CN114838516B - Deep low temperature area multistage mixed structure refrigerator adopting low temperature expansion piston coupling - Google Patents
Deep low temperature area multistage mixed structure refrigerator adopting low temperature expansion piston coupling Download PDFInfo
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- CN114838516B CN114838516B CN202210464345.7A CN202210464345A CN114838516B CN 114838516 B CN114838516 B CN 114838516B CN 202210464345 A CN202210464345 A CN 202210464345A CN 114838516 B CN114838516 B CN 114838516B
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- 230000008878 coupling Effects 0.000 title claims abstract description 14
- 238000010168 coupling process Methods 0.000 title claims abstract description 14
- 238000005859 coupling reaction Methods 0.000 title claims abstract description 14
- 230000006835 compression Effects 0.000 claims abstract description 51
- 238000007906 compression Methods 0.000 claims abstract description 51
- 230000008093 supporting effect Effects 0.000 claims abstract description 19
- 230000007246 mechanism Effects 0.000 claims description 21
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 claims description 6
- 239000007788 liquid Substances 0.000 claims description 3
- 229910052757 nitrogen Inorganic materials 0.000 claims description 3
- 238000007789 sealing Methods 0.000 claims description 3
- 238000010276 construction Methods 0.000 claims 1
- 230000005540 biological transmission Effects 0.000 abstract description 4
- 238000005057 refrigeration Methods 0.000 description 7
- 238000005516 engineering process Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000007123 defense Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical group [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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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
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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
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The invention provides a deep low temperature area multistage mixed structure refrigerator adopting low temperature expansion piston coupling, which belongs to the technical field of low temperature refrigerators and comprises a low temperature expansion piston assembly, a high temperature stage cold finger, a low temperature stage cold finger and a linear compressor. The low-temperature expansion piston assembly comprises a cylinder wall, a piston and a supporting plate spring, wherein the piston comprises two piston ends, namely an expansion piston end and a compression piston end, a cavity between the high-temperature-stage cold end heat exchanger and the expansion piston end forms a high-temperature-stage expansion cavity, and a cavity between the hot end heat exchanger of the second-stage heat regenerator and the compression piston end forms a low-temperature-stage compression cavity. The expansion sound work of the cold end of the high temperature stage is directly transmitted to the cold finger of the low temperature stage through the low temperature expansion piston, so that the transmission loss of the sound work between stages can be greatly reduced, and meanwhile, the low temperature expansion piston can also effectively adjust the sound field distribution of the system. The invention can improve the refrigerating efficiency of the refrigerator in the deep low temperature area, and has compact system and higher power density.
Description
Technical Field
The invention belongs to the technical field of low-temperature refrigerators, and particularly discloses a deep low-temperature area multistage hybrid structure refrigerator coupled by a low-temperature expansion piston.
Background
The cryogenic region refrigeration technology has important application in the fields of national defense and military, aerospace detection, low-temperature superconductivity, biomedical treatment and the like, and the Stirling refrigerator technology and the pulse tube refrigerator technology are low-temperature refrigeration technologies with wider application.
At present, the application of the Stirling refrigerator is mainly concentrated in a higher temperature area, the length of an ejector is increased due to a multistage structure operated in a deep low temperature area, and coaxiality between the ejector and a cylinder is difficult to ensure, so that service life and reliability are reduced.
Compared with a Stirling refrigerator, the low-temperature end of the Stirling pulse tube refrigerator has the advantages of small vibration, high reliability, long service life and the like due to the fact that no moving parts are arranged at the low-temperature end of the Stirling pulse tube refrigerator; however, the defect of low intrinsic efficiency caused by cold end expansion acoustic power dissipation exists, and the operation efficiency in a deep low-temperature area is low. In recent years, many scholars have proposed acoustic power recovery type pulse tube refrigerators that recover the expansion acoustic power to the compression chambers in various configurations to increase overall efficiency.
However, for a multistage Stirling pulse tube refrigerator, limited acoustic power output by a linear compressor is transmitted to a cold end through multiple stages, and expansion acoustic power at a cold end of a high-temperature stage is dissipated and recycled to a compression cavity, so that acoustic power actually transmitted to a low-temperature stage is reduced, and the transmission loss of the interstage acoustic power is remarkable, so that the improvement of the efficiency of the whole machine is limited.
Disclosure of Invention
The invention provides a deep low temperature area multistage hybrid structure refrigerator adopting low temperature expansion piston coupling, which obviously reduces the interstage sound power transmission loss of a multistage pulse tube refrigerator, and can effectively adjust sound field distribution so as to improve the refrigerating performance of the whole refrigerator.
The invention provides a deep low temperature area multistage mixed structure refrigerator adopting low temperature expansion piston coupling, comprising a low temperature expansion piston assembly, a high temperature level cold finger, a low temperature level cold finger and a linear compressor; the low-temperature expansion piston assembly comprises a cylinder wall, a piston and a supporting plate spring; the piston comprises two piston ends, namely an expansion piston end and a compression piston end, and the end surface areas of the expansion piston end and the compression piston end are different; the supporting plate spring is of an annular structure and is positioned between the expansion piston end and the compression piston end, the outer side of the supporting plate spring is fixed with the cylinder wall, and the inner side of the supporting plate spring plays a role in fixing and supporting the piston; the high-temperature-stage cold finger comprises a main room temperature heat exchanger, a high-temperature-stage heat regenerator and a high-temperature-stage cold end heat exchanger which are sequentially connected, wherein the main room temperature heat exchanger is connected with a compression cavity of the linear compressor, the high-temperature-stage cold end heat exchanger is connected with a cylinder wall of the low-temperature expansion piston assembly, and a cavity between the high-temperature-stage cold end heat exchanger and the expansion piston end forms a high-temperature-stage expansion cavity; the low-temperature-stage cold finger is a pulse tube cold finger, a heat exchanger at the hot end of a secondary heat regenerator of the pulse tube cold finger is connected with the cylinder wall of the low-temperature expansion piston assembly, and a cavity between the heat exchanger at the hot end of the secondary heat regenerator and the compression piston end forms a low-temperature-stage compression cavity; the low-temperature expansion piston assembly depends on the difference of the areas of the two ends of the piston, the rigidity of the supporting plate spring and the sound field distribution of the self-moving mass regulating system.
Further, the sides of the expansion piston end and the compression piston end are respectively connected with the cylinder wall in a clearance sealing way.
Further, the low-temperature expansion piston assembly, the high-temperature-stage cold-end heat exchanger and the second-stage heat regenerator hot-end heat exchanger are consistent in temperature and work in a temperature zone below the temperature of liquid nitrogen.
Further, the low-temperature stage cold finger is a single-stage structure pulse tube cold finger or a double-stage structure pulse tube cold finger.
Further, the single-stage structure pulse tube cold finger comprises a secondary heat regenerator hot end heat exchanger, a secondary heat regenerator, a secondary cold end heat exchanger, a secondary pulse tube hot end heat exchanger and a phase modulation mechanism which are connected in sequence; the second-stage pulse tube is arranged on the inner central shafts of the second-stage cold end heat exchanger, the second-stage heat regenerator hot end heat exchanger, the piston, the high-temperature-stage cold end heat exchanger, the high-temperature-stage heat regenerator and the main chamber temperature heat exchanger.
Further, the phase modulation mechanism is a room temperature discharger structure and is positioned in the compression cavity of the linear compressor or is connected with the compression cavity of the linear compressor through a connecting pipe.
Further, the two-stage structure pulse tube cold finger comprises a second-stage heat regenerator hot end heat exchanger, a second-stage heat regenerator, a second-stage cold end heat exchanger, a second-stage pulse tube hot end heat exchanger, a phase modulation mechanism, a third-stage heat regenerator, a third-stage cold end heat exchanger, a third-stage pulse tube and a third-stage pulse tube hot end heat exchanger; the hot end heat exchanger of the second-stage heat regenerator, the second-stage heat regenerator and the second-stage cold end heat exchanger are sequentially connected, and the second-stage cold end heat exchanger is respectively connected with the second-stage pulse tube and the third-stage heat regenerator; the secondary pulse tube is of an annular structure, is arranged on the inner central shafts of the secondary cold end heat exchanger, the secondary heat regenerator hot end heat exchanger, the piston, the high-temperature stage cold end heat exchanger, the high-temperature stage heat regenerator and the main chamber temperature heat exchanger, and is positioned on the coaxial outer side of the tertiary pulse tube; the hot end heat exchanger of the second-stage pulse tube is connected with the second-stage pulse tube and the phase modulation mechanism; the three-stage heat regenerator is sequentially connected with the three-stage cold end heat exchanger, the three-stage pulse tube hot end heat exchanger and the phase modulation mechanism; the third-stage pulse tube is arranged on the internal central shafts of the third-stage cold-end heat exchanger, the third-stage heat regenerator and the second-stage pulse tube; the hot end heat exchanger of the three-stage pulse tube is connected with the three-stage pulse tube and the phase modulation mechanism.
Further, the phase modulation mechanism is a room temperature step ejector structure and is positioned in the compression cavity of the linear compressor or is connected with the compression cavity of the linear compressor through a connecting pipe.
Compared with the prior art, the deep low temperature region multistage mixed structure refrigerator adopting low temperature expansion piston coupling has the following advantages:
the low-temperature expansion piston can efficiently transmit the expansion acoustic power of the high-temperature-stage cold end to the hot end of the low-temperature-stage heat regenerator, so that the transmission loss of the interstage acoustic power is obviously reduced, and the efficiency of the whole machine is improved; the low-temperature expansion piston carries out phase adjustment by utilizing the rigidity of a leaf spring, the dynamic mass and the area difference of two sides of the low-temperature expansion piston, and provides proper sound field conditions for the heat regenerator; the room temperature discharger component of the low-temperature-level phase modulation mechanism further recovers expansion sound power of the low-temperature-level cold end, and simultaneously adjusts sound field distribution of the system to improve refrigeration efficiency. The multistage Stirling mixed structure refrigerator adopting the low-temperature expansion piston coupling in the deep low-temperature area has the advantages of high efficiency, compact system and the like.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are needed in the description of the embodiments or the prior art will be briefly described, and it is obvious that the drawings in the description below are some embodiments of the present invention, and other drawings can be obtained according to the drawings without inventive effort for a person skilled in the art.
Fig. 1 is a structural sectional view of a refrigerator in embodiment 1;
fig. 2 is a structural sectional view of the refrigerator in embodiment 2;
FIG. 3 is a structural cross-sectional view of a cryogenic expansion piston assembly.
In the figure: 1. a main room temperature heat exchanger; 2. a high temperature stage regenerator; 3. a high temperature grade cold end heat exchanger; 4. a piston; 5. a heat exchanger at the hot end of the secondary heat regenerator; 6. a second-stage regenerator; 7. a secondary pulse tube 8, a secondary cold end heat exchanger; 9. a low temperature stage compression chamber; 10. a cylinder; 11. a leaf spring; 12. a high temperature stage expansion chamber; 13. a second-stage pulse tube hot end heat exchanger; 14. a room temperature ejector structure; 15. a linear compressor piston; 16. a three-stage regenerator; 17. a three-stage cold end heat exchanger; 18. a three stage pulse tube; 19. a three-stage pulse tube hot end heat exchanger; 20. a compression chamber; 21. room temperature step ejector structure.
Detailed Description
The following description of the embodiments of the present invention will be made apparent and fully in view of the accompanying drawings, in which some, but not all embodiments of the invention are shown. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Example 1
The embodiment provides a deep low temperature area multistage hybrid structure refrigerator adopting low temperature expansion piston coupling, the structural cross section is shown in figure 1, and the refrigerator comprises a low temperature expansion piston assembly, a high temperature stage cold finger, a low temperature stage cold finger and a linear compressor. The low-temperature stage cold finger is a pulse tube cold finger with a single-stage structure. A linear compressor piston 15 is disposed within a compression chamber 20 of the linear compressor.
The low temperature expansion piston assembly comprises a cylinder wall 10, a piston 4 and a supporting leaf spring 11; the piston 4 comprises two piston ends, namely an expansion piston end and a compression piston end, and the end surface areas of the expansion piston end and the compression piston end are different; the supporting plate spring 11 is of an annular structure, is positioned between the expansion piston end and the compression piston end, is fixed with the cylinder wall 10 on the outer side, and has a fixed supporting effect on the piston 4 on the inner side; the sides of the expansion piston end and the compression piston end are respectively in clearance sealing connection with the cylinder wall 10.
The high-temperature-stage cold finger comprises a main room temperature heat exchanger 1, a high-temperature-stage heat regenerator 2 and a high-temperature-stage cold end heat exchanger 3 which are sequentially connected, wherein the main room temperature heat exchanger 1 is connected with a compression cavity 20 of a linear compressor, and the high-temperature-stage cold end heat exchanger 3 is connected with a cylinder wall 10.
The single-stage structure pulse tube cold finger comprises a secondary heat regenerator hot end heat exchanger 5, a secondary heat regenerator 6, a secondary cold end heat exchanger 8, a secondary pulse tube 7, a secondary pulse tube hot end heat exchanger 13 and a phase modulation mechanism which are connected in sequence; the heat exchanger 5 at the hot end of the secondary heat regenerator is connected with the cylinder wall 10; the secondary pulse tube 7 is arranged on the inner central shafts of the secondary cold end heat exchanger 8, the secondary heat regenerator 6, the secondary heat regenerator hot end heat exchanger 5, the piston 4, the high-temperature stage cold end heat exchanger 3, the high-temperature stage heat regenerator 2 and the main chamber temperature heat exchanger 1.
The cavity between the high-temperature-stage cold-end heat exchanger 3 and the expansion piston end forms a high-temperature-stage expansion cavity 12; a low-temperature-stage compression cavity 9 is formed in a cavity between the hot-end heat exchanger 5 of the second-stage heat regenerator and the compression piston end; the low-temperature expansion piston assembly, the high-temperature-stage cold end heat exchanger 3 and the second-stage heat regenerator hot end heat exchanger 5 are consistent in temperature and work in a temperature zone below the temperature of liquid nitrogen.
The working principle of the refrigerator is as follows: the linear compressor piston 15 reciprocates, the working medium helium forms periodic pressure fluctuation in the system, and the working medium gas passes through a compression cavity 20 of the linear compressor, the main room temperature heat exchanger 1, the high-temperature level heat regenerator 2, the high-temperature level cold end heat exchanger 3 and the high-temperature level expansion cavity 12 in the low-temperature expansion piston assembly to transfer the heat of the high-temperature level cold end to the main room temperature heat exchanger 1 for release, so that a refrigeration effect is generated; the cold quantity of the high-temperature-stage cold end is used for cooling the low-temperature expansion piston assembly and the heat exchanger 5 of the hot end of the secondary heat regenerator, and the redundant cold quantity can be output outwards. Working medium in the low-temperature-stage cold finger passes through a low-temperature-stage compression cavity 9, a second-stage heat regenerator hot-end heat exchanger 5, a second-stage heat regenerator 6, a second-stage cold-end heat exchanger 8, a second-stage pulse tube 7, a second-stage pulse tube hot-end heat exchanger 13 and a phase modulation mechanism in the low-temperature expansion piston assembly, and heat of the cold-end heat exchanger is transferred to the second-stage heat regenerator hot-end heat exchanger 5 and the second-stage pulse tube hot-end heat exchanger 13 to be released, so that a lower temperature zone is obtained.
The low-temperature expansion piston assembly adjusts sound field distribution in the system under the action of the difference of the two end areas of the piston 4, the rigidity of the supporting plate spring 11 and the self moving mass, and simultaneously efficiently transmits expansion sound work of the high-temperature-stage cold end to the low-temperature-stage cold finger inlet, namely the heat exchanger 5 of the hot end of the secondary heat regenerator.
The phase modulation mechanism of the low-temperature-stage cold finger is a room temperature ejector structure 14, is positioned in the compression cavity of the linear compressor or is connected with the compression cavity 20 of the linear compressor through a connecting pipe, and can recover the expansion sound work of the low-temperature-stage cold end to the compression cavity 20 of the compressor and can adjust the sound field distribution. And finally, higher refrigeration efficiency is obtained in a deep low-temperature area.
Example 2
The difference between this embodiment and embodiment 1 is that the low temperature stage cold finger is a two stage pulse tube cold finger, and the sectional view of the structure is shown in fig. 2.
The pulse tube cold finger with the double-stage structure comprises a secondary heat regenerator hot end heat exchanger 5, a secondary heat regenerator 6, a secondary cold end heat exchanger 8, a secondary pulse tube 7, a secondary pulse tube hot end heat exchanger 13, a phase modulation mechanism, a tertiary heat regenerator 16, a tertiary cold end heat exchanger 17, a tertiary pulse tube 18 and a tertiary pulse tube hot end heat exchanger 19; the heat exchanger 5 at the hot end of the secondary heat regenerator is connected with the cylinder wall 10; the hot end heat exchanger 5, the secondary heat regenerator 6 and the secondary cold end heat exchanger 8 of the secondary heat regenerator are sequentially connected, and the secondary cold end heat exchanger 8 is respectively connected with the secondary pulse tube 7 and the tertiary heat regenerator 16; the secondary pulse tube 7 is of an annular structure, is arranged on the inner central shafts of the secondary cold end heat exchanger 8, the secondary heat regenerator 6, the secondary heat regenerator hot end heat exchanger 5, the piston 4, the high-temperature stage cold end heat exchanger 3, the high-temperature stage heat regenerator 2 and the main chamber temperature heat exchanger 1, and is positioned on the coaxial outer side of the tertiary pulse tube 18; the secondary pulse tube hot end heat exchanger 13 is connected with the secondary pulse tube 7 and the phase modulation mechanism; the three-stage heat regenerator 16 is sequentially connected with a three-stage cold-end heat exchanger 17, a three-stage pulse tube 18, a three-stage pulse tube hot-end heat exchanger 19 and a phase modulation mechanism 21, and the three-stage pulse tube 18 is arranged on the inner central shafts of the three-stage cold-end heat exchanger 17, the three-stage heat regenerator 16 and the two-stage pulse tube 7.
The phase modulation mechanism is a room temperature step ejector structure 21, which is positioned in the compression cavity of the linear compressor or is connected with the compression cavity of the linear compressor through a connecting pipe.
The working principle of the refrigerant in this embodiment is different from that of embodiment 1 in that: working medium in the low-temperature stage cold finger passes through a low-temperature stage compression cavity 9, a second-stage heat regenerator hot end heat exchanger 5, a second-stage heat regenerator 6 and a second-stage cold end heat exchanger 8 in the low-temperature expansion piston assembly; the working medium is split at the secondary cold-end heat exchanger 8, and part of the working medium flows through the secondary pulse tube 7, the secondary pulse tube hot-end heat exchanger 13 and the room temperature step ejector structure 21, so that a refrigeration effect is generated at the secondary cold-end heat exchanger 8, and a lower temperature zone is obtained; the cold energy is used for cooling the hot end of the three-stage regenerator 16, and the redundant cold energy can be output to the outside. The other part of working medium flows through the three-stage heat regenerator 16, the three-stage cold-end heat exchanger 17, the three-stage pulse tube 18, the three-stage pulse tube hot-end heat exchanger 19 and the room temperature step ejector structure 21, a refrigeration effect is generated at the three-stage cold-end heat exchanger 17, and the working temperature area is further reduced.
The principles and embodiments of the present invention have been described in this specification with reference to specific examples, the description of which is only for the purpose of aiding in understanding the method of the present invention and its core ideas; also, it is within the scope of the present invention to be modified by those of ordinary skill in the art in light of the present teachings. In view of the foregoing, this description should not be construed as limiting the invention.
Claims (6)
1. The deep low temperature area multistage mixed structure refrigerator adopting low temperature expansion piston coupling is characterized by comprising a low temperature expansion piston assembly, a high temperature level cold finger, a low temperature level cold finger and a linear compressor;
the low-temperature expansion piston assembly comprises a cylinder wall (10), a piston (4) and a supporting plate spring (11);
the piston (4) comprises two piston ends, namely an expansion piston end and a compression piston end, and the end surface areas of the expansion piston end and the compression piston end are different;
the supporting plate spring (11) is of an annular structure, is positioned between the expansion piston end and the compression piston end, is fixed with the cylinder wall (10) at the outer side, and has a fixed supporting function on the piston (4) at the inner side;
the high-temperature-stage cold finger comprises a main room temperature heat exchanger (1), a high-temperature-stage heat regenerator (2) and a high-temperature-stage cold end heat exchanger (3) which are sequentially connected, wherein the main room temperature heat exchanger (1) is connected with a compression cavity (20) of the linear compressor, the high-temperature-stage cold end heat exchanger (3) is connected with a cylinder wall (10), and a cavity between the high-temperature-stage cold end heat exchanger (3) and an expansion piston end forms a high-temperature-stage expansion cavity (12);
the low-temperature stage cold finger is a pulse tube cold finger with a single-stage structure;
the single-stage structure pulse tube cold finger comprises a secondary heat regenerator hot end heat exchanger (5), a secondary heat regenerator (6), a secondary cold end heat exchanger (8), a secondary pulse tube (7), a secondary pulse tube hot end heat exchanger (13) and a phase modulation mechanism which are connected in sequence;
the secondary pulse tube (7) is arranged on the inner central shafts of the secondary cold end heat exchanger (8), the secondary heat regenerator (6), the secondary heat regenerator hot end heat exchanger (5), the piston (4), the high-temperature stage cold end heat exchanger (3), the high-temperature stage heat regenerator (2) and the main room temperature heat exchanger (1);
the heat exchanger (5) at the hot end of the secondary heat regenerator is connected with the cylinder wall (10), and a low-temperature-stage compression cavity (9) is formed by a cavity between the heat exchanger (5) at the hot end of the secondary heat regenerator and the compression piston end;
the low-temperature expansion piston assembly relies on the difference of the areas of the two ends of the piston (4), the rigidity of the supporting plate spring (11) and the sound field distribution of the self dynamic mass adjusting system.
2. The cryogenic region multi-stage hybrid structure refrigerator employing cryogenic expansion piston coupling of claim 1, wherein the phase modulation mechanism is a room temperature ejector structure (14), located within the compression chamber (20) of the linear compressor, or connected to the compression chamber (20) of the linear compressor by a connecting tube.
3. The deep low temperature area multistage mixed structure refrigerator adopting low temperature expansion piston coupling is characterized by comprising a low temperature expansion piston assembly, a high temperature level cold finger, a low temperature level cold finger and a linear compressor;
the low-temperature expansion piston assembly comprises a cylinder wall (10), a piston (4) and a supporting plate spring (11);
the piston (4) comprises two piston ends, namely an expansion piston end and a compression piston end, and the end surface areas of the expansion piston end and the compression piston end are different;
the supporting plate spring (11) is of an annular structure, is positioned between the expansion piston end and the compression piston end, is fixed with the cylinder wall (10) at the outer side, and has a fixed supporting function on the piston (4) at the inner side;
the high-temperature-stage cold finger comprises a main room temperature heat exchanger (1), a high-temperature-stage heat regenerator (2) and a high-temperature-stage cold end heat exchanger (3) which are sequentially connected, wherein the main room temperature heat exchanger (1) is connected with a compression cavity (20) of the linear compressor, the high-temperature-stage cold end heat exchanger (3) is connected with a cylinder wall (10), and a cavity between the high-temperature-stage cold end heat exchanger (3) and an expansion piston end forms a high-temperature-stage expansion cavity (12);
the low-temperature-stage cold finger is a pulse tube cold finger with a double-stage structure;
the two-stage structure pulse tube cold finger comprises a second-stage heat regenerator hot end heat exchanger (5), a second-stage heat regenerator (6), a second-stage cold end heat exchanger (8), a second-stage pulse tube (7), a second-stage pulse tube hot end heat exchanger (13), a phase modulation mechanism, a third-stage heat regenerator (16), a third-stage cold end heat exchanger (17), a third-stage pulse tube (18) and a third-stage pulse tube hot end heat exchanger (19);
the hot end heat exchanger (5), the secondary heat regenerator (6) and the secondary cold end heat exchanger (8) of the secondary heat regenerator are sequentially connected;
the secondary cold end heat exchanger (8) is respectively connected with the secondary pulse tube (7) and the tertiary heat regenerator (16);
the secondary pulse tube (7) is of an annular structure, is arranged on the inner central shafts of the secondary cold end heat exchanger (8), the secondary heat regenerator (6), the secondary heat regenerator hot end heat exchanger (5), the piston (4), the high-temperature stage cold end heat exchanger (3), the high-temperature stage heat regenerator (2) and the main room temperature heat exchanger (1) and is positioned on the coaxial outer side of the tertiary pulse tube (18);
the secondary pulse tube hot end heat exchanger (13) is connected with the secondary pulse tube (7) and the phase modulation mechanism;
the three-stage heat regenerator (16) is sequentially connected with a three-stage cold end heat exchanger (17), a three-stage pulse tube (18), a three-stage pulse tube hot end heat exchanger (19) and a phase modulation mechanism;
the third-stage pulse tube (18) is arranged on the internal central shafts of the third-stage cold-end heat exchanger (17), the third-stage heat regenerator (16) and the second-stage pulse tube (7);
the heat exchanger (5) at the hot end of the secondary heat regenerator is connected with the cylinder wall (10), and a low-temperature-stage compression cavity (9) is formed by a cavity between the heat exchanger (5) at the hot end of the secondary heat regenerator and the compression piston end;
the low-temperature expansion piston assembly relies on the difference of the areas of the two ends of the piston (4), the rigidity of the supporting plate spring (11) and the sound field distribution of the self dynamic mass adjusting system.
4. A deep low temperature zone multi-stage hybrid structure refrigerator employing low temperature expansion piston coupling according to claim 3, wherein the phase modulation mechanism is a room temperature step ejector structure (21) located in the compression chamber (20) of the linear compressor or connected with the compression chamber (20) of the linear compressor through a connection pipe.
5. A cryogenic region multi-stage hybrid construction refrigerator employing cryogenic expansion piston coupling according to claim 1 or 3, characterized in that the sides of the expansion piston end and compression piston end are respectively in clearance sealing connection with the cylinder wall (10).
6. A deep low temperature zone multistage hybrid structure refrigerator adopting low temperature expansion piston coupling according to claim 1 or 3, wherein the low temperature expansion piston assembly, the high temperature stage cold end heat exchanger (3) and the secondary regenerator hot end heat exchanger (5) are consistent in temperature and work in a temperature zone below the liquid nitrogen temperature.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202210464345.7A CN114838516B (en) | 2022-04-29 | 2022-04-29 | Deep low temperature area multistage mixed structure refrigerator adopting low temperature expansion piston coupling |
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| CN202210464345.7A CN114838516B (en) | 2022-04-29 | 2022-04-29 | Deep low temperature area multistage mixed structure refrigerator adopting low temperature expansion piston coupling |
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| CN114838516B true CN114838516B (en) | 2023-10-27 |
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN203258917U (en) * | 2013-04-25 | 2013-10-30 | 浙江大学 | Profound hypothermia ejector adopting full carbon aerogel and stirling cryocooler |
| CN106440449A (en) * | 2016-11-01 | 2017-02-22 | 中国科学院理化技术研究所 | Multi-grade pulse tube refrigerator |
| CN107687718A (en) * | 2017-08-09 | 2018-02-13 | 中国科学院理化技术研究所 | A kind of multi-stage stirling refrigeration machine |
| CN113074469A (en) * | 2021-04-13 | 2021-07-06 | 中国科学院上海技术物理研究所 | Stirling pulse tube composite refrigerator with low-temperature piston active phase modulation |
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2022
- 2022-04-29 CN CN202210464345.7A patent/CN114838516B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN203258917U (en) * | 2013-04-25 | 2013-10-30 | 浙江大学 | Profound hypothermia ejector adopting full carbon aerogel and stirling cryocooler |
| CN106440449A (en) * | 2016-11-01 | 2017-02-22 | 中国科学院理化技术研究所 | Multi-grade pulse tube refrigerator |
| CN107687718A (en) * | 2017-08-09 | 2018-02-13 | 中国科学院理化技术研究所 | A kind of multi-stage stirling refrigeration machine |
| CN113074469A (en) * | 2021-04-13 | 2021-07-06 | 中国科学院上海技术物理研究所 | Stirling pulse tube composite refrigerator with low-temperature piston active phase modulation |
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| CN114838516A (en) | 2022-08-02 |
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