 3rd restricting element 11 of connecting between first circulating pump 8 and second generator 12, adopting this structure can only utilize a circulating pump is that the generator of two pressure positions provides liquid simultaneously, reduces the initial cost of equipment.
Embodiment 4
As shown in Figure 4, this embodiment is the improvement of on embodiment 4 bases, carrying out, wherein the 3rd restricting element 11 and first generator 9 between pipeline on.
Specifically be connected to: the working medium inlet of second generator 12 is communicated with the sender property outlet of first circulating pump 8.The sender property outlet of the 3rd restricting element 11 is communicated with the working medium inlet of first generator 9, and the working medium inlet of the 3rd restricting element 11 links to each other with the sender property outlet of first circulating pump 8.Remaining part connects with embodiment 1.Remaining part connects with embodiment 3.
Compare with embodiment 4 that the difference of working medium workflow is among this embodiment: the partially liq of first circulating pump, 8 outlets directly gets into second generator 12; In second generator 12, by becoming gases at high pressure after the heating of outside high temperature heat source, and get into the 3rd injector 13 as working fluid; Another part liquid gets into first generators 9 through the 3rd restricting element 11 back, in first generator 9, by becoming gases at high pressure after the outside low-temperature heat source heating, and gets into first injector 3 as working fluid.
As shown in Figure 5, this embodiment is the improvement of on embodiment 1 basis, carrying out, and between the evaporimeter 2 and first injector 3, is in series with the 4th injector 15, second condenser 16, second gas-liquid separator 17; Be in series with second circulating pump 18 and the 3rd generator 19 between second gas-liquid separator, 17 liquid outlets and the 4th injector 15 Working-fluid intakings.
Specifically be connected to: the Working-fluid intaking of the 4th injector 15 is communicated with the sender property outlet of the 3rd generator 19; The driving fluid inlet of the 4th injector 15 is communicated with the sender property outlet of evaporimeter 2 and the cold working medium pipe outlet of condenser/evaporator 7 respectively, and the jet exit of the 4th injector 15 is communicated with the working medium inlet of second condenser 16.The working medium inlet of second gas-liquid separator 17 is communicated with the sender property outlet of second condenser 16; The gaseous working medium outlet of second gas-liquid separator 17 is communicated with the driving fluid inlet of first injector 3; The liquid refrigerant outlet is communicated with second circulating pump, 18 working medium inlet, and the sender property outlet of second circulating pump 18 is communicated with the working medium inlet of the 3rd generator 19.Remaining part connects with embodiment 1, and wherein second gas-liquid separator 17 can be selected rectifying column.
The fluid working substance of filling in the auto-cascade injection formula refrigeration machine of this embodiment is the zeotrope that working medium mixes more than three kinds or three kinds; Wherein being rich in the saturation temperature of mid-boiling point working medium under evaporating pressure is lower than and is rich in the saturation temperature of low boiling working fluid under condensing pressure; Be rich in mid-boiling point working medium at the saturation pressure under the first condenser condenses temperature greater than being rich in the saturation pressure of higher boiling working medium under the second condenser condenses temperature, be rich in the saturation pressure of higher boiling working medium under the second condenser condenses temperature greater than being rich in the saturation pressure of low boiling working fluid under evaporating temperature.The pure working medium of the fluid of selecting for use can be various pure cold-producing mediums, as with R236fa as higher boiling working medium, R134a is as mid-boiling point working medium, R32 is as low boiling working fluid.
Above-mentioned auto-cascade injection formula refrigeration machine; The workflow difference of itself and a kind of auto-cascade injection formula refrigeration machine is; Be rich in high boiling working medium and in the 3rd generator 19, become gases at high pressure after the external heat source heating; The high boiling Working medium gas that is rich in of the sender property outlet of the 3rd generator 19 gets into the 4th injector 15 as working fluid; Injection comes the lower boiling working medium of being rich in of flash-pot 2 and from the working medium that is rich in mid-boiling point of condenser/evaporator 7, mist is boosted by injection and reaches intermediate pressure, and gets into 16 heat releases of second condenser; Fluid mixture by partial liquefaction after, gas-liquid mixture gets into second gas-liquid separator 17, wherein be rich in higher boiling working medium liquid phase fluid pass through get back to the 3rd generator 19 after the pressurization of second circulating pump 18; The remaining gaseous fluid that is rich in low boiling working fluid and mid-boiling point working medium gets into first injector 3 and continues to be boosted by injection in second gas-liquid separator 17, gets into 4 heat releases of first condenser after reaching condensing pressure; Fluid-mixing by partial liquefaction after; Gas-liquid mixture gets into first gas-liquid separator 5; The part of liquid phase fluid that wherein is rich in mid-boiling point working medium is got back to first generator 9 after through the pressurization of first circulating pump 8; And in first generator 9, be heated as gases at high pressure by external heat source, get into first injector 3 as working fluid; The working medium liquid phase fluid that another part is rich in mid-boiling point gets into condenser/evaporator 7 evaporation heat absorptions through second restricting element, 6 backs, gets back to the 4th injector 15 then; The remaining gaseous fluid that is rich in low boiling working fluid is cooled in condenser/evaporator 7 and is liquid in first gas-liquid separator 5; And process first throttle element 1 back gets into evaporimeter 2 evaporation heat absorption acquisition refrigeration; Get back to the 4th injector 15 then, system accomplishes the one action process.Because the middle pressure of the 4th injector 15 jet exits is rich in high boiling working medium and is condensed and directly pumps into the 3rd generator 19, reduces the flow and the load of first injector 3, thereby plays the effect of the effect that improves the entire system performance.
As shown in Figure 6; This embodiment is the improvement of on embodiment 1 basis, carrying out; On embodiment 1 basis, increased regenerator 20; Regenerator 20 has two heat exchange pipes of isolating each other, and wherein a heat exchange pipe is the connecting line between the evaporimeter 2 and first injector 3, and another pipeline is the connecting line between condenser/evaporator 7 and the first throttle element 1.
Specifically be linked as: the inlet of cold working medium pipeline is communicated with the sender property outlet of evaporimeter 2 in the regenerator 20; The outlet of cold working medium pipeline is communicated with the driving fluid inlet of first injector 3; The hot working fluid entrance is communicated with condenser/evaporator 7 hot working fluid pipe outlets in the regenerator 20, and the hot working fluid pipe outlet is communicated with the working medium inlet of first throttle element 1.Hot working fluid pipeline and cold working medium pipeline in the regenerator 20 can adopt reverse layout, to improve heat exchange efficiency.Remaining part connects with embodiment 1.
Compare with embodiment 1 that the difference of working medium workflow is among this embodiment: evaporimeter 2 outlets be rich in low boiling working fluid to condenser/evaporator 7 outlets be rich in the low boiling working fluid precooling after get into first injector 3 again.Because the low boiling working fluid that is rich in of condenser/evaporator 7 outlet is crossed and is got into evaporimeter 2 through first throttle element 1 again after cold, has reduced restriction loss, thereby has played the effect that improves the entire system performance.
Application examples 1
As higher boiling working medium, R32 has carried out analog computation as low boiling working fluid to the present invention's device shown in Figure 1 with R134a, and the assumed condition of calculating is following: (1) system is in steady-working state; (2) pressure drop of ignoring pipeline and heat exchanger with leak heat; (3) condensation temperature of condenser working medium is 30 ℃, and the generator occurrence temperature is 100 ℃, and the cryogenic temperature of evaporimeter is-35 ℃.
This moment, the coefficient of performance of this system was 0.1144, and traditional single-stage ejector type refrigerating machine can't be worked under this operating mode.
Claims (8)
1. auto-cascade injection formula refrigeration machine; Comprise first throttle element (1), evaporimeter (2), first injector (3), first condenser (4), first circulating pump (8), first generator (9); It is characterized in that, also comprise first gas-liquid separator (5), second restricting element (6) and condenser/evaporator (7);
The Working-fluid intaking of described first injector (3) is communicated with the sender property outlet of first generator (9); The driving fluid inlet is communicated with the sender property outlet of evaporimeter (2) and the cold working medium pipe outlet of condenser/evaporator (7), and jet exit is communicated with the working medium inlet of first condenser (4);
The working medium inlet of described first gas-liquid separator (5) is communicated with the sender property outlet of first condenser (4); The gaseous working medium outlet is communicated with the hot working fluid entrance of condenser/evaporator (7); The liquid refrigerant outlet is communicated with the working medium inlet of first circulating pump (8) and second restricting element (6) respectively; The sender property outlet of first circulating pump (8) is communicated with the working medium inlet of first generator (9), and the sender property outlet of second restricting element (6) is communicated with the cold working medium entrance of condenser/evaporator (7);
The working medium inlet of described evaporimeter (2) is communicated with the sender property outlet of first throttle element (1), and the working medium inlet of first throttle element (1) is communicated with the hot working fluid pipe outlet of condenser/evaporator (7).
2. auto-cascade injection formula refrigeration machine according to claim 1 is characterized in that, the pipeline between described first injector (3) and first condenser (4) is provided with second injector (10); The Working-fluid intaking of described second injector (10) is communicated with the sender property outlet of first generator (9), and the driving fluid inlet is communicated with the jet exit of first injector (3), and jet exit is communicated with the working medium inlet of first condenser (4).
3. auto-cascade injection formula refrigeration machine according to claim 1 is characterized in that, also comprises the 3rd restricting element (11); Pipeline between described first injector (3) and first condenser (4) is provided with the 3rd injector (13); Be provided with the pipeline that is communicated with between the Working-fluid intaking of described the 3rd injector (13) and the sender property outlet of first circulating pump (8), this pipeline is provided with second generator (12);
The Working-fluid intaking of described the 3rd injector (13) is communicated with the sender property outlet of second generator (12), and the driving fluid inlet is communicated with the jet exit of first injector (3), and jet exit is communicated with the working medium inlet of first condenser (4);
On the pipeline between the sender property outlet that described the 3rd restricting element (11) is located at pipeline or first circulating pump (8) between the working medium inlet of sender property outlet and first generator (9) of first circulating pump (8) enters the mouth with the working medium of second generator (12).
4. auto-cascade injection formula refrigeration machine according to claim 1; It is characterized in that the pipeline between the driving fluid inlet of the sender property outlet of described evaporimeter (2) and first injector (3) is provided with the 4th injector (15), second condenser (16), second gas-liquid separator (17), second circulating pump (18) and the 3rd generator (19);
The Working-fluid intaking of described the 4th injector (15) is communicated with the sender property outlet of the 3rd generator (19); The driving fluid inlet is communicated with the sender property outlet of evaporimeter (2) and the cold working medium pipe outlet of condenser/evaporator (7) respectively, and jet exit is communicated with the working medium inlet of second condenser (16);
The working medium inlet of described second gas-liquid separator (17) is communicated with the sender property outlet of second condenser (16); The gaseous working medium outlet is communicated with the driving fluid inlet of first injector (3); The liquid refrigerant outlet is communicated with second circulating pump (18) working medium inlet, and the sender property outlet of second circulating pump (18) is communicated with the working medium inlet of the 3rd generator (19).
5. the auto-cascade injection formula refrigeration machine of stating according to claim 4 is characterized in that, described first gas-liquid separator (5) is a rectifying column with second gas-liquid separator (17).
6. auto-cascade injection formula refrigeration machine according to claim 1; It is characterized in that; Pipeline between the driving fluid inlet of the sender property outlet of described evaporimeter (2) and first injector (3) is pipeline I; Pipeline between the working medium inlet of condenser/evaporator (7) hot working fluid pipe outlet and first throttle element (1) is pipeline II, utilizes regenerator (20) to carry out heat exchange between pipeline I and the pipeline II.
7. according to the described auto-cascade injection formula of the arbitrary claim of claim 1-6 refrigeration machine, it is characterized in that hot working fluid pipeline and the reverse layout of cold working medium pipeline in the described condenser/evaporator (7).
8. auto-cascade injection formula refrigeration machine according to claim 6 is characterized in that, hot working fluid pipeline and the reverse layout of cold working medium pipeline in the described regenerator (20).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210116545.XA CN102620461B (en) | 2012-04-19 | 2012-04-19 | Auto-cascade jet type refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210116545.XA CN102620461B (en) | 2012-04-19 | 2012-04-19 | Auto-cascade jet type refrigerator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102620461A true CN102620461A (en) | 2012-08-01 |
| CN102620461B CN102620461B (en) | 2014-04-16 |
Family
ID=46560542
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210116545.XA Expired - Fee Related CN102620461B (en) | 2012-04-19 | 2012-04-19 | Auto-cascade jet type refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102620461B (en) |
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103759449A (en) * | 2014-01-09 | 2014-04-30 | 西安交通大学 | Two-stage steam compression circulating system with two ejectors for efficiency enhancement |
| CN104315741A (en) * | 2014-09-30 | 2015-01-28 | 河南科技大学 | Mixing working medium jet type refrigeration cycle system and refrigeration cycle method |
| CN104930741A (en) * | 2015-05-29 | 2015-09-23 | 浙江工业大学 | Novel compression auxiliary jetting refrigerating system with supercooler |
| CN105627622A (en) * | 2016-03-23 | 2016-06-01 | 上海海洋大学 | Jetting type auto-cascade refrigeration system for waste heat recovery of tuna clipper |
| CN106766352A (en) * | 2016-11-12 | 2017-05-31 | 浙江理工大学 | Steam jet type cooling device and its refrigerating method that heat/work(joint drives |
| CN107192153A (en) * | 2017-07-25 | 2017-09-22 | 广东工业大学 | Twin-stage sweat cooling system with injector |
| CN107990590A (en) * | 2017-11-29 | 2018-05-04 | 浙江海洋大学 | A kind of new fishing boat absorption type refrigerating unit and its refrigerating method |
| CN108106048A (en) * | 2018-01-11 | 2018-06-01 | 西安交通大学 | A kind of injector expansion self-cascade refrigeration system system and the course of work |
| CN108344195A (en) * | 2018-04-20 | 2018-07-31 | 天津商业大学 | Recycle the one machine dual temperature refrigeration system of two level injection of expansion work |
| CN108592448A (en) * | 2018-05-22 | 2018-09-28 | 福建工程学院 | Synergy auto-cascading refrigeration system is pressed in a kind of injector |
| CN110296543A (en) * | 2019-07-31 | 2019-10-01 | 广东工业大学 | A kind of refrigeration or heat pump system of the gas-liquid separation heat exchanging of band injection |
| CN111271887A (en) * | 2020-03-09 | 2020-06-12 | 双良节能系统股份有限公司 | Liquid-separating condensation non-azeotropic compression injection type refrigeration cycle and working method thereof |
| CN111397234A (en) * | 2020-03-05 | 2020-07-10 | 浙江大学 | Low-grade heat-driven mixed working medium refrigerating system |
| CN111795452A (en) * | 2019-04-08 | 2020-10-20 | 开利公司 | Air conditioning system |
| CN112524831A (en) * | 2020-12-11 | 2021-03-19 | 西安交通大学 | Flash separation injection refrigeration cycle system using mixed refrigerant and working method |
| CN112696843A (en) * | 2021-01-08 | 2021-04-23 | 西北工业大学 | Jet type refrigerating device for compressing liquid refrigerant |
| CN112815561A (en) * | 2019-10-31 | 2021-05-18 | 广东美的白色家电技术创新中心有限公司 | Refrigeration device |
| CN113175762A (en) * | 2021-04-13 | 2021-07-27 | 西安交通大学 | Synergistic self-cascade refrigeration circulating system of two-phase ejector and control method |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0875283A (en) * | 1994-09-09 | 1996-03-19 | Hitachi Ltd | Cryogenic freezing device |
| US20050188717A1 (en) * | 2004-02-27 | 2005-09-01 | Yasukazu Aikawa | Air conditioning system for vehicle |
| CN1818509A (en) * | 2006-03-09 | 2006-08-16 | 西安交通大学 | Steam jetting refrigerating circulation system |
| CN101603749A (en) * | 2009-07-07 | 2009-12-16 | 河南科技大学 | A kind of auto-cascade injection low-temperature refrigeration circulating device |
| CN101603745A (en) * | 2009-07-07 | 2009-12-16 | 河南科技大学 | A kind of pressure-boosting absorptive-type auto-cascade absorption refrigeration circulating system |
| WO2010096863A1 (en) * | 2009-02-25 | 2010-09-02 | Renewable Energy Systems Limited | A heat pump, a combined heating and cooling system, a power generation system and a solar collector |
| CN102155815A (en) * | 2011-03-30 | 2011-08-17 | 浙江大学 | Steam jet refrigeration system based on double-fluid |
| CN202547173U (en) * | 2012-04-19 | 2012-11-21 | 浙江大学宁波理工学院 | Auto-cascade jet-type refrigerator |
-
2012
- 2012-04-19 CN CN201210116545.XA patent/CN102620461B/en not_active Expired - Fee Related
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0875283A (en) * | 1994-09-09 | 1996-03-19 | Hitachi Ltd | Cryogenic freezing device |
| US20050188717A1 (en) * | 2004-02-27 | 2005-09-01 | Yasukazu Aikawa | Air conditioning system for vehicle |
| CN1818509A (en) * | 2006-03-09 | 2006-08-16 | 西安交通大学 | Steam jetting refrigerating circulation system |
| WO2010096863A1 (en) * | 2009-02-25 | 2010-09-02 | Renewable Energy Systems Limited | A heat pump, a combined heating and cooling system, a power generation system and a solar collector |
| CN101603749A (en) * | 2009-07-07 | 2009-12-16 | 河南科技大学 | A kind of auto-cascade injection low-temperature refrigeration circulating device |
| CN101603745A (en) * | 2009-07-07 | 2009-12-16 | 河南科技大学 | A kind of pressure-boosting absorptive-type auto-cascade absorption refrigeration circulating system |
| CN102155815A (en) * | 2011-03-30 | 2011-08-17 | 浙江大学 | Steam jet refrigeration system based on double-fluid |
| CN202547173U (en) * | 2012-04-19 | 2012-11-21 | 浙江大学宁波理工学院 | Auto-cascade jet-type refrigerator |
Cited By (30)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103759449B (en) * | 2014-01-09 | 2015-10-21 | 西安交通大学 | The two-stage steam compression type circulatory system of dual jet synergy |
| CN103759449A (en) * | 2014-01-09 | 2014-04-30 | 西安交通大学 | Two-stage steam compression circulating system with two ejectors for efficiency enhancement |
| CN104315741A (en) * | 2014-09-30 | 2015-01-28 | 河南科技大学 | Mixing working medium jet type refrigeration cycle system and refrigeration cycle method |
| CN104930741A (en) * | 2015-05-29 | 2015-09-23 | 浙江工业大学 | Novel compression auxiliary jetting refrigerating system with supercooler |
| CN105627622B (en) * | 2016-03-23 | 2018-08-21 | 上海海洋大学 | A kind of tuna clipper waste heat recovery injecting type auto-cascading refrigeration system |
| CN105627622A (en) * | 2016-03-23 | 2016-06-01 | 上海海洋大学 | Jetting type auto-cascade refrigeration system for waste heat recovery of tuna clipper |
| CN106766352B (en) * | 2016-11-12 | 2019-03-12 | 浙江理工大学 | Heat/function joint driving steam jet type cooling device and its refrigerating method |
| CN106766352A (en) * | 2016-11-12 | 2017-05-31 | 浙江理工大学 | Steam jet type cooling device and its refrigerating method that heat/work(joint drives |
| CN107192153A (en) * | 2017-07-25 | 2017-09-22 | 广东工业大学 | Twin-stage sweat cooling system with injector |
| CN107192153B (en) * | 2017-07-25 | 2023-07-28 | 广东工业大学 | Double-stage evaporation refrigeration system with ejector |
| CN107990590A (en) * | 2017-11-29 | 2018-05-04 | 浙江海洋大学 | A kind of new fishing boat absorption type refrigerating unit and its refrigerating method |
| CN107990590B (en) * | 2017-11-29 | 2019-07-05 | 浙江海洋大学 | A kind of fishing boat absorption type refrigerating unit and its refrigerating method |
| CN108106048A (en) * | 2018-01-11 | 2018-06-01 | 西安交通大学 | A kind of injector expansion self-cascade refrigeration system system and the course of work |
| CN108106048B (en) * | 2018-01-11 | 2023-08-01 | 西安交通大学 | Ejector expansion self-cascade refrigeration cycle system and working process |
| CN108344195A (en) * | 2018-04-20 | 2018-07-31 | 天津商业大学 | Recycle the one machine dual temperature refrigeration system of two level injection of expansion work |
| CN108592448A (en) * | 2018-05-22 | 2018-09-28 | 福建工程学院 | Synergy auto-cascading refrigeration system is pressed in a kind of injector |
| CN111795452B (en) * | 2019-04-08 | 2024-01-05 | 开利公司 | Air conditioning system |
| CN111795452A (en) * | 2019-04-08 | 2020-10-20 | 开利公司 | Air conditioning system |
| CN110296543A (en) * | 2019-07-31 | 2019-10-01 | 广东工业大学 | A kind of refrigeration or heat pump system of the gas-liquid separation heat exchanging of band injection |
| CN110296543B (en) * | 2019-07-31 | 2024-07-19 | 广东工业大学 | Refrigerating or heat pump system with jet gas-liquid separation heat exchange function |
| CN112815561A (en) * | 2019-10-31 | 2021-05-18 | 广东美的白色家电技术创新中心有限公司 | Refrigeration device |
| CN112815561B (en) * | 2019-10-31 | 2022-03-25 | 广东美的白色家电技术创新中心有限公司 | Refrigeration device |
| CN111397234B (en) * | 2020-03-05 | 2021-07-20 | 浙江大学 | Low-grade heat-driven mixed working medium refrigerating system |
| CN111397234A (en) * | 2020-03-05 | 2020-07-10 | 浙江大学 | Low-grade heat-driven mixed working medium refrigerating system |
| CN111271887A (en) * | 2020-03-09 | 2020-06-12 | 双良节能系统股份有限公司 | Liquid-separating condensation non-azeotropic compression injection type refrigeration cycle and working method thereof |
| CN112524831B (en) * | 2020-12-11 | 2021-09-03 | 西安交通大学 | Flash separation injection refrigeration cycle system using mixed refrigerant and working method |
| CN112524831A (en) * | 2020-12-11 | 2021-03-19 | 西安交通大学 | Flash separation injection refrigeration cycle system using mixed refrigerant and working method |
| CN112696843A (en) * | 2021-01-08 | 2021-04-23 | 西北工业大学 | Jet type refrigerating device for compressing liquid refrigerant |
| CN113175762A (en) * | 2021-04-13 | 2021-07-27 | 西安交通大学 | Synergistic self-cascade refrigeration circulating system of two-phase ejector and control method |
| CN113175762B (en) * | 2021-04-13 | 2022-08-05 | 西安交通大学 | Synergistic self-cascade refrigeration circulating system of two-phase ejector and control method |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102620461B (en) | 2014-04-16 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102620461B (en) | Auto-cascade jet type refrigerator | |
| CN100434834C (en) | Steam jetting refrigerating circulation system | |
| CN102889752B (en) | Methane-rich gas liquefying device provided with ammonia absorption type refrigerator for precooling and methane-rich gas liquefying technology | |
| CN108211648B (en) | Heat recovery type condensation and temperature and pressure swing adsorption combined process oil gas recovery device | |
| CN202547173U (en) | Auto-cascade jet-type refrigerator | |
| CN104019579B (en) | Mixed working medium low-temperature refrigeration cycle system for driving ejector by utilizing waste heat | |
| CN102650478B (en) | Trans-critical-compression/absorption composite refrigeration device utilizing low-grade heat | |
| CN204373252U (en) | Change type CO2 trans critical cycle refrigeration system | |
| CN103528263A (en) | Injection type refrigerating machine with middle heat exchanging part | |
| CN104929706A (en) | Combined circulating energy supply system | |
| CN102853578B (en) | Mixed working medium two-stage jet type refrigerating machine | |
| CN102620465A (en) | Pump-free jet refrigerating machine | |
| CN101464070B (en) | Injection type low-temperature refrigerator | |
| CN201964557U (en) | Integral type heat pipe hybrid air-conditioner | |
| CN102287949A (en) | Self-cascade system with vortex tube | |
| CN102322705B (en) | Circulating device combining diffusing absorption-type refrigeration and vapor compression refrigeration | |
| CN101482321B (en) | Ultra-low temperature heat pump water heater | |
| KR101138970B1 (en) | Defrosting system using air cooling refrigerant evaporator and condenser | |
| CN101871702B (en) | Double heat source high-efficiency absorption refrigerating plant | |
| CN101776347B (en) | Absorption type refrigerating unit with pressure recovery part | |
| CN101586482B (en) | Low-temperature type engine and heat regenerating method thereof | |
| CN111397234B (en) | Low-grade heat-driven mixed working medium refrigerating system | |
| CN106352586A (en) | Double machine head heat source tower heat pump unit | |
| CN201340140Y (en) | Low-temperature refrigeration apparatus driven by low-temperature heat source | |
| CN202660808U (en) | Novel heat pipe and heat pump combined refrigerating device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140416 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |