CN108120043A - A kind of air vacuum spray penetration refrigerating plant and its method for realizing deep refrigerating - Google Patents
A kind of air vacuum spray penetration refrigerating plant and its method for realizing deep refrigerating Download PDFInfo
- Publication number
- CN108120043A CN108120043A CN201810063184.4A CN201810063184A CN108120043A CN 108120043 A CN108120043 A CN 108120043A CN 201810063184 A CN201810063184 A CN 201810063184A CN 108120043 A CN108120043 A CN 108120043A
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- Prior art keywords
- air
- low temperature
- expander
- turbo
- low
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
- F25B9/065—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders using pressurised gas jets
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/10—Adaptations for driving, or combinations with, electric generators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
- F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders
Abstract
The invention discloses a kind of air vacuum spray penetration refrigerating plant and its methods for realizing deep refrigerating, the deep refrigerating device includes turbo-expander, turbo-expander is by spiral case, turbine wheel shaft, the turbine wheel being located on turbine wheel shaft, and it is located at multiple de Laval noz(zle)s on spiral case, turbine wheel shaft one end fixed turbine impeller, the other end is connected with generator or other machine for doing work, the de Laval noz(zle) being located on turbo-expander spiral case is communicated with air, the outlet of turbo-expander low-pressure end is connected through connecting tube with low temperature chamber one end, the low temperature chamber other end is equipped with air passage, air hose end is equipped with vacuum pump.The present invention is under the swabbing action of vacuum pump, normal temperature and pressure air into turbo-expander may be expanded to very low pressure, can reach extremely low temperature, and the vacuum degree of vacuum pump is higher, the temperature of low temperature chamber is lower, meets the demand of the production for needing deep refrigerating or scientific research institution.
Description
Technical field
The present invention relates to production or the refrigerating fields of scientific research more particularly to air vacuum spray penetration refrigerating field.
Background technology
With the rapid development of economy, the space temperature required for some productions or scientific research is more and more lower, some is very
To reaching less than -180 DEG C.At present, the acquisition majority of this low temperature environment is realized by the dense-air refrigeration cycle of air.Its
Operation principle is that air becomes the gas of high temperature and pressure after compressor compresses, and the gas of high temperature and pressure passes through cooling first
Temperature-fall period is reduced to a certain temperature, enters back into turbo-expander and carries out expansion working, becomes the air of low-temp low-pressure；Low temperature is low
The air of pressure enters low temperature space heat absorption, the gas re-enter compressor compresses after heat absorption.So Xun Huan ensures that low temperature is empty
Between maintain a certain relatively low state of temperature always.
There are the shortcomings that following three aspects for above-mentioned cycling：(1) circulation air is compressed after low temperature space heat absorption, is had
Larger temperature rise, it is necessary to by entering back into turbo-expander after cooling procedure heat release, preferable temperature drop effect could be generated.
So the system must set air-cooling apparatus in compressor outlet.(2) turbo-expander outlet back pressure is unsuitable too low, generally
In normal pressure or so, the too low compression efficiency that can reduce compressor, and then reduce refrigerating efficiency；(3) due to air under normal pressure ,-
180 DEG C or so can liquefy, so, even if compressor delivery pressure is very high, it can theoretically go out turbo-expander
The air themperature of mouth reaches -200 DEG C or so of low temperature, is also irrealizable in practice.In order to overcome deep refrigerating process
In disadvantages mentioned above, the present invention proposes a kind of simple in structure, operational safety economy, and the air vacuum injection that cryogenic temperature is lower
Deep refrigerating device.
It is Chinese Patent Application No. 2017100062707, Chinese Patent Application No. with the most similar technology of the present invention
021382735 and Chinese Patent Application No. 012737747 disclosed in closed air cycle refrigerating plant.In Chinese Patent Application No.
In technology disclosed in 2017100062707, refrigeration system includes the centrifugal blower being interconnected by pipeline, expansion work recycles
Device returns cooler, with cold unit, and expansion work retracting device includes centrifugal compressor and expanding machine, centrifugal blower outlet and institute
Centrifugal compressor entrance to be stated by pipeline to be connected, centrifugal compressor outlet is connected with described time cooler hot-side inlet by pipeline,
It goes back to the outlet of cooler hot junction with the turboexpander inlet by pipeline to be connected, expander outlet is led to described with cold unit entrance
Piping is connected, and is connected with the outlet of cold unit with returning cooler cold-side inlet by pipeline, returns cooler cold side outlet and the centrifugation
Fans entrance is connected by pipeline.The technical shortcoming of the refrigeration machine is that refrigeration system cycles the state for requiring working medium in system
Parameter is metastable, and the refrigeration system that the technology proposes only is absorbed at cold unit with extraneous heat exchange and used
The heat of cold unit, without to the process of Environment release heat, this necessarily causes the heat in system higher and higher, final to make
Cold efficiency is more and more lower, makes cycling that cannot continue to carry out, thus is also impossible to reach the low temperature requirements proposed in patent document；
The air circulating refrigerating process and its device of a kind of producing powder disclosed in Chinese Patent Application No. 021382735, it is through pressure
The air of the compressed high temperature and pressure of contracting machine cools down after being cooled down by cooling device into turbine expander, but in the cooling
After the heat of device high temperature pressure-air is absorbed heat from the low-temperature airflow that refrigerating chamber exports, taken back further through air compressor
System, so the system is also that can not be achieved lasting refrigeration cycle；Chinese Patent Application No. 012737747 discloses one
Kind of open type cold air machine, it include a water cooler, a left drying box, a right drying box, a heat exchanger and
One air turbine expanding machine, during work and the compressed air of high temperature and pressure is by water cooler, and turbine is entered back into after cooling
Expander cools down.But in the apparatus, water cooler can not only waste substantial amounts of water, but also the sky of turbo-expander outlet
Gas can be because causing the icing of low temperature chamber surface or frosting containing moisture so that air temperature drop significantly reduces.
The content of the invention
In order to meet deep refrigerating requirement obtained by some productions or scientific research, the present invention provides a kind of using air as refrigeration
The air vacuum spray penetration refrigeration system of agent.
Present invention simultaneously provides the implementation methods of system depth refrigeration.
In order to achieve the above objectives, the present invention adopts the technical scheme that：
A kind of air vacuum spray penetration refrigeration system, it includes turbo-expander, and turbo-expander is by spiral case, turbine
Axis, the turbine wheel being located on turbine wheel shaft and the multiple de Laval noz(zle)s being located on spiral case, turbine wheel shaft one end fixed turbine leaf
Wheel, the other end are connected with generator or other machine for doing work, which is characterized in that the de Laval noz(zle) being located on turbo-expander spiral case
It being communicated with air, the outlet of turbo-expander low-pressure end is connected through connecting tube with low temperature chamber one end, and the low temperature chamber other end is equipped with air passage,
Air hose end is equipped with vacuum pump.
Above-mentioned low temperature chamber is adiabatic closed good low temperature chamber, and effect is that low temperature low speed flow absorbs in low temperature chamber
The heat of low temperature chamber maintains the low temperature environment of low temperature chamber, absorbs the air after low temperature chamber heat and is made by the suction of vacuum pump
With being discharged in atmospheric environment.
Air vacuum spray penetration refrigeration system of the present invention realizes that the method for deep refrigerating is：
First：Surrounding air realizes drop enthalpy under the ejector action of vacuum pump, by the de Laval noz(zle) in turbo-expander
Speedup becomes the Cryogenic air stream with high flow velocities, high negative；
Second：Under the promotion of high-speed low temperature low-pressure air stream, the impeller blade high-speed rotation of turbo-expander drives turbine
Externally acting or drive electrical power generators, the flow velocity with Airflow reduce axis, become the low speed low-temperature airflow of high negative pressure；
3rd：Low speed low-temperature airflow enters low temperature chamber, after absorbing the indoor heat of low temperature, in the swabbing action of vacuum pump
Under, it is discharged in outdoor environment, the inlet temperature of low temperature room air depends on the vacuum degree of vacuum pump, and the vacuum degree of vacuum pump is got over
Greatly, the negative pressure of low temperature chamber is bigger, then degrees of expansion of the air in turbo-expander is bigger, and the mechanical energy of output is more, turbine
The air themperature of expander outlet is lower, then also lower into the temperature of low temperature room air；The Air Temperature of low temperature chamber outlet
Degree is depending on the thermic load of low temperature chamber and the flow of vacuum pump, and thermic load is smaller, and the flow of vacuum pump is bigger, then low temperature chamber exports
Air themperature it is lower；The temperature of low temperature chamber can be approximately considered the arithmetic average equal to low temperature chamber inlet and outlet air themperature.
It is an advantage of the invention that：
1st, the air of the present invention into turbo-expander is ambient air, be may be expanded in expanding machine very low
Pressure can reach extremely low temperature, and the vacuum degree of vacuum pump is higher, and the temperature of low temperature chamber is lower.If vacuum degree can reach
0.0991MPa, then the inlet air temperature of low temperature chamber theoretically reach as high as less than -180 DEG C of low temperature, and due to negative pressure compared with
Height avoids the Liquefaction of air at lower temperatures, meets the demand of the production for needing deep refrigerating or scientific research institution.
2nd, the present invention during the work time, is not required to set special air-cooling apparatus.
3rd, process of refrigerastion energy-saving and environmental protection of the invention, safety.Air is completely harmless, air vacuum injection to environment
Refrigeration overcomes the insecurity of the environmental hazard and organic refrigerant using conventional refrigerants.
4th, present system composition is simple, and compact-sized, equipment cost is low, and service life is long, easy to maintain.
5th, high cooling efficiency of the present invention, the main power consumption of system are vacuum pump, and the output work of turbo-expander can roll over
Subtract the power consumption of partial vacuum pump, so as to greatly improve refrigerating efficiency.
Description of the drawings
Fig. 1 is the schematic diagram of the embodiment of the present invention
Fig. 2 is turbo-expander schematic diagram in the embodiment of the present invention
In figure：1- turbo-expanders, 2- generators, 3- low temperature chambers, 4- vacuum pumps, 5- air passages, 6- turbine wheel shafts, 7- scaling sprays
Pipe, the first de Laval noz(zle)s of 7a-, the second de Laval noz(zle)s of 7b-, the 3rd de Laval noz(zle)s of 7c-, the 4th de Laval noz(zle)s of 7d-, 8- turbine leafs
Wheel.
Specific embodiment
The workflow with the present invention illustrates its specific embodiment below in conjunction with the accompanying drawings.
As shown in Figure 1, the air vacuum spray penetration refrigeration system of the present invention, it includes turbo-expander 1, turbine expansion
Machine is implemented by spiral case, turbine wheel shaft 6, the turbine wheel 8 being located on turbine wheel shaft 6 and the multiple de Laval noz(zle)s 7 being located on spiral case
It is set in example there are four de Laval noz(zle), is the first de Laval noz(zle) 7a, the second de Laval noz(zle) 7b, the 3rd de Laval noz(zle) 7c and the 4th respectively
De Laval noz(zle) 7d；6 one end fixed turbine impeller 8 of turbine wheel shaft, the other end is connected with generator 2, as can be seen from Figure 1：It is located at
De Laval noz(zle) 7 on spiral case is communicated with air, and turbo-expander decompression brings out mouth and passes through through connecting pipe and 3 input end of low temperature chamber
Flanged joint, 3 other end of low temperature chamber are equipped with air passage 5, and there is vacuum pump 4 in 5 end of air hose by flanged joint.
Air vacuum spray penetration refrigeration system of the present invention realizes that the method for deep refrigerating is：
First：Surrounding air realizes drop under the ejector action of vacuum pump 4, by the de Laval noz(zle) 7 in turbo-expander
Enthalpy speedup becomes have high flow velocities, the air stream of low-pressure low-temperature；
Second：Under the promotion of high-speed low temperature low-pressure air stream, 8 high-speed rotation of turbine wheel of turbo-expander drives
The generator 2 being connected with turbine wheel shaft 6 generates electricity, and the flow velocity with Airflow reduces, and becomes the low speed low-temperature airflow of high negative pressure；
3rd：Low speed low-temperature airflow enters low temperature chamber 3, after absorbing the heat in low temperature chamber 3, makees in the suction of vacuum pump 4
It under, is discharged in outdoor environment, so that low temperature chamber 3 keeps very low temperature.
The design parameter of each component of air vacuum injection cooling device is determined below according to the thermic load of low temperature chamber, specifically
It is as follows：
If environment temperature is 27 DEG C, atmospheric pressure 0.1MPa, de Laval noz(zle) outlet temperature is -250 DEG C, low temperature chamber outlet
Temperature is -175 DEG C, and low temperature chamber thermic load is 1000W.
According to conditions above, the design parameter of each equipment and component is determined respectively：
The turbine wheel high-speed rotation of turbo-expander, 80% kinetic energy are converted into mechanical energy acting, be left 20% it is dynamic
It can make the temperature rise that turbo-expander exports, turbo-expander outlet temperature is low temperature chamber inlet temperature, then
T3=T2+0.2(T1-T2)=23+0.2 × (300-23)=78.4K (- 194.6 DEG C)
(1) vacuum pump type selecting parameter
The flow of vacuum pump can determine, as the following formula really according to the temperature of the thermic load and air of low temperature chamber disengaging low temperature chamber
It is fixed：
The vacuum degree of vacuum pump can as the following formula be determined according to low temperature chamber inlet temperature：
(absolute pressure) then vacuum pump
Vacuum degree be 0.0991MPa.
(2) design parameter of turbo-expander jet pipe
It is assumed that as shown in Fig. 2, setting 4 de Laval noz(zle)s altogether, then the mass flow of each jet pipe is：
The design parameter of each jet pipe should be：
De Laval noz(zle) intake area：f1=542.43mm2；
De Laval noz(zle) exit area：f2=469.89mm2；
De Laval noz(zle) throat section area：f0in=54.02mm2；
Throat section is to outlet length:L=92.44mm.
Specific calculating process is as follows：
Pressure P at de Laval noz(zle) throat sectionc=0.528P1=0.0528MPa>Pb=0.0009MPa；De Laval noz(zle)
Temperature at throat section
Speed at de Laval noz(zle) throat section
Air at de Laval noz(zle) throat section compares volume
Area at de Laval noz(zle) throat section
Diameter at de Laval noz(zle) throat section
Speed at de Laval noz(zle) outlet
Air at de Laval noz(zle) outlet compares volume
Area at de Laval noz(zle) outlet
Diameter at de Laval noz(zle) outlet
Tip angle is taken as 10 °, then the flaring segment length of de Laval noz(zle)If
Speed C at de Laval noz(zle) import section1=20m/s, the then area at de Laval noz(zle) import section
Diameter at de Laval noz(zle) import section
Claims (2)
1. a kind of air vacuum spray penetration refrigerating plant, it includes turbo-expander, and turbo-expander is by spiral case, turbine wheel shaft,
The turbine wheel being located on turbine wheel shaft and the multiple de Laval noz(zle)s being located on spiral case, turbine wheel shaft one end fixed turbine impeller, separately
One end is connected with generator or other machine for doing work, which is characterized in that be located at de Laval noz(zle) on turbo-expander spiral case with it is big
Gas phase is led to, and the outlet of turbo-expander low-pressure end is connected through connecting tube with low temperature chamber one end, and the low temperature chamber other end is equipped with air passage, air hose
End is equipped with vacuum pump.
2. a kind of method that deep refrigerating is realized using air vacuum spray penetration refrigerating plant described in claim 1, special
Sign is that step is as follows：
First：Surrounding air realizes drop enthalpy speedup under the ejector action of vacuum pump, by the de Laval noz(zle) in turbo-expander,
Become the Cryogenic air stream with high flow velocities, high negative；
Second：Under the promotion of high-speed low temperature low-pressure air stream, the impeller blade high-speed rotation of turbo-expander drives turbine wheel shaft pair
Outer acting or drive electrical power generators, the flow velocity with Airflow reduce, and become the low speed low-temperature airflow of high negative pressure；
3rd：Low speed low-temperature airflow enters low temperature chamber, after absorbing the indoor heat of low temperature, under the swabbing action of vacuum pump, and row
Into outdoor environment, so that low temperature chamber keeps very low temperature；The inlet temperature of low temperature room air depends on the true of vacuum pump
Reciprocal of duty cycle, the vacuum degree of vacuum pump is bigger, and the negative pressure of low temperature chamber is bigger, then degrees of expansion of the air in turbo-expander is bigger,
The mechanical energy of output is more, and the air themperature of turbo-expander outlet is lower, then is also got over into the temperature of low temperature room air
It is low；The air themperature of low temperature chamber outlet depends on the thermic load of low temperature chamber and the flow of vacuum pump, and thermic load is smaller, vacuum pump
Flow is bigger, then the air themperature of low temperature chamber outlet is lower.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810063184.4A CN108120043A (en) | 2018-01-23 | 2018-01-23 | A kind of air vacuum spray penetration refrigerating plant and its method for realizing deep refrigerating |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810063184.4A CN108120043A (en) | 2018-01-23 | 2018-01-23 | A kind of air vacuum spray penetration refrigerating plant and its method for realizing deep refrigerating |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN108120043A true CN108120043A (en) | 2018-06-05 |
Family
ID=62233166
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|---|---|---|---|
| CN201810063184.4A Withdrawn CN108120043A (en) | 2018-01-23 | 2018-01-23 | A kind of air vacuum spray penetration refrigerating plant and its method for realizing deep refrigerating |
Country Status (1)
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111188652A (en) * | 2020-03-11 | 2020-05-22 | 谢劲松 | Negative pressure impeller rotor engine |
| CN111735227A (en) * | 2019-01-16 | 2020-10-02 | 李华玉 | Second-class thermally-driven compression heat pump |
| CN112524833A (en) * | 2020-11-30 | 2021-03-19 | 中国电子科技集团公司第十六研究所 | Low-temperature turbine refrigerator |
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| Publication number | Priority date | Publication date | Assignee | Title |
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Application publication date: 20180605 |
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