CN108592481B - Multi-temperature-zone refrigerator adopting pulse tube type free piston Stirling refrigerator - Google Patents
Multi-temperature-zone refrigerator adopting pulse tube type free piston Stirling refrigerator Download PDFInfo
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- CN108592481B CN108592481B CN201810437993.7A CN201810437993A CN108592481B CN 108592481 B CN108592481 B CN 108592481B CN 201810437993 A CN201810437993 A CN 201810437993A CN 108592481 B CN108592481 B CN 108592481B
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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
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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
- F25B9/14—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
- F25B9/145—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 pulse-tube 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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/14—Compression machines, plants or systems characterised by the cycle used
Abstract
The refrigerator with the multiple temperature zones comprises a refrigerator body and a refrigerating system, wherein the refrigerator body comprises a refrigerating chamber, a freezing chamber and a temperature-changing chamber, the refrigerating chamber is positioned at the upper half part of the refrigerator body, and the freezing chamber and the temperature-changing chamber are positioned at the lower half part of the refrigerator; the refrigerating system is composed of a compression throttling refrigerating system and a Stirling refrigerator-heat pipe system, wherein the Stirling refrigerator-heat pipe system comprises a pulse tube type free piston Stirling refrigerator, a cold end gravity heat pipe, a hot end gravity heat pipe, a cold guide copper sleeve and a heat conduction copper sleeve, a condensation section pipeline of the hot end gravity heat pipe is upwards arranged on the inner side of the left wall surface of a refrigerator shell, an evaporation section pipeline of the cold end gravity heat pipe is downwards arranged on the rear wall surface and the left and right wall surfaces in the temperature-variable chamber, a condensation section of the cold end gravity heat pipe is connected with a cold head of the pulse tube type free piston Stirling refrigerator through the cold guide copper sleeve, and an evaporation section of the hot end gravity heat pipe is connected with.
Description
Technical Field
The invention belongs to the field of household appliances, and particularly relates to a multi-temperature-zone refrigerator adopting a pulse tube type free piston Stirling refrigerator.
Background
With the improvement of living standard of people, the freezing function of a common refrigerator (the temperature is higher than minus 18 ℃) can not meet the freezing requirement of people on some foods gradually, and for example, some seafood needs to be better preserved at the temperature of minus 40 ℃. Taking meat as an example, the time for preservation in a common refrigerator cannot exceed 2 days at 7 ℃ and 5 days at 0 ℃ and cannot exceed 1 month at-18 ℃. For food which needs to be preserved for a long time, the lower the freezing temperature is, the more the growth and the propagation 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 generally adopts a single-stage vapor compression type throttling refrigeration system, which consists of four basic parts, namely a compressor, a condenser, a throttling component and an evaporator, wherein all the 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 the vapor compression refrigeration has the advantages of high refrigeration speed, good refrigeration effect and mature technology, thereby having stable performance and long service life. When the refrigerator adopting the 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 work again. The above processes are repeated and circulated. Therefore, even if the refrigerator is in a steady state, there is a periodic fluctuation in the temperature in the cabinet, which is disadvantageous for some high-grade food preservation such as seafood. And the single-stage steam compression throttling refrigeration system is difficult to realize the refrigeration temperature below 40 ℃ below zero, and can not meet the temperature requirement for preserving some foods.
The heat pipe is a heat transfer element with extremely high heat conductivity, transfers heat through evaporation and condensation of liquid in the totally-enclosed vacuum pipe, and has high heat conductivity. The gravity heat pipe can only conduct heat in one direction, and the condensation section is higher than the evaporation section. When the gravity heat pipe works, working liquid in the gravity heat pipe absorbs heat and is vaporized into steam in the evaporation section, the steam rises to the cooling section to release heat and is condensed into liquid again, and then the liquid flows back to the evaporation section by means of gravity. The heat pipe used in the invention is a two-phase closed thermosiphon (gravity heat pipe).
The Stirling refrigeration cycle consists of two isothermal processes and an isochoric process, and the theoretical cycle efficiency of the Stirling refrigeration cycle is Carnot efficiency. Relatively speaking, 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 without a valve. Helium is adopted as a refrigerating working medium, so that the damage to an ozone layer is avoided, 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, the free piston Stirling refrigerator has the advantages of few moving parts, oil-free lubrication, low possibility of abrasion, high reliability, long service life, compact structure, light weight, high refrigeration efficiency and the like, and the free piston Stirling refrigerator also has the advantages of high temperature control precision, high efficiency under full load and partial load, and can control the refrigeration capacity and the refrigeration temperature by adjusting input voltage.
The invention patent 'multi-temperature zone refrigerator' of application number 2016105783878 adopts the stirling refrigerator to realize the functions of high temperature control precision, good environmental adaptability and small humidity and temperature fluctuation of the wine cabinet, but the expansion piston of the traditional stirling refrigerator still has the defects of pumping loss, shuttle loss, axial heat conduction loss and the like caused by high-frequency motion of a cold end and a hot end.
Disclosure of Invention
The invention aims to provide a multi-temperature-zone refrigerator using a novel efficient pulse tube type free piston Stirling refrigerator. The expansion cylinder of the free piston Stirling refrigerator becomes a pulse tube of a pulse tube cold finger, a laminar flow guider 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. The change combines the advantages of the free piston Stirling refrigerator and the pulse tube refrigerator, and eliminates pumping loss, shuttle loss and axial heat conduction loss caused by the low-temperature expansion piston by eliminating the expansion piston which moves at a high frequency at a cold end and a hot end. The problem of sound power recovery of the pulse tube refrigerator is solved by arranging the shorter room-temperature expansion piston at the hot end, and therefore when the sound power of the cold end is completely recovered, the theoretical efficiency of the novel pulse tube type free piston Stirling refrigerator is Carnot cycle efficiency. Meanwhile, the low-temperature expansion piston is eliminated, so that the manufacturing difficulty of the refrigerating machine is reduced, and the quality of the whole machine is reduced.
The invention provides a multi-temperature-zone refrigerator adopting a pulse tube type free piston Stirling refrigerator, which is characterized by comprising a refrigerator body and a refrigerating system.
The refrigerator body comprises a refrigerating chamber, a freezing chamber and a temperature-changing chamber, wherein the refrigerating chamber is positioned at the upper half part of the refrigerator body, and the freezing chamber and the temperature-changing chamber are positioned at the lower half part of the refrigerator; the refrigerating system consists of a compression throttling refrigerating system and a free piston Stirling refrigerator-heat pipe system, wherein the free piston Stirling refrigerator-heat pipe system comprises a pulse tube type free piston Stirling refrigerator, a cold end gravity heat pipe, a hot end gravity heat pipe, a cold guide copper sleeve and a heat conduction copper sleeve, a condensation section pipeline of the hot end gravity heat pipe is upwards arranged on the inner side of the left wall surface of a refrigerator shell, an evaporation section pipeline of the cold end gravity heat pipe is downwards arranged on the rear wall surface and the left and right wall surfaces in the temperature-variable chamber, a condensation section of the cold end gravity heat pipe is connected with a cold head of the pulse tube type free piston Stirling refrigerator through the cold guide copper sleeve, an evaporation section of the hot end gravity heat pipe is connected with the hot end of the pulse tube type free piston Stirling refrigerator through the heat conduction copper sleeve, the pulse tube, the frame comprises a flange, a piston pipe 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 cylindrical 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 central line of the base is superposed with the central line of the flange, the piston pipe is a straight-through pipe, an opening at one end of the piston pipe is positioned outside the small disc, an opening at the other end of the piston pipe is positioned in the base, a cylindrical piston cavity is arranged in the piston pipe and used for accommodating a compression piston and an expansion piston of a refrigerator, a plurality of through holes penetrating through the pipe wall of the piston pipe are arranged on 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 frame, a gap is arranged between the outer yoke and the inner yoke, the compression piston is arranged in a 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, the expander unit comprises an expansion piston, an expansion piston spring, an expansion piston rod, a first-stage hot end heat exchanger, a second-stage hot end heat exchanger, a heat regenerator, a pulse tube and a cold end heat exchanger, the first-stage hot end heat exchanger is cylindrical, is sleeved on the outer wall of the piston tube and is arranged on the end face of a small circular disc, one end of the pulse tube is connected with one end of the outer side of the piston tube, the other end of the pulse tube is connected with the cold end heat exchanger, the heat regenerator is cylindrical and is arranged on 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 second-stage hot end, the other end of the expansion piston 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 cavity form a compression cavity, and the expansion piston, the secondary hot end heat exchanger and the piston cavity form an expansion cavity.
The refrigerator with multiple temperature zones, which is provided by the invention and adopts the pulse tube type free piston Stirling refrigerator, can also have the following characteristics: the heat-conducting copper sleeve is a circular copper sleeve, an opening at one end of the heat-conducting copper sleeve is connected with a cold head of the pulse tube type free piston Stirling refrigerator, heat-conducting silicone grease is coated between the inner side of the circular copper sleeve and the cold head of the pulse tube type free piston Stirling refrigerator, and a circular groove is formed in the circular copper sleeve so that a heat-conducting working medium flows in the circular groove to fully exchange heat; two cold-conducting small holes communicated with the circular groove are formed in the side face of the circular copper sleeve.
In addition, the refrigerator with multiple temperature zones, which is provided by the invention and adopts the pulse tube type free piston Stirling refrigerator, can also have the following characteristics: the heat-conducting copper sleeve is an annular copper sleeve, heat-conducting silicone grease is coated between the inner surface of the annular copper sleeve and the hot end of the pulse tube type free piston Stirling refrigerator, and an annular groove is formed in the annular copper sleeve, so that a heat-conducting working medium flows in the annular groove to fully exchange heat; two heat conduction small holes communicated with the annular groove are formed in the side face of the annular copper sleeve.
In addition, the refrigerator with multiple temperature zones, which is provided by the invention and adopts the pulse tube type free piston Stirling refrigerator, can also have the following characteristics: wherein the refrigerating temperature range of the temperature-changing chamber is-60-10 ℃, and the temperature-changing chamber is provided with cold energy by a pulse tube type free piston Stirling refrigerator; the pulse tube type free piston Stirling refrigerator is an integral free piston Stirling refrigerator driven by a linear motor, the pulse tube type free piston Stirling refrigerator is installed in the middle of the left side of the refrigerator, a damping block is fixed at the tail of the pulse tube type free piston Stirling refrigerator, and the damping block faces to a back plate of a refrigerator body.
In addition, the refrigerator with multiple temperature zones, which is provided by the invention and adopts the pulse tube type free piston Stirling refrigerator, can also have the following characteristics: the cold-end gravity heat pipe comprises a first cold-end heat pipe and a second cold-end heat pipe, the first cold-end heat pipe and the second cold-end heat pipe are respectively connected with a first cold guide small hole and a second cold guide small hole on the side surface of the cold guide copper sleeve, a cold-end gravity heat pipe pipeline inclines downwards at an angle of 15 degrees, and a working medium used in the cold-end gravity heat pipe pipeline is R170; the hot end gravity heat pipe comprises a first hot end heat pipe and a second hot end heat pipe, the first hot end heat pipe and the second hot end heat pipe are respectively connected with a first heat conduction small hole and a second heat conduction small hole on the side surface of the heat conduction copper sleeve, and a hot end gravity heat pipe pipeline inclines downwards by 10 degrees.
In addition, the refrigerator with the multiple temperature zones, which is provided by the invention and adopts the pulse tube type free piston Stirling refrigerator, is characterized by further comprising a fluid director which is arranged at one end of the pulse tube and is positioned in the pulse tube.
In addition, the refrigerator with multiple temperature zones, which is provided by the invention and adopts the pulse tube type free piston Stirling refrigerator, can also have the following characteristics: the cold end heat exchanger and the heat regenerator are also provided with first filter layers which are cylindrical and made of stainless steel wire meshes.
In addition, the refrigerator with multiple temperature zones, which is provided by the invention and adopts the pulse tube type free piston Stirling refrigerator, can also have the following characteristics: wherein, the heat regenerator is cylindrical and is made of polyester films.
Action and Effect of the invention
Compared with the existing refrigerator, the invention has the beneficial effects that:
(1) due to the adoption of the free piston Stirling refrigerator, the lowest refrigerating temperature of the refrigerator can reach-60 ℃, and the stroke of the compression piston can be adjusted 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 free piston Stirling is combined with the gravity heat pipe, so that the problems of cold conduction and heat dissipation of the free piston Stirling are effectively solved, the free piston Stirling is tightly combined with the refrigerator body, the heat transfer efficiency is improved, the installation is simple, and the internal volume of the refrigerator body is not occupied.
(3) The coaxial pulse tube type free piston Stirling refrigerator cancels the longer low-temperature expansion piston of the traditional free piston Stirling refrigerator and is replaced by the work recovery expansion piston working in a shorter room temperature area. The expansion cylinder of the free piston Stirling refrigerator becomes a pulse tube of a pulse tube cold finger, a laminar flow guider 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. The change combines the advantages of the free piston Stirling refrigerator and the pulse tube refrigerator, and eliminates pumping loss, shuttle loss and axial heat conduction loss caused by the low-temperature expansion piston by eliminating the expansion piston which moves at a high frequency at a cold end and a hot end. The problem of sound power recovery of the pulse tube refrigerator is solved by arranging the shorter room-temperature expansion piston at the hot end, and therefore when the sound power of the cold end is completely recovered, the theoretical efficiency of the novel pulse tube type free piston Stirling refrigerator is Carnot cycle efficiency. Meanwhile, the low-temperature expansion piston is eliminated, so that the manufacturing difficulty of the refrigerating machine is reduced, and the quality of the whole machine is reduced.
Drawings
FIG. 1 is a schematic external view of a pulse tube type free piston Stirling cryocooler in use with the present invention.
Fig. 2 is a schematic diagram of a cold-end cold-conducting copper sleeve of a pulse tube type free piston stirling cryocooler used in the invention.
Fig. 3 is a schematic diagram of a hot-end heat-conducting copper sleeve of a pulse tube type free piston stirling cooler used in the invention.
FIG. 4 is a schematic diagram of the assembly of the pulse tube type free piston Stirling refrigerator, the cold conducting copper sleeve and the heat conducting copper sleeve adopted by the invention.
Fig. 5 is a schematic view of the assembly of the pulse tube type free piston stirling cooler and gravity assisted heat pipe system of the present invention.
FIG. 6 is a schematic view of the assembly of the compression-throttling refrigeration system, the pulse tube type free piston Stirling refrigerator and the gravity assisted heat pipe system of the present invention.
FIG. 7 is a front view of the refrigeration system and refrigerator cabinet assembly of the present invention.
Figure 8 is a rear view of the refrigeration system and refrigerator cabinet assembly of the present invention.
Fig. 9 is an external view of the refrigerator of the present invention.
Fig. 10 is a schematic view illustrating an operation principle of the multi-temperature zone refrigerator of the present invention.
Fig. 11 is a schematic cross-sectional view of a pulse tube type free piston stirling cooler in an embodiment of the invention.
Fig. 12 is a perspective view of a frame in an embodiment of the invention.
Fig. 13 is a view from a in fig. 12.
Fig. 14 is a cross-sectional view C-C of fig. 13.
Detailed Description
In order to make the technical means, creation features, achievement purposes and effects of the invention easy to understand, the following embodiments specifically describe the multi-temperature-zone refrigerator adopting the pulse tube type free piston stirling cryocooler in combination with the accompanying drawings.
Examples
As shown in fig. 1 to 9, a multi-temperature-zone refrigerator combining a stirling cryocooler and compression throttling refrigeration includes a refrigerator body 700 and a refrigeration system. The refrigerator cabinet 700 includes a refrigerator housing 706, a display 707, a refrigerator door 708, and a thermal insulation layer 705. The inner space of the refrigerator body is provided with a refrigerating chamber 701 which is positioned at the upper half part of the refrigerator, a freezing chamber 703 which is positioned at the right side of the lower half part of the refrigerator, a temperature changing chamber 702 which is positioned at the left side of the lower half part of the refrigerator, and each chamber is internally provided with an object placing plate 704. The display screen 707 is connected to the controller 800, and can display the temperature in each refrigeration chamber, and can also control the operating frequency of the inverter compressor 608 and the input voltage of the free-piston stirling cryocooler 100, thereby effectively controlling the refrigeration temperature in each chamber.
The refrigeration system includes a compression-throttling refrigeration system 600 and a free-piston stirling cooler-heat pipe system 500. The compression throttle refrigeration system 600 includes: the system comprises an inverter compressor 608, a condenser 604, a dry filter 601, a capillary tube 607, a freezing chamber liquid collector 606, a freezing chamber evaporator 605, a refrigerating chamber liquid collector 603 and a refrigerating chamber evaporator 602. The inverter compressor 608 is positioned at the bottom of the refrigerator, and a vent is arranged at the position of the inverter compressor at the rear side of the refrigerator, so that heat generated by the compressor can be conveniently discharged to the environment; the condenser 604 is located on the right side of the refrigerator, is mounted inside the refrigerator housing 706, and can transfer heat to the environment through the housing; the dry filter 601 is located at the end of the evaporator 604, connecting the evaporator 604 and the capillary tube 607; the other end of the capillary tube 607 is connected with a freezing chamber evaporator 605, and the freezing chamber evaporator 605 is positioned on the right side of the lower half part of the refrigerator and is used for providing cold energy for the freezing chamber 703; the freezing chamber evaporator 605 and the refrigerating chamber evaporator 602 are connected, and the refrigerating chamber evaporator 602 is arranged at the upper half part of the refrigerator to provide cold energy for the refrigerating chamber 701; the refrigerating compartment liquid trap 603 and the freezing compartment liquid trap 606 are located at inlet ends of the refrigerating compartment evaporator 602 and the freezing compartment evaporator 605, respectively.
As shown in fig. 4 and 5, the free piston stirling cooler-heat pipe system 500 is composed of a free piston stirling cooler system 400 and a heat pipe system, and the free piston stirling cooler system 400 includes a pulse tube type free piston stirling cooler 100, a cold-conducting copper sleeve 200 and a heat-conducting copper sleeve 300. The heat pipe system comprises a cold-end gravity heat pipe and a hot-end gravity heat pipe, wherein the cold-end gravity heat pipe is composed of a first cold-end heat pipe 503 and a second cold-end heat pipe 504, and the hot-end gravity heat pipe is composed of a first hot-end heat pipe 501 and a second hot-end heat pipe 502. For normal operation, the pipes of the first cold-end heat pipe 503 and the second cold-end heat pipe 504 which are cold-conducting are inclined downward at an angle of 15 °, and the pipes of the first hot-end heat pipe 501 and the second hot-end heat pipe 502 which are heat-conducting are inclined downward at an angle of 10 °. The pulse tube type free piston Stirling refrigerator 100 is arranged on the middle part of the refrigerator to the left, and can be conveniently connected with a first hot end heat pipe 501, a second hot end heat pipe 502, a first cold end heat pipe 503 and a second cold end heat pipe 504. Bolts 102 may secure the damper block 101 of the refrigerator to the end of the pulse tube type free piston stirling cooler 100.
The working medium used in the first hot end heat pipe 501 and the second hot end heat pipe 502 is R600a, and is distributed on the upper half part of the left side surface of the refrigerator, the lower end of the inner side of the refrigerator shell 706 is respectively connected with the first heat conducting small hole 301 and the second heat conducting small hole 302 on the heat conducting copper sleeve 300, and the working medium is used for dissipating heat of the hot end 103 of the free piston Stirling refrigerator 100; the working medium used in the first cold-end heat pipe 503 and the second cold-end heat pipe 504 is R170, and is folded and distributed at the inner side of the temperature-changing chamber 702, the upper ends of the working medium are respectively connected with the first cold-guiding small hole 202 and the second cold-guiding small hole 203 on the cold-guiding copper sleeve, and the cold energy generated by the cold head 104 of the free-piston Stirling refrigerator 100 is transmitted into the temperature-changing chamber 702. Grooves are formed in the cold conducting copper sleeve 200 and the heat conducting copper sleeve 300, so that the working medium flows in the grooves to perform phase change heat exchange.
As shown in fig. 2, the cold-conducting copper bush 200 is a circular copper bush, one end of the cold-conducting copper bush is provided with an opening and is connected with the cold head 104 of the free-piston stirling cryocooler 100, heat-conducting silicone grease is coated between the inner side of the circular copper bush and the cold head 104 of the free-piston stirling cryocooler 100, and a circular groove 201 is formed in the circular copper bush, so that the heat-conducting working medium R170 flows in the circular groove 201 to fully exchange heat; the side surface of the round copper sleeve is provided with a first cold-conducting small hole 202 and a second cold-conducting small hole 203 which are communicated with the circular groove 201.
As shown in fig. 3, the heat-conducting copper bush 300 is an annular copper bush, heat-conducting silicone grease is coated between the inner surface of the annular copper bush and the hot end 103 of the free piston stirling cryocooler 100, and an annular groove 303 is formed in the annular copper bush, so that the heat-transferring working medium R600a flows in the annular groove 303 to exchange heat sufficiently; the side surface of the annular copper sleeve is provided with a first heat conduction small hole 301 and a second heat conduction small hole 302 which are communicated with the annular groove 303.
As shown in fig. 10, in the compression-throttling refrigeration system 600, a working medium is compressed by the variable frequency compressor 608 to become high-temperature high-pressure gas, flows into the condenser 604 from the outlet of the compressor 608, is condensed in the condenser 604 to release heat, becomes low-temperature high-pressure liquid, is throttled by the capillary 607 to become low-temperature low-pressure liquid, enters the freezing chamber evaporator 605 to evaporate and absorb heat, and then continues to enter the refrigerating chamber evaporator 602 to absorb heat, so as to provide cold for the freezing chamber 703 and the refrigerating chamber 701. After the evaporation process, the working medium is changed into low-temperature and low-pressure gas, and the gas flows into the variable frequency compressor 608 to complete the compression and throttling cycle process. The cold end of the free piston Stirling refrigerator is connected with a first cold end heat pipe 503 and a second cold end heat pipe 504, the working medium of the free piston Stirling refrigerator is R170, the free piston Stirling refrigerator becomes liquid after being condensed in the cold guide copper sleeve 200, flows downwards under the action of gravity, evaporates and absorbs heat at an evaporation section in the temperature change chamber 702 to become gaseous, and then flows upwards to return to the cold guide copper sleeve 200, so that the circulation process is completed. The free piston Stirling hot end is connected with the first hot end heat pipe 501 and the second hot end heat pipe 502, the working medium is R600a, the working medium is evaporated into gas in the heat conducting copper sleeve 300 and flows upwards, the gas is condensed in the condensation section and becomes liquid after releasing heat, and the gas flows back to the heat conducting copper sleeve 300 under the action of gravity. The display screen 707 is connected to the controller 800, and can display the temperature in each refrigeration chamber, and also control the operating frequency of the inverter compressor 608 and the input voltage of the free-piston stirling cryocooler 100 to precisely control the refrigeration temperature in each chamber.
As shown in fig. 11, the coaxial pulse tube type free piston stirling cooler 100 includes a linear motor 1, a compression unit, an expander unit, a frame 50, and a housing 60.
As shown in fig. 12, 13, and 14, the frame 50 includes a flange 52, a piston tube 51 disposed in the flange 52, and a base 53.
The flange 52 is in a disc shape, one side of the flange is also provided with a concentric small disc 521, and the flange 52 is uniformly provided with a plurality of connecting through holes.
The base 53 is cylindrical, one end of the base is connected with one side of the flange 52, the other end of the base is a free end, the center line of the base 53 is overlapped 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 the embodiment, the base 53 is four support legs arranged around the center line of the flange 52.
The linear motor 1 comprises an outer yoke 11, an inner yoke 14 and a rotor, wherein the outer yoke 11 and the inner yoke 14 are respectively arranged on the frame, a gap is formed between the outer yoke and the inner yoke, the rotor is arranged in the gap, and the rotor comprises a permanent magnet 13 and a permanent magnet support 15.
As shown in fig. 11, the linear motor 1 mainly includes an outer yoke 11, a coil 12, a permanent magnet 13, an inner yoke 14, and a permanent magnet support 15, the mover includes a permanent magnet 13, a permanent magnet support 15, a connecting member 16, a fixing nut 18, a compression piston 19, and a compression piston plate spring 17 (1/3, which only takes the plate spring mass when calculating the mover mass), and the permanent magnet support 15 is connected to the permanent magnet 13, and is connected to the compression piston 19 and the connecting member 16 by a screw thread. The outer yoke iron 11 and the inner yoke iron 14 are made of soft magnetic materials, such as electrically pure iron and silicon steel sheets, and the permanent magnet 13 is made of permanent magnetic materials, such as Ru Fe B and Al Ni Co permanent magnetic materials. The outer yoke 11, the coil 12, the permanent magnet 13, and the inner yoke 14 are all annular and are arranged coaxially. The outer yoke 11 and the inner yoke 14 are respectively disposed on the frame 50, and a gap is formed between the outer yoke and the inner yoke, and the mover is disposed in the gap.
When the coil is energized with a direct current, the outer yoke iron 11 and the inner yoke iron 14 form a magnetic loop, thereby generating magnetic poles on the outer yoke iron 11 and the inner yoke iron 14. When alternating current is supplied to the coil, the permanent magnet 13 is subjected to alternating electromagnetic force to perform reciprocating linear motion. When the permanent magnet 13 makes reciprocating linear motion, the compression piston 19 is driven to make reciprocating linear motion, and the compression piston plate spring 17 provides axial reciprocating elastic force and radial support.
The compression unit comprises a connector 16, a compression piston plate spring 17, a fixing nut 18 and 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 rack 50 through the connecting piece, the compression piston 19 is arranged in the piston cavity, one end of the compression piston is connected with the rotor and is connected with 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 end heat exchanger 26, a secondary hot end heat exchanger 33, a heat regenerator 25, a pulse tube 31, a cold end heat exchanger 24 and a cold finger shell 35.
The primary hot end heat exchanger 26 is cylindrical, is sleeved on the outer wall of the piston pipe 51 and is arranged on the end face of the small circular 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 pipe 51.
The regenerator 25 is a cylinder with an annular section and is arranged outside the pulse tube 31, one end of the regenerator is connected with the cold-end heat exchanger 24, and the other end of the regenerator is connected with the first-stage hot-end heat exchanger 26. The heat regenerator 25 is made of any one of polyester film, nylon and polytetrafluoroethylene material, and in the embodiment, the heat regenerator 25 is made of polyester film, and the thickness of the polyester film is 20-50 μm.
The secondary hot end heat exchanger 33 is arranged in the pulse tube 31 and located 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, and the other end of the piston rod passes through the compression piston 19 and the compression piston plate spring 17 and then is connected with the expansion piston plate spring 22.
The cold finger shell 35 is arranged outside the primary hot end heat exchanger 26, the heat 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, the cold finger shell 35 and the frame 50 are connected into a whole through connecting pieces.
The radiator 27 is located outside the first-stage hot-end heat exchanger 26 and is arranged on the cold finger shell 35, and the first-stage hot-end heat exchanger 26 transfers heat to the radiator 27 on the outer side through the cold finger shell 35 and finally releases the heat to the environment.
The undamped dynamic vibration absorbing unit 4 is connected with the housing 60 and is arranged outside the housing 60 for damping the refrigerator.
The motion process of the expansion piston and the compression piston and the gas flow process are as follows:
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 by pure air, and the refrigeration effect is generated by the displacement phase difference between the expansion piston 21 and the compression piston 19, and normally the displacement of the expansion piston 21 leads the displacement of the compression piston 19 by 70 to 100 degrees. Since the linear motor is excited by sine alternating current, the motion of the expansion piston 21 and the compression piston 19 is also a continuous motion in a sine curve, but in order to explain the working principle, it is assumed that the expansion piston 21 and the compression piston 19 make intermittent jumping motion according to a cycle rule.
And (3) sound wave compression process: the expansion piston 21 stays still at the top dead center, the compression piston 19 moves upwards from the bottom dead center, at the moment, sound waves in the main compression cavity 29 are compressed and flow into the first-stage hot end heat exchanger 26 at the outer side of the cylinder, heat generated in the compression process is released to the first-stage hot end heat exchanger 26, the first-stage hot end heat exchanger 26 transfers the heat to the radiator 27 at the outer side through the outer shell, and finally the heat is released to the environment. Ideally, the cylinder and the outer shell are completely heat-conducting, and meanwhile, the heat exchange area between the primary hot-end heat exchanger 26 and the radiator 27 is infinite, so that the temperature of the working medium is kept unchanged. In practice, however, isothermal compression is not possible and intermittent movement of the expansion piston 21 is not possible, the expansion piston 21 having already begun to move downward as the compression piston 19 moves upward.
The heat release process of the heat regenerator is as follows: the compression piston 19 does not move after moving to the top dead center, the expansion piston 21 moves downwards, at the moment, sound waves pass through the heat regenerator 25 and are fully contacted with the filler in the heat regenerator 25 for heat exchange, 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 volume, and complete heat exchange between the sound wave and the filler of the regenerator 25 is not possible.
The sound wave laminar flow process: after passing through the cold side heat exchanger 24, the gas passes through the flow director 32 and enters the pulse tube 31 in a laminar flow to push the gas in the pulse tube 31 towards the expansion chamber 28. After the gas is compressed, the pressure and temperature rise. The generated heat is transferred radially through the secondary hot side heat exchanger 33 to the primary hot side heat exchanger 26 and ultimately to the radiator 27 and released to the environment. The gas in the expansion cavity 28 expands to do work, the expansion piston is pushed to a lower dead point in an auxiliary mode, and the work recovery compression cavity becomes small, so that the effect of recovering acoustic work is achieved. In practice, the compression piston 19 does not remain at top dead centre but moves downwards with the expansion piston 21, but it is noted that the two do not move in the same direction but that the expansion piston leads the compression piston by a certain phase angle.
The sound 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 sound waves in the expansion cavity 28 back to the pulse tube 31, gas expands in the pulse tube to absorb heat, a refrigeration effect is generated, and the lowest refrigeration temperature is reached at the top of the pulse tube 31 close to the fluid director 32. The generated cold is led out to the cold environment through the cold end heat exchanger 24. The acoustic wave working medium returns to the heat regenerator 25 along the original path and fully contacts with the filler for heat exchange, and returns to the main compression cavity 29 again to wait for the next compression after absorbing the heat in the heat regenerator 25. The temperature and pressure of the acoustic wave increase and the temperature of regenerator 25 decreases. In practice, the expansion piston 21 does not reach the top dead center when the compression piston 19 reaches the bottom dead center, but during the return to the top dead center, but it still leads the compression piston 19 in the phase of the displacement wave.
The embodiment is suitable for the refrigerating temperature above 220K (-53 ℃), and can provide the refrigerating capacity of 50W-200W.
Effects and effects of the embodiments
The pulse tube type free piston Stirling refrigerator of the embodiment cancels the longer low-temperature expansion piston of the traditional free piston Stirling refrigerator and replaces the long low-temperature expansion piston with the work recovery expansion piston working in a shorter room temperature area. The expansion cylinder of the free piston Stirling refrigerator becomes a pulse tube of a pulse tube cold finger, a laminar flow guider 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. The change combines the advantages of the free piston Stirling refrigerator and the pulse tube refrigerator, and eliminates pumping loss, shuttle loss and axial heat conduction loss caused by the low-temperature expansion piston by eliminating the expansion piston which moves at a high frequency at a cold end and a hot end. The problem of sound power recovery of the pulse tube refrigerator is solved by arranging the shorter room-temperature expansion piston at the hot end, and therefore when the sound power of the cold end is completely recovered, the theoretical efficiency of the novel pulse tube type free piston Stirling refrigerator is Carnot cycle efficiency. Meanwhile, the low-temperature expansion piston is eliminated, so that the manufacturing difficulty of the refrigerating machine is reduced, and the quality of the whole machine 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 (8)
1. A multi-temperature-zone refrigerator adopting a pulse tube type free piston Stirling refrigerator is characterized by comprising:
a refrigerator body and a refrigerating system are arranged in the refrigerator,
the refrigerator body comprises a refrigerating chamber, a freezing chamber and a temperature-changing chamber, wherein the refrigerating chamber is positioned at the upper half part of the refrigerator body, and the freezing chamber and the temperature-changing chamber are positioned at the lower half part of the refrigerator; the refrigerating system consists of a compression throttling refrigerating system and a free piston Stirling refrigerator-heat pipe system, wherein the free piston Stirling refrigerator-heat pipe system comprises a pulse tube type free piston Stirling refrigerator, a cold end gravity heat pipe, a hot end gravity heat pipe, a cold guide copper sleeve and a heat conduction copper sleeve, a condensation section pipeline of the hot end gravity heat pipe is upwards arranged on the inner side of the left wall surface of a refrigerator shell, an evaporation section pipeline of the cold end gravity heat pipe is downwards arranged on the rear wall surface and the left and right wall surfaces in the temperature change chamber, the condensation section of the cold end gravity heat pipe is connected with a cold head of the pulse tube type free piston Stirling refrigerator through the cold guide copper sleeve, the evaporation section of the hot end gravity heat pipe is connected with the hot end of the pulse tube type free piston Stir,
the pulse tube type free piston Stirling refrigerator comprises a linear motor, a compression unit, an expansion unit and a frame,
wherein the frame comprises a flange, a piston pipe 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 cylindrical 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 central line of the base is superposed with the central line of the flange,
the piston tube is a straight 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 arranged in the piston tube and used for accommodating a compression piston and an expansion piston of the refrigerator, a plurality of through holes penetrating through the tube wall of the piston tube are arranged on the piston cavity,
the linear motor comprises an outer yoke iron, an inner yoke iron and a rotor, the outer yoke iron and the inner yoke iron are respectively arranged on the rack, a gap is arranged between the outer yoke iron and the inner yoke iron, 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 rack through a connecting piece, the compression piston is arranged in the piston pipe, 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 expansion 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, a cold end heat exchanger and a fluid director,
the first-stage hot end heat exchanger is cylindrical, is sleeved on the outer wall of the piston tube and is arranged on the end surface 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 of the pulse tube is connected with the cold end heat exchanger,
the fluid director is arranged at one end of the pulse tube and is positioned in the pulse tube,
the heat regenerator is cylindrical and arranged on 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 hot end heat exchanger is arranged in the pulse tube,
the expansion piston is arranged in the piston pipe, 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 penetrates 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 constitute a compression chamber,
the expansion piston, the secondary hot end heat exchanger and the piston cavity form an expansion cavity.
2. The multi-temperature zone refrigerator using the pulse tube type free piston stirling cooler of claim 1, wherein:
the heat-conducting copper sleeve is a circular copper sleeve, an opening at one end of the heat-conducting copper sleeve is connected with the cold head of the pulse tube type free piston Stirling refrigerator, heat-conducting silicone grease is coated between the inner side of the circular copper sleeve and the cold head of the pulse tube type free piston Stirling refrigerator, and a circular groove is formed in the circular copper sleeve so that a heat-conducting working medium flows in the circular groove to fully exchange heat; and two cold-conducting small holes communicated with the annular groove are formed in the side surface of the circular copper sleeve.
3. The multi-temperature zone refrigerator using the pulse tube type free piston stirling cooler of claim 1, wherein:
the heat-conducting copper sleeve is an annular copper sleeve, heat-conducting silicone grease is coated between the inner surface of the annular copper sleeve and the hot end of the pulse tube type free piston Stirling refrigerator, and an annular groove is formed in the annular copper sleeve, so that a heat-transfer working medium flows in the annular groove to fully exchange heat; two heat conduction small holes communicated with the annular groove are formed in the side face of the annular copper sleeve.
4. The multi-temperature zone refrigerator using the pulse tube type free piston stirling cooler of claim 1, wherein:
the refrigerating temperature range of the temperature-changing chamber is-60-10 ℃, and the temperature-changing chamber is provided with cold energy by the pulse tube type free piston Stirling refrigerating machine; the pulse tube type free piston Stirling refrigerator is an integral free piston Stirling refrigerator driven by a linear motor, the pulse tube type free piston Stirling refrigerator is installed in the middle of the left side of the refrigerator, a damping block is fixed at the tail of the pulse tube type free piston Stirling refrigerator, and the damping block faces to a back plate of a refrigerator body.
5. The multi-temperature zone refrigerator using the pulse tube type free piston stirling cooler of claim 1, wherein:
the cold-end gravity heat pipe comprises a first cold-end heat pipe and a second cold-end heat pipe, wherein the first cold-end heat pipe and the second cold-end heat pipe are respectively connected with a first cold guide small hole and a second cold guide small hole on the side surface of a cold guide copper sleeve, a cold-end gravity heat pipe pipeline inclines downwards by an angle of 15 degrees, and a working medium used in the cold-end gravity heat pipe pipeline is R170; the hot end gravity heat pipe comprises a first hot end heat pipe and a second hot end heat pipe, the first hot end heat pipe and the second hot end heat pipe are respectively connected with a first heat conduction small hole and a second heat conduction small hole in the side face of the heat conduction copper sleeve, and a hot end gravity heat pipe pipeline inclines downwards by 10 degrees.
6. The multi-temperature zone refrigerator using a pulse tube type free piston stirling cooler of claim 1 further comprising:
and the fluid director is arranged at one end of the pulse tube and is positioned in the pulse tube.
7. The multi-temperature zone refrigerator using the pulse tube type free piston stirling cooler of claim 1, wherein:
the cold end heat exchanger and the heat regenerator are further provided with a first filter layer, and the first filter layer is cylindrical and made of a stainless steel wire mesh.
8. The multi-temperature zone refrigerator using the pulse tube type free piston stirling cooler of claim 1, wherein:
wherein, the heat regenerator is cylindrical and is made of polyester films.
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| CN112611122B (en) * | 2020-12-23 | 2021-11-09 | 同济大学 | Steam backheating combined cycle refrigerator and refrigerator adopting same |
| CN112902504B (en) * | 2021-03-11 | 2022-03-29 | 中国科学院上海技术物理研究所 | Throttling evaporation integrated cold head heat exchanger of extremely low temperature throttling refrigerator and manufacturing method |
| CN114562828A (en) * | 2022-02-28 | 2022-05-31 | 武汉高芯科技有限公司 | Stirling refrigerating machine with filtering function |
| CN116379632B (en) * | 2023-06-05 | 2023-07-28 | 合肥航谱时代科技有限公司 | Stirling refrigerator |
| CN116907161B (en) * | 2023-09-12 | 2023-12-08 | 苏州华冷科技有限公司 | Deep low temperature Leng Lianxiang of many refrigerators |
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