CN109916102A - Auto-cascade cycle dual temperature system with vortex tube - Google Patents
Auto-cascade cycle dual temperature system with vortex tube Download PDFInfo
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- CN109916102A CN109916102A CN201910052193.8A CN201910052193A CN109916102A CN 109916102 A CN109916102 A CN 109916102A CN 201910052193 A CN201910052193 A CN 201910052193A CN 109916102 A CN109916102 A CN 109916102A
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Abstract
The present invention discloses a kind of Auto-cascade cycle dual temperature system with vortex tube, belong to auto-cascading refrigeration system technical field, it is not high to solve traditional auto-cascading refrigeration system refrigerating efficiency, the low problem of energy utilization rate, in this case, pass through setting vortex tube and the second condenser, the refrigerant for coming out compressor flows directly into vortex tube, and cold end of a part of refrigerant through vortex tube further cools down and participates in original auto-cascade refrigeration, needed for another part is further heated up through the hot end of vortex tube to provide life heat source, to improve the refrigerating efficiency of system and the utilization rate of the energy.
Description
Technical field
The present invention relates to auto-cascading refrigeration system technical field, in particular to a kind of Auto-cascade cycle dual temperature system with vortex tube
System.
Background technique
Traditional auto-cascading refrigeration system includes compressor, condenser, gas-liquid separator, first throttle valve, heat exchanger,
Two throttle valves and evaporator, refrigerant (mixture for being generally at least two-spot non-azeotropic working medium) after compressor compresses, at
For high temperature and high pressure gas, the gas-liquid mixture of cryogenic high pressure is formed after condenser condenses, and subsequently into gas-liquid separator, is passed through
Gas-liquid separator separates form vapor phase refrigerant and liquid phase refrigerant, wherein liquid phase refrigerant flows after first throttle valve throttles
Enter and exchange heat in heat exchanger with the vapor phase refrigerant in inflow heat exchanger simultaneously, eventually returns in compressor；And after exchanging heat
Vapor phase refrigerant flowed into evaporator through second throttle, and eventually return to press after absorbing the heat in outside ambient air
In contracting machine, during this, due to condenser and outside air heat convection, so that heat is distributed into external environment, due to
The refrigerating efficiency of system does not improve, and radiates only by condenser, it is difficult to needed for meeting the heat source in life, the utilization of the energy
Rate is lower.
Summary of the invention
In order to solve the above-mentioned technical problem, refrigerating efficiency, satisfaction life heat can be improved the object of the present invention is to provide a kind of
Auto-cascade cycle dual temperature system needed for source with vortex tube.
In order to realize that the purpose of foregoing invention, the present invention propose the first following technical solution:
A kind of Auto-cascade cycle dual temperature system with vortex tube, the refrigeration cycle at least two-spot mixed non-azeotropic refrigerant, comprising:
Compressor；
Vortex tube including minor air cell, is respectively communicated with the cold end nozzle and hot end nozzle of the minor air cell；
First condenser；
Second condenser；
Gas-liquid separator has liquid phase branch and gas phase branch；
First throttle valve；
First Heat Exchanger is internally provided with the first pipeline and the second pipeline that can mutually exchange heat；
Second heat exchanger is internally provided with the third pipeline and the 4th pipeline that can mutually exchange heat；
Second throttle；
Evaporator；
Third throttle valve；
The first heating of user end, including the first heating pipeline to exchange heat with first condenser pipe；
The second heating of user end, including the second heating pipeline to exchange heat with second condenser pipe；
The compressor, minor air cell, cold end nozzle, the first condenser pipe, liquid phase branch, first throttle valve, the first pipeline according to
It is secondary be connected constitute liquid-phase loop；The compressor, minor air cell, cold end nozzle, the first condenser pipe, gas phase branch, second
Pipeline, third pipeline, second throttle, evaporator, the 4th pipeline are sequentially connected logical composition gas phase circuit；The compressor,
Minor air cell, hot end nozzle, the second condenser pipe, third throttle valve are sequentially connected logical composition heat supplying loop.
In above-mentioned technical proposal, it is preferred that be arranged on the path for being exported to the suction port of compressor of the 4th pipeline
There is bypass, first pipeline is passed through in the bypass.
The present invention also proposes following second of technical solution, is also able to achieve the purpose of foregoing invention:
A kind of Auto-cascade cycle dual temperature system with vortex tube, it is special for the refrigeration cycle of at least two-spot mixed non-azeotropic refrigerant
Sign is, comprising:
Compressor；
Vortex tube including minor air cell, is respectively communicated with the cold end nozzle and hot end nozzle of the minor air cell；
First condenser has the first condenser pipe；
Second condenser has the second condenser pipe；
Gas-liquid separator has liquid phase branch and gas phase branch；
First throttle valve；
First Heat Exchanger is internally provided with the first pipeline and the second pipeline that can mutually exchange heat；
Second heat exchanger is internally provided with the third pipeline and the 4th pipeline that can mutually exchange heat；
Second throttle；
Evaporator；
Third throttle valve；
The first heating of user end, including the first heating pipeline to exchange heat with first condenser pipe；
The second heating of user end, including the second heating pipeline to exchange heat with second condenser pipe；
The compressor, the first condenser pipe, liquid phase branch, first throttle valve, the first pipeline, which are sequentially connected, logical constitutes liquid phase
Circuit；The compressor, the first condenser pipe, gas phase branch, the second pipeline, minor air cell, cold end nozzle, third pipeline,
Two throttle valves, evaporator, the 4th pipeline are sequentially connected logical composition gas phase circuit；The compressor, the first condenser pipe, gas phase
Branch, the second pipeline, minor air cell, hot end nozzle, the second condenser pipe, third throttle valve are sequentially connected logical composition heat supplying loop.
In above-mentioned technical proposal, it is preferred that be arranged on the path for being exported to the suction port of compressor of the 4th pipeline
There is the first branch, first branch passes through first pipeline.
In above-mentioned technical proposal, it is preferred that the third throttle valve, which is exported on the path of the suction port of compressor, to be arranged
There is the second branch, second branch passes through first pipeline.
The present invention is obtained as follows compared with prior art the utility model has the advantages that in this case, passes through setting vortex tube and the second condensation
Device, the refrigerant for coming out compressor flows into vortex tube, and cold end of a part of refrigerant through vortex tube further cools down
And original auto-cascade refrigeration is participated in, needed for another part is further heated up through the hot end of vortex tube to provide life heat source, from
And improve the refrigerating efficiency of system and the utilization rate of the energy.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of the Auto-cascade cycle dual temperature system of the embodiment of the present invention one；
Fig. 2 is the structural schematic diagram of the Auto-cascade cycle dual temperature system of the embodiment of the present invention two；
Wherein: 1, compressor；2, vortex tube；21, minor air cell；22, cold end nozzle；23, hot end nozzle；3, the first condenser；31,
First condenser pipe；4, the second condenser；41, the second condenser pipe；42, third throttle valve；5, gas-liquid separator；51, liquid phase
Branch；511, first throttle valve；52, gas phase branch；6, First Heat Exchanger；61, the first pipeline；62, the second pipeline；7, it second changes
Hot device；71, third pipeline；711, second throttle；72, the 4th pipeline；8, evaporator；9, the first heating of user end；91, first
Heating pipeline；10, the second heating of user end；101, the second heating pipeline.
Specific embodiment
By the technology contents of invention are described in detail, construction feature, are reached purpose and efficacy, simultaneously below in conjunction with embodiment
Cooperation attached drawing is described in detail.
Embodiment 1
As shown in Figure 1, Auto-cascade cycle dual temperature system includes compressor 1, vortex tube 2, the first condenser 3, the second condenser 4, gas-liquid
Separator 5, first throttle valve 511, First Heat Exchanger 6, the second heat exchanger 7, second throttle 711, evaporator 8, third throttling
Valve 42, the first heating of user end 9 and the second heating of user end 10.Wherein, vortex tube 2 includes minor air cell 21, is respectively communicated with whirlpool
The cold side outlet 22 of flow chamber 21 and hot end outlet 23.First condenser 3 has the first condenser pipe 31, and the second condenser 4 has
Second condenser pipe 41.Gas-liquid separator 5 has liquid phase branch 51 and gas phase branch 52.First Heat Exchanger 6 is internally provided with energy
The first pipeline 61 and the second pipeline 62 mutually to exchange heat.Second heat exchanger 7 is internally provided with the third pipeline 71 that can mutually exchange heat
With the 4th pipeline 72.The first heating of user end 9 includes the first heating pipeline 91 to exchange heat with the first condenser pipe 31, is absorbed
The heat of first condenser 3 release；The second heating of user end 10 includes the second heating to exchange heat with the second condenser pipe 41
Pipeline 101 absorbs the heat of the second condenser 4 release.
Compressor 1, minor air cell 21, cold end nozzle 22, the first condenser pipe 31, liquid phase branch 51, first throttle valve 511,
First pipeline 61 is sequentially connected logical composition liquid-phase loop；Compressor 1, minor air cell 21, cold end nozzle 22, the first condenser pipe 31,
Gas phase branch 52, the second pipeline 62, third pipeline 71, second throttle 711, evaporator 8, the 4th pipeline 72 are sequentially connected logical structure
At gas phase circuit；Compressor 1, minor air cell 21, hot end nozzle 23, the second condenser pipe 41, third throttle valve 42 are sequentially connected logical
Constitute heat supplying loop.
The working principle of the Auto-cascade cycle dual temperature system of embodiment 1 is as follows: mix refrigerant is (by least two-spot non-azeotropic working medium
Mix) gas that high temperature and pressure is formed after the compression of compressor 1, subsequently into the minor air cell 21 of vortex tube 2, a part
Refrigerant heats up the higher gas of formation temperature in minor air cell 21, then comes out from hot end nozzle 23 successively through the second condenser
4, third throttle valve 42 is returned again to heat supplying loop is formed in compressor 1, which can be used for heat supply of living, with
The second heating of user end 10 exchanges heat, and transfers heat to the second heating end 10；Another part refrigerant is in minor air cell 21
The gas-liquid mixture that high pressure low temperature is formed after cooling, then enters in the first condenser 3 from cold end nozzle 22, first condenser
3 exchange heat with the first heating of user end 9, and transfer heat to the first heating of user end 9, and then gas-liquid mixture enters gas
In liquid/gas separator 5, liquid phase refrigerant and vapor phase refrigerant are formed after the separation of gas-liquid separator 5, wherein liquid phase refrigerant is through liquid
Phase branch 51, first throttle valve 511 enter First Heat Exchanger 6 the first pipeline 61 in, vapor phase refrigerant through gas phase branch 52 into
Enter in the second pipeline 62 of First Heat Exchanger, the two exchanges heat in First Heat Exchanger 6, and the liquid phase refrigerant after heat exchange is direct
It is back in compressor 1, forms liquid-phase loop；Vapor phase refrigerant after heat exchange enters in the third pipeline 71 of the second heat exchanger 7,
Then enter in evaporator 8 through second throttle 711 and heat convection is carried out by evaporator 8 and the air of external environment, inhale
The heat of outside ambient air is received, temperature is increased, and is then exported the refrigerant that side comes out from evaporator 8 and is changed into second
In 4th pipeline 72 of hot device 7, temperature is further increased, after the refrigerant after then heating up comes out from the outlet of the 4th pipeline 72
It is again introduced into the first pipeline 61, absorbs heat again, temperature is increased again, is finally returned to compressor 1, is formed gas phase and is returned
Road.In addition, can also return directly in compressor 1 from the refrigerant that the outlet of the 4th pipeline 72 comes out, it is again introduced into first
It is, to reduce the temperature difference of itself and 1 entrance of compressor, to meet compression to further absorb heat in first pipeline 61 of heat exchanger 6
1 entrance of machine needs the demand overheated, Energy Efficiency Ratio is improved, therefore, in being exported on the path of 1 entrance of compressor for the 4th pipeline 72
The first pipeline 61 of First Heat Exchanger 6 is passed through in a settable bypass, the bypass.
In embodiment 1, vortex tube is arranged at compressor outlet, refrigerant is pre-chilled using vortex tube cold end,
It is heated up to refrigerant using vortex tube hot end come needed for supplying heating for residential area, the advantage of this configuration is to be able to achieve the energy
Reasonable utilization keep system more compact in addition, the volume of condenser can be reduced.
Embodiment 2
Embodiment 2 the difference from embodiment 1 is that, the position of vortex tube 2, the first condenser 3 and the second condenser 4 is adjusted
It is whole, it is flowed directly in the first condenser 3 by the compressed high-temperature high-pressure refrigerant of compressor 1, to give the first heating of user
9 supply heats of end, needed for the life heat source for meeting the first heating of user end 9；Secondly, the refrigerant of gas phase all the way passes through vortex tube
2 hot end is flow in the second condenser 4, to supply heat to the second heating of user end 10, meets the second heating of user end 10
Life heat source needed for, and the refrigerant that the cold end of vortex tube 2 comes out all the way participates in remaining self-cascade refrigeration system, such one
Come, compared to the scheme in embodiment 1, using the technical solution in embodiment 2, refrigeration effect is more preferable, and the utilization rate of the energy is more
It is high.
Specifically, the piping connection relationship of all parts of the Auto-cascade cycle dual temperature system of embodiment 2 is as follows:
Compressor 1, the first condenser pipe 31, liquid phase branch 51, first throttle valve 511, the first pipeline 61 are sequentially connected logical composition
Liquid-phase loop；Compressor 1, the first condenser pipe 31, gas phase branch 52, the second pipeline 62, minor air cell 21, cold end nozzle 22,
Three pipelines 71, second throttle 711, evaporator 8, the 4th pipeline 72 are sequentially connected logical composition gas phase circuit；Compressor 1, first
Condenser pipe 31, gas phase branch 52, the second pipeline 62, minor air cell 21, hot end nozzle 23, the second condenser pipe 41, third throttling
Valve 42 is sequentially connected logical composition heat supplying loop.
The working principle of the Auto-cascade cycle dual temperature system of embodiment 2 is as follows:
In the first condenser pipe 31 that the high-temperature high-pressure refrigerant come out from compressor 1 flows directly into the first condenser 3, and pass through
First condenser pipe 31 releases a large amount of heat, the first heating pipeline 91 at the first heating of user end 9 and the first condensation during this
Pipeline 31 carries out heat exchange, and absorbs the heat that the first condenser pipe 31 is released, to meet the life at the first heating of user end 9
Needed for heat source；Refrigerant after letting off heat becomes the gas-liquid mixture of cryogenic high pressure, and the gas-liquid mixture is through gas-liquid separator 5
Separation forms two branches of liquid phase refrigerant and vapor phase refrigerant, wherein liquid phase refrigerant is after the throttling of first throttle valve 511
It flowing in the first pipeline 61 of First Heat Exchanger 6, vapor phase refrigerant flows directly into the second pipeline 62 of First Heat Exchanger 6, and two
Person carries out heat exchange in First Heat Exchanger 6, and the liquid phase refrigerant after heat exchange returns directly in compressor 1, forms liquid phase and returns
Road；Vapor phase refrigerant after heat exchange enters in the minor air cell 21 of vortex tube 2, and a part of vapor phase refrigerant is after minor air cell 21 heats up
It comes out, is entered back into the second condenser pipe 41 of the second condenser 4 from the hot end nozzle 23 of vortex tube 2, and pass through the second condensation
Pipeline 41 releases a large amount of heat, the of the second heating pipeline 101 and the second condenser 4 at the second heating of user end 10 during this
Two condenser pipes 41 carry out heat exchange, and absorb the heat that the second condenser pipe 41 is released, to meet the second heating of user end
Needed for 10 life heat source, this partial gas phase refrigerant of heat is let off after the throttling of third throttle valve 42, again passes by the
One branch enters in the first condenser pipe 61 of the first condenser 6, eventually returns to form heat supply in compressor 1 after absorbing heat
Circuit；Another part vapor phase refrigerant comes out after minor air cell 21 cools down from the cold end nozzle 22 of vortex tube 2, enters back into second and changes
In the third pipeline 71 of hot device 7, enter in evaporator 8 after the throttling of second throttle 711 after absorbing heat, and pass through evaporator
8 carry out heat convection with outside air, absorb the heat of external environment, temperature is increased, subsequently into the second heat exchanger 7
It in 4th pipeline 72, further absorbs heat, temperature increases again, this some refrigerant after heating is again introduced into First Heat Exchanger 6
The first pipeline 61 in absorb heat again, temperature further increases, then from the first pipeline 61 outlet finally returned again to out to pressure
In contracting machine 1, gas phase circuit is formed.In addition, compressor 1 can also be returned directly to from the refrigerant that the outlet of the 4th pipeline 72 comes out
It is interior, be again introduced into the first pipeline 61 of First Heat Exchanger 6, entered to reduce it with compressor 1 to further absorb heat
The temperature difference of mouth meets the needs of 1 entrance of compressor needs overheat, and improves Energy Efficiency Ratio and is therefore exported to pressure in the 4th pipeline 72
Settable one first branch on the path of 1 entrance of contracting machine, first branch pass through the first pipeline 61 of First Heat Exchanger 6.Into one
Step, the refrigerant come out from the outlet of third throttle valve 42 can also return directly to be again introduced into first in compressor 1
It is, to reduce the temperature difference of itself and 1 entrance of compressor, to meet compression to further absorb heat in first pipeline 61 of heat exchanger 6
Machine entrance needs the demand overheated, Energy Efficiency Ratio is improved, therefore, in the path for being exported to 1 entrance of compressor of third throttle valve 42
Upper settable one second branch, second branch pass through the first pipeline 61 of First Heat Exchanger 6.
In embodiment 2, by vortex tube setting in First Heat Exchanger exit, refrigerant is carried out using vortex tube cold end pre-
It is cold, so that refrigerant is further decreased temperature before entering evaporator, refrigerating efficiency is improved, using vortex tube hot end to refrigerant
It heats up, can be used to condense the refrigerant in gas-liquid separator in gas phase circuit again after supplying needed for heating for residential area
Temperature, the final refrigerating efficiency for improving whole system.
In conclusion the technical solution in above-mentioned two embodiment can be promoted Auto-cascade cycle dual temperature system refrigerating efficiency and
The utilization rate of the energy.
The above embodiments merely illustrate the technical concept and features of the present invention, and its object is to allow person skilled in the art
Scholar cans understand the content of the present invention and implement it accordingly, and it is not intended to limit the scope of the present invention.It is all according to the present invention
Equivalent change or modification made by spirit, should be covered by the protection scope of the present invention.
Claims (5)
1. a kind of Auto-cascade cycle dual temperature system with vortex tube, for the refrigeration cycle of at least two-spot mixed non-azeotropic refrigerant,
It is characterized in that, comprising:
Compressor (1)；
Vortex tube (2) including minor air cell (21), is respectively communicated with the cold end nozzle (22) and hot end nozzle of the minor air cell (21)
(23)；
First condenser (3) has the first condenser pipe (31)；
Second condenser (4) has the second condenser pipe (41)；
Gas-liquid separator (5) has liquid phase branch (51) and gas phase branch (52)；
First throttle valve (511)；
First Heat Exchanger (6) is internally provided with the first pipeline (61) and the second pipeline (62) that can mutually exchange heat；
Second heat exchanger (7) is internally provided with the third pipeline (71) and the 4th pipeline (72) that can mutually exchange heat；
Second throttle (711)；
Evaporator (8)；
Third throttle valve (42)；
The first heating of user end (9), including the first heating pipeline (91) to exchange heat with first condenser pipe (31)；
The second heating of user end (10), including the second heating pipeline (101) to exchange heat with second condenser pipe (41)；
The compressor (1), minor air cell (21), cold end nozzle (22), the first condenser pipe (31), liquid phase branch (51),
One throttle valve (511), the first pipeline (61) are sequentially connected logical composition liquid-phase loop；The compressor (1), minor air cell (21),
Cold end nozzle (22), the first condenser pipe (31), gas phase branch (52), the second pipeline (62), third pipeline (71), the second throttling
Valve (711), evaporator (8), the 4th pipeline (72) are sequentially connected logical composition gas phase circuit；The compressor (1), minor air cell
(21), hot end nozzle (23), the second condenser pipe (41), third throttle valve (42) are sequentially connected logical composition heat supplying loop.
2. the Auto-cascade cycle dual temperature system according to claim 1 with vortex tube, it is characterised in that: the 4th pipeline (72)
The path for being exported to the compressor (1) entrance on be provided with bypass, first pipeline (61) is passed through in the bypass.
3. a kind of Auto-cascade cycle dual temperature system with vortex tube, for the refrigeration cycle of at least two-spot mixed non-azeotropic refrigerant,
It is characterized in that, comprising:
Compressor (1)；
Vortex tube (2) including minor air cell (21), is respectively communicated with the cold end nozzle (22) and hot end nozzle of the minor air cell (21)
(23)；
First condenser (3) has the first condenser pipe (31)；
Second condenser (4) has the second condenser pipe (41)；
Gas-liquid separator (5) has liquid phase branch (51) and gas phase branch (52)；
First throttle valve (511)；
First Heat Exchanger (6) is internally provided with the first pipeline (61) and the second pipeline (62) that can mutually exchange heat；
Second heat exchanger (7) is internally provided with the third pipeline (71) and the 4th pipeline (72) that can mutually exchange heat；
Second throttle (711)；
Evaporator (8)；
Third throttle valve (42)；
The first heating of user end (9), including the first heating pipeline (91) to exchange heat with first condenser pipe (31)；
The second heating of user end (10), including the second heating pipeline (101) to exchange heat with second condenser pipe (41)；
The compressor (1), the first condenser pipe (31), liquid phase branch (51), first throttle valve (511), the first pipeline
(61) it is sequentially connected logical composition liquid-phase loop；The compressor (1), the first condenser pipe (31), gas phase branch (52), second
Pipeline (62), minor air cell (21), cold end nozzle (22), third pipeline (71), second throttle (711), evaporator (8), the 4th
Pipeline (72) is sequentially connected logical composition gas phase circuit；The compressor (1), the first condenser pipe (31), gas phase branch (52),
Second pipeline (62), minor air cell (21), hot end nozzle (23), the second condenser pipe (41), third throttle valve (42) are sequentially connected
It is logical to constitute heat supplying loop.
4. the Auto-cascade cycle dual temperature system according to claim 3 with vortex tube, it is characterised in that: the 4th pipeline (72)
The path for being exported to the compressor (1) entrance on be provided with the first branch, first branch passes through described first
Pipeline (61).
5. the Auto-cascade cycle dual temperature system according to claim 3 with vortex tube, it is characterised in that: the third throttle valve
(42) it is exported on the path of the compressor (1) entrance and is provided with the second branch, second branch is by described the
One pipeline (61).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910052193.8A CN109916102A (en) | 2019-01-21 | 2019-01-21 | Auto-cascade cycle dual temperature system with vortex tube |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910052193.8A CN109916102A (en) | 2019-01-21 | 2019-01-21 | Auto-cascade cycle dual temperature system with vortex tube |
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| CN109916102A true CN109916102A (en) | 2019-06-21 |
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ID=66960487
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110821592A (en) * | 2019-11-08 | 2020-02-21 | 司徒健南 | Waste heat energy conversion system |
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|---|---|---|---|---|
| CN101135503A (en) * | 2007-09-25 | 2008-03-05 | 西安交通大学 | High temperature heat pump system with vortex tube |
| WO2011046458A1 (en) * | 2009-10-12 | 2011-04-21 | Oleszkiewicz Blazej | The compression heat pump with thermal accelerator |
| CN102230687A (en) * | 2011-04-27 | 2011-11-02 | 浙江大学 | Heating device using low-grade heat source |
| CN102287949A (en) * | 2011-06-14 | 2011-12-21 | 浙江大学 | Self-cascade system with vortex tube |
| CN102338496A (en) * | 2011-09-30 | 2012-02-01 | 浙江大学 | Multi-temperature-zone refrigeration system with vortex tube |
-
2019
- 2019-01-21 CN CN201910052193.8A patent/CN109916102A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101135503A (en) * | 2007-09-25 | 2008-03-05 | 西安交通大学 | High temperature heat pump system with vortex tube |
| WO2011046458A1 (en) * | 2009-10-12 | 2011-04-21 | Oleszkiewicz Blazej | The compression heat pump with thermal accelerator |
| CN102230687A (en) * | 2011-04-27 | 2011-11-02 | 浙江大学 | Heating device using low-grade heat source |
| CN102287949A (en) * | 2011-06-14 | 2011-12-21 | 浙江大学 | Self-cascade system with vortex tube |
| CN102338496A (en) * | 2011-09-30 | 2012-02-01 | 浙江大学 | Multi-temperature-zone refrigeration system with vortex tube |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110821592A (en) * | 2019-11-08 | 2020-02-21 | 司徒健南 | Waste heat energy conversion system |
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Application publication date: 20190621 |