CN108518912B - Multi-temperature-zone air-cooled refrigerator adopting pulse tube type free piston Stirling refrigerator - Google Patents
Multi-temperature-zone air-cooled refrigerator adopting pulse tube type free piston Stirling refrigerator Download PDFInfo
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- CN108518912B CN108518912B CN201810437951.3A CN201810437951A CN108518912B CN 108518912 B CN108518912 B CN 108518912B CN 201810437951 A CN201810437951 A CN 201810437951A CN 108518912 B CN108518912 B CN 108518912B
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- 238000007906 compression Methods 0.000 claims description 76
- 230000006835 compression Effects 0.000 claims description 74
- 238000005485 electric heating Methods 0.000 claims description 11
- 238000001816 cooling Methods 0.000 claims description 9
- 238000010257 thawing Methods 0.000 claims description 6
- 230000017525 heat dissipation Effects 0.000 claims description 4
- 230000000149 penetrating effect Effects 0.000 claims description 3
- 238000005057 refrigeration Methods 0.000 description 20
- 238000000034 method Methods 0.000 description 18
- 230000008569 process Effects 0.000 description 16
- 230000000694 effects Effects 0.000 description 10
- 239000007789 gas Substances 0.000 description 7
- 230000033001 locomotion Effects 0.000 description 7
- 235000013305 food Nutrition 0.000 description 6
- 238000011084 recovery Methods 0.000 description 6
- 238000010438 heat treatment Methods 0.000 description 5
- 238000007710 freezing Methods 0.000 description 4
- 230000008014 freezing Effects 0.000 description 4
- 238000007664 blowing Methods 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
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- 239000000696 magnetic material Substances 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 238000005086 pumping Methods 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 230000036760 body temperature Effects 0.000 description 2
- 235000013372 meat Nutrition 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 235000014102 seafood Nutrition 0.000 description 2
- 229910000976 Electrical steel Inorganic materials 0.000 description 1
- 102000004190 Enzymes Human genes 0.000 description 1
- 108090000790 Enzymes Proteins 0.000 description 1
- CBENFWSGALASAD-UHFFFAOYSA-N Ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 239000006096 absorbing agent Substances 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 238000009920 food preservation Methods 0.000 description 1
- 239000001307 helium Substances 0.000 description 1
- 229910052734 helium Inorganic materials 0.000 description 1
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical compound [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 244000005700 microbiome Species 0.000 description 1
- 235000016709 nutrition Nutrition 0.000 description 1
- 230000035764 nutrition Effects 0.000 description 1
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
- F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
-
- 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
- F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
-
- 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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D29/00—Arrangement or mounting of control or safety devices
- F25D29/005—Mounting of control devices
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
The invention relates to a multi-temperature-zone air-cooled refrigerator adopting a pulse tube type free piston Stirling refrigerator, which comprises a refrigerator box body, a refrigerating part and a control part, wherein the refrigerator box body is provided with at least one air chamber, an air delivery channel arranged outside the air chamber and an air return channel, an air supply port communicated with the air delivery channel and the air chamber and an air return port communicated with the air return channel and the air chamber are respectively arranged on the air chamber wall of the air chamber, the position of the air return port is higher than the position of the air supply port, the air delivery channel and the air return channel are both closed channels and communicated, the refrigerating part comprises the pulse tube type free piston Stirling refrigerator, a cold end heat exchanger and a cold end air supply device, the cold end heat exchanger is arranged on the cold end and is positioned at the joint of the air delivery channel and the air return channel, the cold end heat exchanger is separated from the air delivery channel and the air return channel, and the controller is respectively connected with an indoor temperature sensor, a cold end temperature sensor, an air chamber air supply valve and an air chamber air return valve, and the opening and closing of the air chamber valve.
Description
Technical Field
The invention belongs to the field of household appliances, and particularly relates to a multi-temperature-zone air-cooled refrigerator adopting a pulse tube type free piston Stirling refrigerator.
Background
With the improvement of the living standard of people, the freezing function of a common refrigerator (the temperature is higher than-18 ℃) can not meet the freezing requirement of people on some foods gradually, for example, some seafood needs to be stored better below-40 ℃. Taking meat food as an example, when the meat food is stored in a common refrigerator, the temperature of 7 ℃ is not higher than 2 days, the temperature of 0 ℃ is not higher than 5 days, and the time of 18 ℃ is not higher than 1 month. For foods which need to be stored for a long time, the lower the freezing temperature is, the more the growth and reproduction of microorganisms and the activity of enzymes can be inhibited, the less the nutrition loss is, and the better the preservation freshness is.
The traditional household refrigerator refrigeration generally adopts a single-stage vapor compression type throttling refrigeration system, and consists of four basic parts, namely a compressor, a condenser, a throttling part and an evaporator, wherein the four basic parts are connected together through pipelines to form a closed system. The system is filled with a certain amount of refrigerant, and the refrigerant is refrigerated in the system through four circulation processes of compression, condensation, throttling and evaporation. The refrigerator adopting vapor compression refrigeration has the advantages of high refrigeration speed, good refrigeration effect, mature technology, stable performance and long service life. When the refrigerator adopting vapor compression refrigeration works, the compressor is intermittently started and stopped under the control of the temperature controller. When the temperature in the refrigerator is higher than the set temperature, the compressor starts to refrigerate, the temperature in the refrigerator is reduced until the temperature in the refrigerator reaches a certain critical value below the set temperature, the compressor stops working, and the temperature in the refrigerator starts to rise. When the temperature rises to another critical value higher than the set temperature, the compressor starts to start working again. The above process is repeatedly circulated. Therefore, even though the refrigerator is in a stable state, there is a periodic fluctuation in the temperature in the cabinet, which is disadvantageous for some advanced food preservation like seafood. And the single-stage vapor compression throttling refrigeration system is difficult to realize the refrigeration temperature below minus 40 ℃ and cannot meet the temperature requirement for preserving some foods.
The Stirling refrigeration cycle consists of two isothermal and isovolumetric processes, with a theoretical cycle efficiency of Carnot efficiency. Relatively, the Stirling refrigeration technology has higher refrigeration efficiency under the low-temperature refrigeration working condition. The Stirling refrigerator adopts closed circulation of gas expansion refrigeration and is formed by communicating a compression unit and an expansion unit in a valveless manner. Helium is adopted as a refrigerating working medium, so that the ozone layer is not damaged, and the refrigerating technology is extremely environment-friendly. The free piston Stirling refrigerator has no complex pipeline system, the compressor and the expander are integrated together, and the free piston Stirling refrigerator has the advantages of less moving parts, no oil lubrication, difficult abrasion, high reliability, long service life, compact structure, light weight, high refrigeration efficiency and the like, and also has high temperature control precision, higher efficiency under full load and partial load, and can control the refrigeration capacity and the refrigeration temperature by adjusting input voltage.
Disclosure of Invention
The invention aims to provide a multi-temperature-zone air-cooled refrigerator using a novel efficient pulse tube type free piston Stirling refrigerator. The expansion cylinder of the free piston Stirling refrigerator is changed into a pulse tube of a pulse tube cold finger, a laminar flow deflector is arranged at the cold end of the pulse tube, and a secondary hot end heat exchanger is arranged at the hot end of the pulse tube. This modification combines the advantages of free piston Stirling and pulse tube refrigerators by eliminating pumping, shuttling and axial heat transfer losses from a low temperature expansion piston by eliminating the expansion piston moving at high frequencies at the cold and hot ends. The problem of acoustic power recovery of the pulse tube refrigerator is solved by arranging the shorter room temperature expansion piston at the hot end, so that the mechanical theory efficiency of the novel pulse tube free piston Stirling refrigerator is Carnot cycle efficiency when the acoustic power at the cold end is completely recovered. Meanwhile, the low-temperature expansion piston is omitted, so that the manufacturing difficulty of the refrigerator is reduced, and the quality of the whole refrigerator is reduced.
The invention provides a multi-temperature-zone air-cooled refrigerator adopting a pulse tube type free piston Stirling refrigerator, which has the characteristics that the refrigerator comprises a refrigerator body, a refrigerating part and a control part,
wherein the refrigerator body is provided with at least one air chamber, an air delivery channel and an air return channel, wherein the air delivery channel and the air delivery channel are arranged outside the air chamber, the air chamber wall of the air chamber is respectively provided with an air delivery port communicated with the air delivery channel and the air chamber, and an air return port communicated with the air return channel and the air chamber, the position of the air return port is higher than that of the air delivery port, the air delivery channel and the air return channel are both closed channels and communicated, the refrigerating part comprises a pulse tube type free piston Stirling refrigerator, a cold end heat exchanger and a cold end air supply device, the pulse tube type free piston Stirling refrigerator is provided with a cold finger, the cold finger is provided with a cold end and a hot end, the cold end heat exchanger is arranged on the cold end and is positioned at the joint of the air delivery channel and the air return channel, the cold end heat exchanger separates the air delivery channel and the air return channel, the air supply device is arranged in the air delivery channel or the air return channel and is positioned beside the cold end heat exchanger, the control part comprises a controller, an indoor temperature sensor, a cold end temperature sensor, an air chamber supply valve and an air chamber return valve, the air chamber air supply valve is arranged in the air supply opening, the air chamber air return valve is arranged in the air return opening, the indoor temperature sensor is arranged in the air chamber, the cold head temperature sensor is arranged on the cold end, the controller is respectively connected with the indoor temperature sensor, the cold head temperature sensor, the air chamber air supply valve and the air chamber air return valve, the controller respectively controls the opening and closing of the air chamber air supply valve and the air chamber air return valve, the pulse tube type free piston Stirling refrigerator comprises a linear motor, a compression unit, an expander unit and a frame, wherein the frame comprises a flange, a piston tube arranged in the flange and a base, the flange is in a disc shape, one side of the flange is also provided with a concentric small disc, the base is in a cylinder shape, one end of the base is connected with the other side of the flange, the other end of the base is a free end, the center line of the base coincides with the center line of the flange, the piston tube is a straight-through tube, one end opening is positioned at the outer side of the small disc, the other end opening is positioned in the base, a cylindrical piston cavity is formed in the piston tube and is used for accommodating a compression piston and an expansion piston of the refrigerator, a plurality of through holes penetrating through the wall of the piston tube are formed in the piston cavity, the linear motor comprises an outer yoke, an inner yoke and a rotor, the outer yoke and the inner yoke are respectively arranged on the machine frame, a gap is formed between the outer yoke and the inner yoke, the rotor is arranged in the gap, the compression unit is provided with a compression piston and a compression piston spring, the compression piston spring is fixedly connected with the machine frame through a connecting piece, the compression piston is arranged in the piston tube, one end of the compression piston is connected with the rotor and is connected with the compression piston spring, the other end of the compression piston is a free end of the expansion piston, the expansion piston is provided with an expansion piston rod, a first-stage heat exchanger, a second-stage heat exchanger, a hot-stage heat exchanger, a heat regenerator, a cold-stage heat exchanger and a cold-stage heat exchanger are arranged on the outer wall of the piston tube and are respectively arranged on the end face of the small disc, one end of the other end of the heat tube is connected with one end of the piston tube, the other end of the cold-stage heat exchanger is connected with the cold-stage heat exchanger, the heat exchanger is in a cylinder shape, the cold-stage heat exchanger is arranged in the cylinder, one end heat exchanger is arranged on the outer wall of the piston tube, and the heat exchanger is connected with the outer side of the compression piston tube, and the other end of the heat exchanger is connected with the compression piston tube through the compression piston spring and the compression piston.
In addition, in the multi-temperature zone refrigerator adopting the pulse tube type free piston Stirling refrigerator provided by the invention, the refrigerator is characterized by further comprising: and the defrosting device is arranged on the cold end heat exchanger.
In addition, in the multi-temperature zone refrigerator adopting the pulse tube type free piston Stirling refrigerator provided by the invention, the refrigerator also has the following characteristics: the defrosting device is an electric heating wire wound outside the cold end heat exchanger.
In addition, in the multi-temperature zone refrigerator adopting the pulse tube type free piston Stirling refrigerator provided by the invention, the refrigerator also has the following characteristics: wherein, the cold end heat exchanger is a fin type heat exchanger.
In addition, in the multi-temperature zone refrigerator adopting the pulse tube type free piston Stirling refrigerator provided by the invention, the refrigerator also has the following characteristics: the controller also comprises a control return air valve channel, a control temperature sensor channel, a control air inlet valve channel, a control cold end temperature sensor channel and a control cold end fan channel.
In addition, in the multi-temperature zone refrigerator adopting the pulse tube type free piston Stirling refrigerator provided by the invention, the refrigerator also has the following characteristics: wherein, the air return opening and the air supply opening are not arranged in the same air chamber wall.
In addition, in the multi-temperature zone refrigerator adopting the pulse tube type free piston Stirling refrigerator provided by the invention, the refrigerator also has the following characteristics: wherein, cold junction air supply arrangement is the fan.
In addition, in the multi-temperature zone refrigerator adopting the pulse tube type free piston Stirling refrigerator provided by the invention, the refrigerator is characterized by further comprising:
the hot end heat exchanger and the radiator fan are arranged on the hot end and are arranged in the same closed box body.
In addition, in the multi-temperature zone refrigerator adopting the pulse tube type free piston Stirling refrigerator provided by the invention, the refrigerator also has the following characteristics: the airtight box body is provided with an air inlet for introducing fresh air and an air outlet for realizing heat dissipation of the hot end.
Effects and effects of the invention
Compared with the existing refrigerator, the refrigerator has the beneficial effects that:
(1) By adopting the free piston Stirling refrigerator, the lowest refrigerating temperature of the refrigerator can reach-60 ℃, and the stroke of the compression piston can be regulated by changing the driving voltage, so that the refrigerating capacity and the refrigerating temperature are controlled. The food can be classified and preserved according to the requirements of different freezing temperatures.
(2) The coaxial pulse tube type free piston Stirling refrigerator provided by the invention eliminates a longer low-temperature expansion piston of the traditional free piston Stirling refrigerator, and replaces the longer low-temperature expansion piston with a work recovery expansion piston working in a shorter room temperature region. The expansion cylinder of the free piston Stirling refrigerator is changed into a pulse tube of a pulse tube cold finger, a laminar flow deflector is arranged at the cold end of the pulse tube, and a secondary hot end heat exchanger is arranged at the hot end of the pulse tube. This modification combines the advantages of free piston Stirling and pulse tube refrigerators by eliminating pumping, shuttling and axial heat transfer losses from a low temperature expansion piston by eliminating the expansion piston moving at high frequencies at the cold and hot ends. The problem of acoustic power recovery of the pulse tube refrigerator is solved by arranging the shorter room temperature expansion piston at the hot end, so that the mechanical theory efficiency of the novel pulse tube free piston Stirling refrigerator is Carnot cycle efficiency when the acoustic power at the cold end is completely recovered. Meanwhile, the low-temperature expansion piston is omitted, so that the manufacturing difficulty of the refrigerator is reduced, and the quality of the whole refrigerator is reduced.
Drawings
FIG. 1 is a schematic diagram of the refrigeration principle of a multi-temperature-zone air-cooled refrigerator employing a pulse tube type free piston Stirling refrigerator employed in the present invention;
FIG. 2 is a schematic cross-sectional view of a pulse tube type free piston Stirling refrigerator in accordance with an embodiment of the invention;
FIG. 3 is a schematic perspective view of a frame in an embodiment of the invention;
FIG. 4 is a view in the direction A of FIG. 3; and
fig. 5 is a cross-sectional view of C-C in fig. 4.
Detailed Description
In order to make the technical means, creation characteristics, achievement of the purposes and effects achieved by the present invention easy to understand, the following embodiments specifically describe the multi-temperature zone refrigerator adopting the pulse tube type free piston Stirling refrigerator of the present invention with reference to the accompanying drawings.
Examples
The multi-temperature-zone air-cooled refrigerator comprises a refrigerator body, a refrigerating part and a control part.
As shown in FIG. 1, the refrigerator body is provided with three box-shaped air chambers which are an air chamber I, an air chamber II and an air chamber III sequentially arranged from top to bottom, wherein the air chamber I, the air chamber II and the air chamber III are mutually independent and have rectangular cross sections.
The air delivery duct 23k is arranged outside the three air chambers, the air return duct 24k is arranged outside the three air chambers, and the air delivery duct 23k and the air return duct 24k are closed channels and are communicated.
The air supply chamber walls of the three air chambers are respectively provided with an air supply port communicated with the air supply channel and the inside of the air chambers and an air return port communicated with the air return channel and the inside of the air chambers, in the embodiment, the position of the air return port is higher than that of the air supply port, the position of the air supply port is close to the bottom of the air chambers, the air return port and the air supply port are not in the same air chamber wall, and the air return port and the air supply port are respectively arranged on two opposite side walls.
The air delivery duct 23k is respectively communicated with the air delivery openings of the air chamber I, the air chamber II and the air chamber III.
The return air duct 24k is respectively communicated with return air inlets of the air chambers I, II and III.
The refrigerating part comprises a pulse tube type free piston Stirling refrigerator 2k, a cold end fin heat exchanger 3k, a cold end fan 4k, an electric heating wire 5k, a hot end fin heat exchanger 6k, an air inlet 7k, a filter screen 8k, a hot end fan 9k and an air outlet 10k.
The pulse tube free piston Stirling cooler 2k has cold fingers with a cold end and a hot end.
The cold end fin heat exchanger 3k is arranged on the cold end and is positioned at the joint of the air delivery duct 23k and the air return duct 24k, and the cold end fin heat exchanger 3k separates the air delivery duct 23k and the air return duct 24k. The cold end fin heat exchanger 3k is wound with an electric heating wire 5k for defrosting.
The cold end fan 4k is disposed in the air delivery duct 23k at the front end of the cold end fin heat exchanger 3 k.
The hot end fin heat exchanger 6k is arranged on the hot end of the coaxial pulse tube type free piston Stirling refrigerator 2k, the hot end fin heat exchanger 6k, the hot end fan 9k and a refrigerator 2k body are arranged in the same closed box body, an air inlet 7k for introducing fresh air and an air outlet 10k for realizing hot end heat dissipation are arranged on the upper portion of the closed box body, a filter screen 8k is further arranged in the air inlet 7k, the hot end fan 9k is arranged at the tail portion of the refrigerator 2k body, and the air outlet 10k is opposite to the hot end fan 9k and is arranged on the side wall of the closed box body.
The control part comprises a controller 1k, an air chamber I temperature sensor 11k, an air chamber II temperature sensor 12k, an air chamber III temperature sensor 13k, a cold head temperature sensor 14k, a control return air valve channel 15k, a control temperature sensor channel 16k, a control inlet air valve channel 17k, a control cold end temperature sensor channel 18k, a control cold end fan channel 19k, a control heating wire 20k, a control refrigerator power line 21k, a control hot end fan 22k, an air chamber I air supply valve A, an air chamber II air supply valve B, an air chamber III air supply valve C, an air chamber I return air valve a, an air chamber II return air valve B, an air chamber III return air valve C, a hot end fan 9k and a cold end fan 4k.
The air supply valve A of the air chamber I, the air supply valve B of the air chamber II and the air supply valve C of the air chamber III are respectively arranged in the air supply openings of the air chamber I, the air chamber II and the air chamber III.
The air chamber I air return valve a, the air chamber II air return valve b and the air chamber III air return valve c are respectively arranged in the air inlets of the air chamber I, the air chamber II and the air chamber III.
The temperature sensor 11k of the air chamber I, the temperature sensor 12k of the air chamber II and the temperature sensor 13k of the air chamber III are respectively arranged in the air chamber I, the air chamber II and the air chamber III.
A coldhead temperature sensor 14k is provided on the cold end.
The controller 1k is connected with the controller 1k, the air chamber I temperature sensor 11k, the air chamber II temperature sensor 12k, the air chamber III temperature sensor 13k, the cold head temperature sensor 14k, the control return air valve channel 15k, the control temperature sensor channel 16k, the control inlet air valve channel 17k, the control cold end temperature sensor channel 18k, the control cold end fan channel 19k, the control heating wire 20k, the control refrigerator power line 21k, the control hot end fan 22k, the air chamber I air supply valve A, the air chamber II air supply valve B, the air chamber III air supply valve C, the air chamber I return air valve a, the air chamber II return air valve B, the air chamber III return air valve C and the refrigerator 2k respectively.
The controller 1k controls the opening and closing of the refrigerator 2k, the hot end fan 9k and the cold end fan 4k respectively, and the opening and closing of the valves of the air chamber I air supply valve A, the air chamber II air supply valve B, the air chamber III air supply valve C, the air chamber I return air valve a, the air chamber II return air valve B and the air chamber III return air valve C.
As shown in fig. 2, the coaxial pulse tube type free piston stirling cooler 2k includes a linear motor 1, a compression unit, an expander unit, a frame 50, and a housing 60.
As shown in fig. 3, 4, 5, the frame 50 includes a flange 52, a piston tube 51 provided in the flange 52 and a base 53,
the flange 52 is in a disc shape, a concentric small disc 521 is further arranged on one side of the flange, and a plurality of connecting through holes are uniformly formed in the flange 52.
The base 53 is cylindrical, one end is connected with one side of the flange 52, the other end is a free end, the center line of the base 53 coincides with the center line of the flange 52, a plurality of connecting screw holes are formed in the free end of the base 53, and in an embodiment, the base 53 is four supporting legs arranged around the center line of the flange 52.
The piston tube 51 is a straight tube, is disposed in the flange 52 and is coaxial with the flange 52, an opening at one end of the outer side is located at the outer side of the small disc 521, an opening at one end of the inner side is located in the base 53, a cylindrical piston cavity is formed in the piston tube 51, a plurality of through holes 511 perpendicular to the axis of the piston tube and penetrating through the wall of the piston tube are formed in the piston cavity, in an embodiment, the cross sections of the through holes 511 are circular arc grooves, and the number of the through holes is 3.
The linear motor 1 includes an outer yoke 11, an inner yoke 14, and a mover, the outer yoke 11, the inner yoke 14 are respectively provided on the frame with a gap therebetween, the mover is provided in the gap, and the mover includes a permanent magnet 13 and a permanent magnet holder 15.
As shown in fig. 1, the linear motor 1 mainly comprises an outer yoke 11, a coil 12, a permanent magnet 13, an inner yoke 14, a permanent magnet bracket 15, a mover comprising a permanent magnet 13, a permanent magnet bracket 15, a connecting piece 16, a fixing nut 18, a compression piston 19 and a compression piston plate spring 17 (only 1/3 of the mass of the plate spring is taken when calculating the mass of the mover), the permanent magnet bracket 15 being connected with the permanent magnet 13 and being connected with the compression piston 19 and the connecting piece 16 by threads. The outer yoke 11 and the inner yoke 14 are made of soft magnetic materials, commonly used materials such as electric pure iron, silicon steel sheets and the like, and the permanent magnet 13 is made of permanent magnetic materials, commonly used Ru-Fe-B and AlNi-Co permanent magnetic materials. The outer yoke 11, the coil 12, the permanent magnet 13, and the inner yoke 14 are all ring-shaped and coaxially arranged. The outer yoke 11 and the inner yoke 14 are respectively provided on the frame 50 with a gap therebetween, and the mover is provided in the gap.
When the coil is energized with direct current, the outer yoke 11 and the inner yoke 14 form a magnetic return line, thereby generating magnetic poles on the outer yoke 11 and the inner yoke 14. When alternating current is supplied to the coil, the permanent magnet 13 is subjected to alternating electromagnetic force to perform reciprocating rectilinear motion. When the permanent magnet 13 moves in a reciprocating linear motion, the compression piston 19 is driven to move in a reciprocating linear motion, and the compression piston plate spring 17 provides an axial reciprocating elastic force and radial support.
The compression unit comprises a connection 16, a compression piston plate spring 17, a fixing nut 18, a compression piston 19. The compression piston plate spring 17 is connected with the connecting piece 16 through the fixing nut 18, the compression piston plate spring 17 is fixedly connected with the frame 50 through the connecting piece, the compression piston 19 is arranged in the piston cavity, one end of the compression piston 19 is connected with the rotor and the compression piston spring 17, and the other end of the compression piston is a free end.
The expander unit comprises an expansion piston 21, an expansion piston plate spring 22, a piston rod 23, a primary hot side heat exchanger 26, a secondary hot side heat exchanger 33, a regenerator 25, a pulse tube 31, a cold side heat exchanger 24, a cold finger shell 35,
the primary hot-end heat exchanger 26 is cylindrical, is sleeved on the outer wall of the piston tube 51 and is arranged on the end face of the small disc 521, the primary hot-end heat exchanger 26 and the frame 50 are of a split structure, and the primary hot-end heat exchanger 26 is in interference fit with the outer wall of the piston tube 51.
One end of pulse tube 31 is connected to one end outside of piston tube 51, the other end is connected to cold side heat exchanger 24,
regenerator 25 is a circular cylinder with a circular cross section, and is arranged outside pulse tube 31, one end of which is connected to cold-end heat exchanger 24, and the other end of which is connected to primary hot-end heat exchanger 26.
The secondary hot end heat exchanger 33 is arranged in the pulse tube 31 and is positioned at the joint of the pulse tube 31 and the piston tube 51, the secondary hot end heat exchanger 33 and the frame 50 are of a split structure, and the secondary hot end heat exchanger 33 is in interference fit with the inner wall of the piston tube 51.
The expansion piston 21 is arranged in the piston tube 51, the expansion piston plate spring 22 is fixedly connected with the frame 50 through a connecting piece, one end of the piston rod 23 is connected with the expansion piston 21, the other end is connected with the expansion piston plate spring 22 after passing through the compression piston 19 and the compression piston plate spring 17,
the compression piston 19, the expansion piston 21 and the piston chamber form a compression chamber, the compression piston 19, the secondary hot side heat exchanger 33 and the piston chamber form an expansion chamber, and the expansion chamber and the compression chamber are coaxially arranged.
The cold finger shell 35 is arranged outside the primary hot end heat exchanger 26, the regenerator 25 and the cold end heat exchanger 24, the shell 60 is arranged outside the frame 50 and the expander unit 30, and the shell 60 and the cold finger shell 35 are connected with the frame 50 into a whole through connecting pieces.
The radiator 27 is located outside the primary hot side heat exchanger 26 and is disposed on the cold finger shell 35, and the primary hot side heat exchanger 26 transfers heat to the outside radiator 27 through the cold finger shell 35 and finally releases the heat to the environment.
The undamped dynamic vibration absorber unit 4 is connected with the housing 60 and is disposed outside the housing 60 for damping the refrigerator.
The movement process of the expansion piston and the compression piston and the gas flow process:
the expansion piston plate spring 22 is fixed to the piston rod 23, and the expansion piston 21 is connected to the piston rod 23.
The expansion piston 21 is driven purely pneumatically, and a refrigerating effect is generated by using the displacement phase difference between the expansion piston 21 and the compression piston 19, and the displacement of the expansion piston 21 leads the phase of the compression piston 19 by 70-100 degrees. Since the linear motor is excited by sinusoidal alternating current, the movement of the expansion piston 21 and the compression piston 19 is also sinusoidal continuous movement, but for the purpose of illustrating the working principle thereof, it is assumed that the expansion piston 21 and the compression piston 19 are intermittently and jumped in accordance with a cyclic law.
The acoustic wave compression process comprises the following steps: the expansion piston 21 stays at the top dead center and the compression piston 19 moves upwards from the bottom dead center, at this time, sound waves in the main compression cavity 29 are compressed and flow into the primary hot end heat exchanger 26 outside the cylinder, heat generated in the compression process is released to the primary hot end heat exchanger 26, and the primary hot end heat exchanger 26 transfers the heat to the radiator 27 outside through the outer shell, and finally the heat is released to the environment. Ideally, the cylinder and the outer shell are considered to be completely heat-conducting, and the heat exchange area of the primary hot-end heat exchanger 26 and the radiator 27 is infinite, so that the temperature of the working medium is kept unchanged. However, in practice isothermal compression is not possible and intermittent movement of the expansion piston 21 is not possible, the expansion piston 21 having begun to move downwards by the time the compression piston 19 moves upwards.
The heat release process of the heat regenerator comprises the following steps: the compression piston 19 moves to the upper dead point and then the expansion piston 21 moves downwards, and at the moment, the sound waves pass through the heat regenerator 25 and fully contact with the filler in the heat regenerator 25 for heat exchange, so that heat is released into the heat regenerator 25, at the moment, the temperature of the heat regenerator 25 is increased, and the temperature and the pressure of the sound waves are reduced. However, in the actual heat exchange process, the heat exchange process of the regenerator 25 is not constant, and complete heat exchange between the sound wave and the filler of the regenerator 25 is not possible.
Acoustic laminar flow process: the gas flows through cold side heat exchanger 24 and then enters pulse tube 31 in laminar flow through flow director 32, pushing the gas in pulse tube 31 toward expansion chamber 28. After the gas is extruded, the pressure and temperature rise. The generated heat is transferred radially to the primary hot side heat exchanger 26 through the secondary hot side heat exchanger 33 and finally to the radiator 27 and released to the environment. The gas in the expansion cavity 28 expands to do work, the expansion piston is assisted to push to the lower dead center, and the work recovery compression cavity is reduced, so that the effect of recovering sound work is achieved. In actual operation, the compression piston 19 does not stay at top dead center all the time, but moves downward with the expansion piston 21, but it is noted that the two do not move in the same direction but the expansion piston leads the compression piston by a certain phase angle.
And (3) an acoustic wave refrigeration process: the expansion piston 21 starts to move upwards from the bottom dead center to the top dead center, the compression piston 19 moves to the bottom dead center, the expansion piston 21 pushes the sound wave in the expansion cavity 28 back into the pulse tube 31, the gas expands and absorbs heat in the pulse tube, a refrigeration effect is generated, and the lowest refrigeration temperature is reached at the top of the pulse tube 31 close to the flow director 32. The generated cold is directed out to the cold environment through cold side heat exchanger 24. The sound wave working medium returns to the regenerator 25 along the original path and fully contacts with the filler for heat exchange, absorbs the heat in the regenerator 25, and returns to the main compression cavity 29 again to wait for the next compression. The temperature and pressure of the process sound wave rise and the regenerator 25 temperature falls. In practice, the expansion piston 21 does not reach the top dead center when the compression piston 19 reaches the bottom dead center, but is in the process of returning to the top dead center, but it still advances the compression piston 19 in the displacement wave phase.
The embodiment is suitable for the refrigerating temperature above 220K (-53 ℃) and can provide the refrigerating capacity of 50W-200W.
The controller 1k of the refrigerator can control the driving voltage of the pulse tube type stirling refrigerator 2k according to the actual load to realize the refrigerating temperature of each temperature zone. The cold end of the refrigerator is connected with the fin heat exchanger 3k, the cold end fan 4k respectively sends cold air with different temperatures to each air chamber through an air supply valve A, B, C with adjustable opening, return air flows back to the cold end of the refrigerator 2k through return air valves a, b and c, heat exchange is conducted by convection with the fin heat exchanger 3k of the cold end, and the temperature is reduced; the electric heating wires 5k are wound on the fin heat exchanger 3k, so that a defrosting function is realized; the hot end of the refrigerator is connected with the fin heat exchanger 6k, fresh air enters the hot end of the refrigerator through the filter screen 8k from the air inlet 7k, and the fan 9k passes through the air outlet 10k to the external environment so as to realize heat dissipation of the hot end; the control function is realized by the controller 1: six valve openings are respectively controlled by a control return air valve channel 15k and a control air inlet valve channel 17k, a control temperature sensor channel 16k transmits signals of an air chamber I temperature sensor 11k, an air chamber II temperature sensor 12k and an air chamber III temperature sensor 13k which are arranged in each air chamber, a control cold end temperature sensor channel 18k controls a cold end temperature sensor 14k of a cold end of a refrigerator, a control cold end fan channel 19k, a control heating wire 20k, a control refrigerator power wire 21k and a control hot end fan 22k respectively control the start and stop of a fan 4k, a heating wire 5k, a refrigerator 2k and a fan 9 k.
I the set temperature of the box body is 7 DEG C
II the set temperature of the box body is-18 DEG C
III the set temperature of the box body is-48 DEG C
The implementation procedure is briefly described as follows.
1. And (3) an initial cooling process:
when the temperature is initially lowered, the temperatures in the three boxes are all kept at the ambient temperature (23 ℃), the pulse tube type Stirling refrigerator 2k operates at the maximum, and the air inlet valve A, B, C and the air return valves a, b and c all maintain the maximum opening.
When the I box body reaches the target temperature (7-0.2 ℃, namely 6.8 ℃), the air inlet valve A and the air return valve a are closed, and the I box body is cooled. At this time, the intake valve B, C and the return valves b and c still maintain the maximum opening, and the refrigerator 2k still operates at the maximum power.
When the II box body reaches the target temperature (-18 ℃ to 0.2 ℃, namely-18.2 ℃), the air inlet valve B and the air return valve B are closed, and the II box body is cooled. At this time, the intake valve C and the return valve C still maintain the maximum opening, and the refrigerator 2k still operates at the maximum power.
When the III box body reaches the target temperature (-48-0.2 ℃, namely-48.2 ℃), the air inlet valve C and the air return valve C are closed, and the III box body is cooled. At this time, all the boxes are cooled, and the refrigerator 2k, the cold end fan 4k and the hot end fan 9k stop running.
In the primary cooling process, the air moisture content in the air duct is large, so that frost is seriously formed on the surface of the cold-end fin heat exchanger 3k, and the heating wire 3k is started to defrost after the primary cooling is finished, so that the heat transfer resistance of the cold-end fin heat exchanger 3k is prevented from being increased due to the fact that the frost layer is too thick.
2. The process of accurately controlling the temperature of each box body:
as external thermal loads penetrate, the temperature of each tank will gradually rise above the target temperature.
When the temperature of the III box body is higher than the set temperature of 0.2 ℃ (namely-47.8 ℃), firstly detecting whether the cold head temperature is higher than-53 ℃, if so, starting the refrigerator 2k and the hot end fan 9k, reducing the input power of the refrigerator 2k to-53 ℃ after the cold head temperature is reduced to the maximum input power, always keeping the cold head temperature to-53 ℃, opening the cold end fan 4k, opening an air inlet valve C and an air return valve C by 20% (the opening cannot be too large, otherwise, the air in the box body and the air in an air duct are mutually streamed, so that the temperature fluctuation in the box body is severe), blowing cold air with low temperature into the III box body, and when the box body temperature reaches-48.2 ℃, stopping the refrigerator 2k, and closing the air inlet valve C and the air return valve C. Because the heat transfer temperature difference between the cold side heat exchanger 3k and the air (typically 5 ℃) is considered, the cold head temperature cannot be reduced to-48 ℃ only when cooling the III box, otherwise the cold air temperature passing through the cold side fin heat exchanger 3k may be-43 ℃ only, and the temperature of the III box cannot be reduced to the target temperature. In addition, since the electric heating frost-containing process is performed after the initial cooling is completed, the cold head temperature is not lower than-53 ℃, without considering the control method in this case.
Similarly, when the temperature in the II box body is higher than the set temperature of 0.2 ℃ (namely-17.8 ℃), firstly detecting whether the cold head temperature is-23 ℃ (the heat exchange temperature difference of 5 ℃ is also taken here), if the temperature is higher than-23 ℃, starting the refrigerator 2k and the hot end fan 9k, reducing the input power of the refrigerator 2k and always keeping the cold head temperature to be-23 ℃ after the cold head temperature is reduced to-23 ℃, then starting the cold end fan 4k, starting the air inlet valve B and the air return valve B for 20 percent of opening, blowing cold air into the II box body, and stopping the refrigerator 2k and closing the air inlet valve B and the air return valve B when the box body temperature reaches-18.2 ℃; if the cold head temperature is detected to be lower than-23 ℃, the electric heating wire 5 is started, after the cold head temperature is quickly increased to-23 ℃, electric heating is stopped, the refrigerator 2k and the cold end fan 4k are operated, the input power of the refrigerator 2k is required to be always kept at-23 ℃, the air inlet valve B and the air return valve B are opened for 20% of opening, and cold air is blown into the II box body. It is noted that when the temperature of the cold head is detected to be lower than-23 ℃, the temperature of the cold head can be slowly waited to automatically rise to-23 ℃, but the temperature of the cold head is automatically raised for too long, the temperature of the II box body in the period of time can deviate from the set temperature greatly, and the accurate temperature control cannot be ensured. So that the temperature of the cold head is quickly raised to-23 ℃ by adopting the electric heating assistance.
When the temperature in the box I is higher than the set temperature of 0.2 ℃ (namely 7.2 ℃), firstly detecting whether the temperature of a cold head is 2 ℃ (the heat exchange temperature difference of 5 ℃ is also taken here), if the temperature is higher than 2 ℃, starting a refrigerator 2k and a hot end fan 9k, reducing the input power of the refrigerator 2k and always keeping the temperature of the cold head to be 2 ℃ after the temperature of the cold head is reduced to 2 ℃, then starting the cold end fan 4k, opening an air inlet valve A and an air return valve a by 20%, blowing cold air into the box I, and stopping the refrigerator 2k and closing the air inlet valve A and the air return valve a when the temperature of the box I reaches 6.8 ℃; if the temperature of the cold head is detected to be lower than 2 ℃, the electric heating wire 5k is started, after the temperature of the cold head is quickly increased to 2 ℃, the electric heating is stopped, the refrigerator 2k and the cold end fan 4k are operated, the input power of the refrigerator 2k is required to be always kept at the temperature of 2 ℃, and the air inlet valve A and the air return valve a are opened by 20% to blow cold air into the I box body.
Description:
when the III box body is precisely controlled in temperature, the cold head temperature is set to be minus 53 ℃, the purpose is to consider the heat transfer temperature difference of 5 ℃ between the cold end heat exchanger 3k and the air, and the purpose is to reduceLoss. Assuming that the cold head temperature is set to-80 ℃, the blown cold air is about-75 ℃, and the cold air with the temperature of-75 ℃ is used for cooling the target temperature of-48 DEG CThe case body is->The loss is too large, in addition, the input work required for reducing the cold head to-80 ℃ is larger, the refrigerating capacity is smaller, and the COP is lower. Comprehensively considering, the efficiency of keeping the temperature of the cold head at-53 ℃ is optimal when the temperature of the III box body is accurately controlled. Similarly, when the temperature of the I, II box body is precisely controlled, the efficiency of keeping the temperature of the cold head at 2 ℃ and-23 ℃ is optimal.
Summarizing:
when the temperature of the box body is higher than the set temperature by 0.2 ℃, the box body starts to be cooled. And stopping cooling the box body when the temperature of the box body is lower than the set temperature by 0.2 ℃.
Effects and effects of the examples
The pulse tube type free piston Stirling refrigerator of the embodiment eliminates a longer low-temperature expansion piston of the traditional free piston Stirling refrigerator and replaces the longer low-temperature expansion piston with a work recovery expansion piston working in a shorter room temperature area. The expansion cylinder of the free piston Stirling refrigerator is changed into a pulse tube of a pulse tube cold finger, a laminar flow deflector is arranged at the cold end of the pulse tube, and a secondary hot end heat exchanger is arranged at the hot end of the pulse tube. This modification combines the advantages of free piston Stirling and pulse tube refrigerators by eliminating pumping, shuttling and axial heat transfer losses from a low temperature expansion piston by eliminating the expansion piston moving at high frequencies at the cold and hot ends. The problem of acoustic power recovery of the pulse tube refrigerator is solved by arranging the shorter room temperature expansion piston at the hot end, so that the mechanical theory efficiency of the novel pulse tube free piston Stirling refrigerator is Carnot cycle efficiency when the acoustic power at the cold end is completely recovered. Meanwhile, the low-temperature expansion piston is omitted, so that the manufacturing difficulty of the refrigerator is reduced, and the quality of the whole refrigerator is reduced.
The above embodiments are preferred examples of the present invention, and are not intended to limit the scope of the present invention.
Claims (7)
1. A multi-temperature area air-cooled refrigerator adopting a pulse tube type free piston Stirling refrigerator is characterized by comprising the following components:
a refrigerator body, a refrigerating part and a control part,
wherein the refrigerator body is provided with at least one air chamber, an air delivery duct and an air return duct which are arranged outside the air chamber,
an air supply port communicating the air supply duct with the inside of the air chamber and an air return port communicating the air return duct with the inside of the air chamber are respectively arranged on the air chamber wall of the air chamber, the position of the air return port is higher than that of the air supply port,
the air delivery duct and the air return duct are both closed channels and are communicated,
the refrigerating part comprises a pulse tube type free piston Stirling refrigerator, a cold end heat exchanger and a cold end air supply device,
the pulse tube type free piston Stirling refrigerator has a cold finger having a cold end and a hot end,
the cold end heat exchanger is arranged on the cold end and positioned at the joint of the air delivery duct and the air return duct, the cold end heat exchanger separates the air delivery duct from the air return duct,
the air supply device is arranged in the air supply duct or the air return duct and is positioned beside the cold end heat exchanger,
the control part comprises a controller, an air chamber internal temperature sensor, a cold head temperature sensor, an air chamber air supply valve and an air chamber return valve,
the air chamber air supply valve is arranged in the air supply opening, the air chamber return valve is arranged in the air return opening,
the indoor temperature sensor is disposed in the wind chamber,
the cold head temperature sensor is arranged on the cold end,
the controller comprises a control return air valve channel, a control temperature sensor channel, a control air inlet valve channel, a control cold end temperature sensor channel and a control cold end fan channel, the controller is respectively connected with the indoor temperature sensor, the cold end temperature sensor, the air chamber air supply valve and the air chamber return air valve, the controller respectively controls the opening and closing of the air chamber air supply valve and the air chamber return air valve,
the pulse tube type free piston Stirling refrigerator comprises a linear motor, a compression unit, an expander unit and a frame,
wherein the frame comprises a flange, a piston tube arranged in the flange and a base,
the flange is in a disc shape, one side of the flange is also provided with a concentric small disc,
the base is in a cylinder shape, one end of the base is connected with the other side of the flange, the other end of the base is a free end, the center line of the base is coincident with the center line of the flange,
the piston tube is a straight-through tube, one end of the piston tube is provided with an opening positioned at the outer side of the small disc, the other end of the piston tube is provided with an opening positioned in the base,
the piston tube is internally provided with a cylindrical piston cavity for accommodating a compression piston and an expansion piston of the refrigerator, the piston cavity is provided with a plurality of through holes penetrating the wall of the piston tube,
the linear motor comprises an outer yoke, an inner yoke and a rotor, wherein the outer yoke and the inner yoke are respectively arranged on the frame, a gap is arranged between the outer yoke and the inner yoke, the rotor is arranged in the gap,
the compression unit is provided with a compression piston and a compression piston spring, the compression piston spring is fixedly connected with the frame through a connecting piece, the compression piston is arranged in the piston tube, one end of the compression piston is connected with the rotor and the compression piston spring, the other end of the compression piston is a free end,
the expander unit comprises an expansion piston, an expansion piston spring, an expansion piston rod, a primary hot end heat exchanger, a secondary hot end heat exchanger, a heat regenerator, a pulse tube and a cold end heat exchanger,
the primary hot end heat exchanger is cylindrical, is sleeved on the outer wall of the piston tube and is arranged on the end face of the small disc,
one end of the pulse tube is connected with one end of the outer side of the piston tube, the other end is connected with the cold end heat exchanger,
the heat regenerator is cylindrical and arranged at the outer side of the pulse tube, one end of the heat regenerator is connected with the cold end heat exchanger, the other end of the heat regenerator is connected with the primary hot end heat exchanger,
the secondary warm side heat exchanger is disposed within the pulse tube,
the expansion piston is arranged in the piston tube, the expansion piston spring is fixedly connected with the frame through a connecting piece,
one end of the expansion piston rod is connected with the expansion piston, the other end of the expansion piston rod passes through the compression piston and the compression piston spring and then is connected with the expansion piston spring,
the compression piston, the expansion piston and the piston chamber form a compression chamber,
the expansion piston, the secondary hot end heat exchanger and the piston cavity form an expansion cavity,
the cold end heat exchanger is a fin type heat exchanger.
2. The multi-temperature zone air cooled refrigerator employing a pulse tube type free piston stirling cooler of claim 1 further comprising:
and the defrosting device is arranged on the cold end heat exchanger.
3. The multi-temperature zone air cooled refrigerator employing a pulse tube type free piston stirling cooler of claim 2 wherein:
the defrosting device is an electric heating wire wound outside the cold end heat exchanger.
4. The multi-temperature zone air cooled refrigerator employing a pulse tube type free piston stirling cooler of claim 1 wherein:
wherein, the air return opening and the air supply opening are not in the same air chamber wall.
5. The multi-temperature zone air cooled refrigerator employing a pulse tube type free piston stirling cooler of claim 1 wherein:
wherein, cold junction air supply arrangement is the fan.
6. The multi-temperature zone air cooled refrigerator employing a pulse tube type free piston stirling cooler of claim 1 further comprising:
the hot end heat exchanger and the cooling fan are arranged on the hot end, and the hot end heat exchanger and the cooling fan are arranged in the same closed box body.
7. The multi-temperature zone air cooled refrigerator employing a pulse tube type free piston stirling cooler of claim 6 wherein:
the airtight box body is provided with an air inlet for introducing fresh air and an air outlet for realizing heat dissipation of the hot end.
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| CN115218602B (en) * | 2022-06-27 | 2023-08-11 | 青岛海尔生物医疗股份有限公司 | Method and device for controlling temperature of refrigerator, refrigerator and storage medium |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010196910A (en) * | 2009-02-23 | 2010-09-09 | Aisin Seiki Co Ltd | Cold box with refrigerator unit |
| CN105115219A (en) * | 2015-08-24 | 2015-12-02 | 上海理工大学 | Cryogenic refrigerator for combined pulse heat pipes of Stirling cryocooler |
| CN106052258A (en) * | 2016-07-21 | 2016-10-26 | 上海理工大学 | Refrigerator having multiple temperature zones |
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010196910A (en) * | 2009-02-23 | 2010-09-09 | Aisin Seiki Co Ltd | Cold box with refrigerator unit |
| CN105115219A (en) * | 2015-08-24 | 2015-12-02 | 上海理工大学 | Cryogenic refrigerator for combined pulse heat pipes of Stirling cryocooler |
| CN106052258A (en) * | 2016-07-21 | 2016-10-26 | 上海理工大学 | Refrigerator having multiple temperature zones |
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