CN115111843A - Coupled multi-temperature-zone refrigerating system - Google Patents
Coupled multi-temperature-zone refrigerating system Download PDFInfo
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- CN115111843A CN115111843A CN202210733249.8A CN202210733249A CN115111843A CN 115111843 A CN115111843 A CN 115111843A CN 202210733249 A CN202210733249 A CN 202210733249A CN 115111843 A CN115111843 A CN 115111843A
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- 238000005057 refrigeration Methods 0.000 claims abstract description 117
- 238000007710 freezing Methods 0.000 claims abstract description 26
- 230000008014 freezing Effects 0.000 claims abstract description 26
- 239000003507 refrigerant Substances 0.000 claims description 22
- 239000007788 liquid Substances 0.000 claims description 17
- 239000012071 phase Substances 0.000 claims description 12
- 230000001105 regulatory effect Effects 0.000 claims description 5
- 239000007791 liquid phase Substances 0.000 claims description 4
- 230000017525 heat dissipation Effects 0.000 abstract description 6
- 238000010586 diagram Methods 0.000 description 6
- 238000001704 evaporation Methods 0.000 description 6
- 230000008020 evaporation Effects 0.000 description 6
- 239000007789 gas Substances 0.000 description 4
- 238000001816 cooling Methods 0.000 description 3
- 235000013305 food Nutrition 0.000 description 3
- 235000014102 seafood Nutrition 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000001307 helium Substances 0.000 description 2
- 229910052734 helium Inorganic materials 0.000 description 2
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical compound [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 238000004321 preservation Methods 0.000 description 2
- 239000013526 supercooled liquid Substances 0.000 description 2
- 241000219112 Cucumis Species 0.000 description 1
- 235000015510 Cucumis melo subsp melo Nutrition 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 235000012055 fruits and vegetables Nutrition 0.000 description 1
- 235000013622 meat product Nutrition 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000001629 suppression Effects 0.000 description 1
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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
- F25D11/022—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures with two or more evaporators
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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
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/06—Superheaters
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
- F25D11/04—Self-contained movable devices, e.g. domestic refrigerators specially adapted for storing deep-frozen articles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
- F25D19/04—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors with more than one refrigeration unit
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- Mechanical Engineering (AREA)
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- Combustion & Propulsion (AREA)
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Abstract
The invention discloses a coupled multi-temperature-zone refrigeration system, which consists of a Lorentz cycle refrigeration system and a free piston type Stirling refrigeration system, and comprises a freezing evaporator, a refrigerating evaporator, an electronic expansion valve, a low-temperature section heat regenerator, a high-temperature section heat regenerator, a condenser, a compressor, a free piston type Stirling refrigerator, a hot end heat exchanger and a cold end heat exchanger; the Lorentz circulating refrigeration system is coupled with the Stirling refrigeration system, so that refrigeration in multiple temperature areas can be realized at the same time; the phase change temperature slip characteristic of the non-azeotropic mixed working medium in the Lorentz circulating refrigeration system is fully utilized, the heat exchange temperature difference of each refrigeration temperature area is effectively reduced, and cold energy can be provided for heat dissipation of the hot end of the free piston type Stirling refrigerator, so that the working temperature of the hot end of the free piston type Stirling refrigerator is reduced, low-load low-frequency operation is realized, the input power is effectively reduced, and vibration and working noise are reduced.
Description
Technical Field
The invention relates to a refrigeration system of a refrigerator, in particular to a coupled multi-temperature-zone refrigeration system.
Background
With the improvement of living standard and consumption idea of people, the common refrigerator can not meet different freezing storage requirements of people on colorful foods. The common refrigerator can meet the requirements of cold storage at 4 ℃ of melons, fruits and vegetables and common freezing at-18 ℃ of meat products at the same time, but cannot meet the requirements of deep freezing and storage below-40 ℃ for some seafood. Also, the freshness-keeping period of food at different storage temperatures varies, for example: tuna can be stored for only 3 months at-18 ℃ but for 2 years at-55 ℃ and below.
A conventional household refrigerator refrigerating system generally employs a single-stage vapor compression type refrigerating cycle, and generally, only 1 evaporator is provided in a freezing chamber, and its cooling energy is supplied to a refrigerating chamber and the freezing chamber through different air ducts, respectively. Therefore, the problems of large heat exchange temperature difference, low working efficiency, high energy consumption and the like in a refrigeration area exist, and meanwhile, the refrigeration temperature below minus 40 ℃ is difficult to realize, so that the storage and preservation requirements of deep sea seafood products cannot be met.
The free piston type Stirling refrigerator adopts helium as a working medium, can provide refrigeration temperature below minus 60 ℃, has the advantages of few moving parts, long service life, compact structure, light weight, high refrigeration efficiency and the like, and has higher refrigeration efficiency when working under different load conditions. With the gradual maturity of the free piston type Stirling refrigerator technology, the cost of the free piston type Stirling refrigerator is reduced year by year, the Stirling refrigerator starts to enter the market of the civil refrigerator, and the low-temperature deep freezing requirement of seafood products is expected to be met. But the working hot end of the free piston type Stirling refrigerator has higher heat dissipation requirement; meanwhile, the stirling cryocooler generates a large noise due to its high 80HZ operating frequency, which undoubtedly puts higher demands on the damping and noise suppression technology. The large-scale popularization and application of the Stirling refrigerator in the refrigerator are limited.
Disclosure of Invention
In order to solve the problems in the prior art, the invention aims to provide a coupled multi-temperature-zone refrigeration system, which realizes multi-temperature-zone refrigeration and has the advantages of high energy efficiency, low noise and high temperature control precision.
In order to achieve the purpose, the invention adopts the following technical scheme:
the coupled multi-temperature-zone refrigeration system comprises a Lorentz circulation refrigeration system and a free piston type Stirling refrigeration system;
the Lorentz circulating refrigeration system comprises a freezing evaporator, an electronic expansion valve, a low-temperature section heat regenerator, a high-temperature section heat regenerator, a condenser, a compressor and a refrigeration evaporator; the free piston type Stirling refrigerating system comprises a free piston type Stirling refrigerating machine, and a hot end heat exchanger and a cold end heat exchanger which are respectively arranged at the hot end and the cold end of the free piston type Stirling refrigerating machine;
the low-temperature side outlet of the low-temperature section heat regenerator is connected with the inlet of the hot end heat exchanger through the refrigeration evaporator, the outlet of the hot end heat exchanger is connected with the low-temperature side inlet of the high-temperature section heat regenerator, the low-temperature side outlet of the high-temperature section heat regenerator is connected with the high-temperature side inlet of the high-temperature section heat regenerator through the compressor and the condenser in sequence, the high-temperature side outlet of the high-temperature section heat regenerator is connected with the high-temperature side inlet of the low-temperature section heat regenerator, and the high-temperature side outlet of the low-temperature section heat regenerator is connected with the low-temperature side inlet of the low-temperature section heat regenerator through the electronic expansion valve and the freezing evaporator.
The coupled multi-temperature-zone refrigeration system comprises a Lorentz circulation refrigeration system and a free piston type Stirling refrigeration system;
the Lorentz circulating refrigeration system comprises a freezing evaporator, an electronic expansion valve, a low-temperature section heat regenerator, a high-temperature section heat regenerator, a condenser, a compressor and a refrigeration evaporator; the free piston type Stirling refrigerating system comprises a free piston type Stirling refrigerating machine, and a hot end heat exchanger and a cold end heat exchanger which are respectively arranged at the hot end and the cold end of the free piston type Stirling refrigerating machine;
the low-temperature side outlet pipeline of the low-temperature section heat regenerator is divided into two paths, one path of pipeline is connected with the inlet of the hot end heat exchanger after being provided with an electronic regulating valve, and the other path of pipeline is connected with the low-temperature side inlet of the high-temperature section heat regenerator after being converged with the outlet of the hot end heat exchanger through a refrigeration evaporator; the low-temperature side outlet of the high-temperature section heat regenerator is connected with the high-temperature side inlet of the high-temperature section heat regenerator through the compressor and the condenser in sequence, the high-temperature side outlet of the high-temperature section heat regenerator is connected with the high-temperature side inlet of the low-temperature section heat regenerator, and the high-temperature side outlet of the low-temperature section heat regenerator is connected with the low-temperature side inlet of the low-temperature section heat regenerator through the electronic expansion valve and the freezing evaporator.
The coupled multi-temperature-zone refrigeration system comprises a Lorentz circulation refrigeration system and a free piston type Stirling refrigeration system;
the Lorentz circulating refrigeration system comprises a freezing evaporator, an electronic expansion valve, a low-temperature section heat regenerator, a high-temperature section heat regenerator, a condenser, a compressor and a refrigeration evaporator; the free piston type Stirling refrigerating system comprises a free piston type Stirling refrigerating machine, and a hot end heat exchanger and a cold end heat exchanger which are respectively arranged at the hot end and the cold end of the free piston type Stirling refrigerating machine;
the outlet of the low-temperature side of the low-temperature section heat regenerator is connected with the inlet of the gas-liquid separator, the gas-phase outlet of the gas-liquid separator is connected with the inlet of the hot-end heat exchanger, the liquid-phase outlet of the gas-liquid separator is connected with the inlet of the refrigeration evaporator, and the outlet of the hot-end heat exchanger is converged with the outlet of the refrigeration evaporator and is connected with the inlet of the low-temperature side of the high-temperature section heat regenerator; the low-temperature side outlet of the high-temperature section heat regenerator is connected with the high-temperature side inlet of the high-temperature section heat regenerator through the compressor and the condenser in sequence, the high-temperature side outlet of the high-temperature section heat regenerator is connected with the high-temperature side inlet of the low-temperature section heat regenerator, and the high-temperature side outlet of the low-temperature section heat regenerator is connected with the low-temperature side inlet of the low-temperature section heat regenerator through the electronic expansion valve and the freezing evaporator.
The refrigerant adopted by the Lorentz circulating refrigeration system is a non-azeotropic mixed working medium with the phase-change temperature slippage more than 20 ℃.
The non-azeotropic mixed working medium is refrigerant R32/R600a or refrigerant R170/R600 a.
Compared with the prior art, the invention has the following beneficial effects:
(1) the Lorentz circulating refrigeration system is coupled with the Stirling refrigeration system, and multi-temperature-zone refrigeration is realized at the same time; because the Lorentz circulating refrigeration system is adopted, the refrigeration temperature of 4 ℃ and the common freezing temperature of-18 ℃ can be provided, the phase change temperature slip characteristic of the non-azeotropic mixed working medium is fully utilized, and the heat exchange temperature difference of each refrigeration temperature area is effectively reduced, so that the energy efficiency of the refrigerator system is improved; meanwhile, the free piston type Stirling refrigerating system is adopted, so that the low-temperature deep freezing temperature of-60 ℃ or below can be provided, and the refrigerating temperature and the refrigerating capacity can be adjusted by changing the working voltage according to different refrigerating requirements. Can realize multi-temperature-zone refrigeration at the same time, and meet the preservation requirements of different foods.
(2) The cold energy in the Lorentz cycle is introduced into the hot end heat exchanger of the free piston type Stirling refrigerator, the working temperature of the hot end of the free piston type Stirling refrigerator is adjusted, the working temperature of the hot end of the free piston type Stirling refrigeration system is adjusted by adopting a low-temperature non-azeotropic working medium in the Lorentz cycle refrigeration system, and the free piston type Stirling refrigerator can work at a lower heat dissipation temperature, so that the free piston type Stirling refrigerator is in a low-frequency operation state, the input power is effectively reduced, and the vibration and the working noise are reduced.
(3) The phase change temperature slippage characteristic of the non-azeotropic mixed working medium in the Lorentz circulation refrigerating system is fully utilized, and the mixed working medium with large temperature slippage can obtain a wide-range continuous evaporation curve, so that the proper hot end working temperature is provided for the free piston type Stirling refrigerating machine, the operation is simple and easy, the temperature control precision is high, and the refrigerating performance of the Stirling refrigerating system is effectively improved.
Drawings
Fig. 1 is a schematic structural diagram of a coupled multi-temperature-zone refrigeration system according to embodiment 1 of the present invention.
Fig. 2 is a schematic structural diagram of a coupled multi-temperature-zone refrigeration system according to embodiment 2 of the present invention.
Fig. 3 is a schematic structural diagram of a coupled multi-temperature-zone refrigeration system according to embodiment 3 of the present invention.
FIG. 4 is a performance curve of the Lorentz cycle of example 1 using the R32/R600a mixed working fluid at different mass ratios of R32.
FIG. 5 is a graph of the operating temperature of the cold and hot ends of the free piston Stirling refrigerator of example 1 under two different operating conditions.
In the figure: 1. the system comprises a freezing evaporator, 2 electronic expansion valves, 3 low-temperature section heat regenerators, 4 high-temperature section heat regenerators, 5 condensers, 6 compressors, 7 free piston type Stirling refrigerators, 8 hot end heat exchangers, 9 cold end heat exchangers, 10 electronic control valves, 11 refrigerating evaporators and 12 gas-liquid separators.
Detailed Description
The following examples are given to further illustrate the present invention in detail, but are not intended to limit the present invention.
Example 1
Fig. 1 is a schematic structural diagram of a coupled multi-temperature-zone refrigeration system according to embodiment 1 of the present invention.
The coupled multi-temperature-zone refrigeration system provided by the embodiment 1 of the invention comprises a Lorentz cycle refrigeration system and a free piston type Stirling refrigeration system, wherein the Lorentz cycle refrigeration system comprises a refrigeration evaporator 1, an electronic expansion valve 2, a low-temperature section heat regenerator 3, a high-temperature section heat regenerator 4, a condenser 5, a compressor 6 and a refrigeration evaporator 11, and the Lorentz cycle refrigeration system adopts non-azeotropic mixed working media with the phase change temperature slip larger than 20 ℃, such as environment-friendly working media R32/R600a and R170/R600 35 600a, and can also be a combination of R125/R600a, R23/R600a, R290/R600a, R1270/R600a and other non-azeotropic mixed working media meeting the characteristic of large temperature slip. As shown in fig. 4, it can be seen that: in the range of 0.175-0.35 of the mass ratio of R32, the Lorentz cycle shows better volume refrigerating capacity and coefficient of performance (COP) value, and the proportion can be selected according to the actual operation condition.
In the free piston type Stirling refrigeration system, helium is used as a working medium, so that the environment is not damaged. The free piston type Stirling refrigerating system comprises a free piston type Stirling refrigerating machine 7, a hot end heat exchanger 8 and a cold end heat exchanger 9, wherein the hot end heat exchanger 8 and the cold end heat exchanger 9 are respectively arranged at the hot end and the cold end of the free piston type Stirling refrigerating machine 7, cold energy generated by the free piston type Stirling refrigerating machine 7 is efficiently transmitted into a low-temperature freezing chamber through the cold end heat exchanger 9, heat generated by the free piston type Stirling refrigerating machine is taken away by the hot end heat exchanger 8, and a proper hot end working temperature is provided to maintain efficient refrigerating performance of the Stirling refrigerating machine.
The inlet of the hot end heat exchanger 8 is connected with the low-temperature side outlet of the low-temperature section heat regenerator 3 through the refrigeration evaporator 11, and the outlet of the hot end heat exchanger 8 is connected with the low-temperature side inlet of the high-temperature section heat regenerator 4; the low-temperature side outlet of the high-temperature section heat regenerator 4 is connected with the high-temperature side inlet of the high-temperature section heat regenerator 4 through a compressor 6 and a condenser 5 in sequence, the high-temperature side outlet of the high-temperature section heat regenerator 4 is connected with the high-temperature side inlet of the low-temperature section heat regenerator 3, and the high-temperature side outlet of the low-temperature section heat regenerator 3 is connected with the low-temperature side inlet of the low-temperature section heat regenerator 3 through an electronic expansion valve 2 and a freezing evaporator 1.
The invention relates to a coupled multi-temperature-zone refrigerating system, which has the working principle as follows:
as shown in fig. 1, in the lorentz cycle, a non-azeotropic mixed refrigerant is compressed by a compressor 6 to become high-temperature high-pressure gas, then enters a condenser 5 to be condensed and radiated to become high-pressure normal-temperature liquid, and then sequentially exchanges heat with a low-temperature side working medium in a high-temperature section heat regenerator 4 and a low-temperature section heat regenerator 3 to be cooled to become supercooled liquid, and the supercooled liquid is throttled by an electronic expansion valve 2 to become a low-temperature low-pressure state, enters a refrigeration evaporator 1 to be evaporated and absorbed and provides a refrigeration temperature of-18 ℃, then enters the low-temperature section heat regenerator 3 to exchange heat with the high-temperature working medium, and the temperature is further increased. Then enters the refrigeration evaporator 11 to continue evaporation and absorb heat and provide refrigeration temperature of 4 ℃. After evaporation and heat absorption are finished, the gas enters the high-temperature section heat regenerator 4 for further temperature rise to become superheated gas, and then enters the compressor 6 to finish circulation. As can be seen from fig. 1, the refrigerant throttled by the electronic expansion valve 2 enters the refrigeration evaporator 1 first, and then enters the refrigeration evaporator 11, and a low temperature section heat regenerator 3 is introduced between the two evaporators. Thus, the special temperature slippage effect of the non-azeotropic mixed working medium is utilized to partially evaporate in the low-temperature evaporator (namely, the freezing evaporator 1) and then enter the intermediate heat exchanger (namely, the low-temperature section heat regenerator 3), so that on one hand, the temperature of the working medium before throttling is further reduced, and on the other hand, the inlet temperature of the working medium before the high-temperature evaporator (namely, the refrigeration evaporator 11) is increased, so as to make up for the defect of small slippage temperature difference of the non-azeotropic mixed working medium, thereby reducing the heat transfer temperature difference of the high-temperature evaporator (namely, the refrigeration evaporator 11), reducing the loss of the ignition and improving the coefficient of performance (COP) of the system.
In the free piston type Stirling refrigerating system, cold energy generated by a cold head of a free piston type Stirling refrigerating machine 7 can provide low-temperature deep freezing temperature of-60 ℃ and below through a cold end heat exchanger 9; the form of the cold end heat exchanger 9 can be air cooling type, direct cooling type, and can also be a heat pipe form. As shown in fig. 5, it can be seen that: when the temperature of the hot end is 10 ℃, the Stirling refrigerator has the lowest temperature of the cold end, and the performance is optimal at the moment. Considering that the refrigerating temperature of the refrigerator system is usually 5 ℃, the refrigerant at the outlet of the refrigerating evaporator 11 is introduced into the hot end heat exchanger 8 of the free piston type Stirling refrigerator 7 to regulate the hot end working temperature. Therefore, better temperature matching characteristics can be obtained, the heat exchange efficiency of the hot end heat exchanger 8 is improved, the free piston type Stirling refrigerator 7 can work at the optimal hot end temperature, the input power is reduced, the vibration and the working noise are reduced, and the performance of the free piston type Stirling refrigeration system is effectively improved.
Example 2
Fig. 2 is a schematic structural diagram of a coupled multi-temperature-zone refrigeration system according to embodiment 2 of the present invention.
The difference from the coupled multi-temperature-zone refrigeration system provided in embodiment 1 is that, when the load of the hot-end heat exchanger 8 of the free-piston stirling cooler 7 is small or the cold capacity of the high-temperature zone of the lorentz cycle is large, the coupled multi-temperature-zone refrigeration system provided in embodiment 2 arranges the refrigeration evaporators 11 in parallel. The low-temperature side outlet pipeline of the low-temperature section heat regenerator 3 is divided into two paths, one path of pipeline is connected with the inlet of an electronic regulating valve 10, the other path of pipeline is connected with the inlet of a refrigeration evaporator 11, and the outlet of the electronic regulating valve 10 is connected with the inlet of a hot-end heat exchanger 8; the outlet of the refrigeration evaporator 11 is connected with the low-temperature side inlet of the high-temperature section heat regenerator 4 after being converged with the outlet of the hot end heat exchanger 8.
When the system is operated, the non-azeotropic mixed refrigerant absorbs heat in the refrigeration evaporator 1 and the low-temperature section heat regenerator 3 and is partially evaporated, the evaporation temperature is increased due to the phase change temperature slippage phenomenon of the non-azeotropic mixed working medium, and then the refrigerant is divided into two paths: one path enters a hot end heat exchanger 8 through an electronic regulating valve 10 to provide cold energy for the heat dissipation of the hot end of the free piston type Stirling refrigerator 7 and improve the refrigeration performance of the free piston type Stirling refrigerator; the other path enters a refrigerating evaporator 11 to provide refrigerating capacity for a refrigerating temperature zone. In this embodiment, the hot-end heat exchanger 8 and the refrigeration evaporator 11 are arranged in parallel, and the flow of the refrigerant in the hot-end heat exchanger 8 is adjusted by the electronic control valve 10, so that the heat dissipation requirement of the stirling refrigerator and the refrigeration requirement of the refrigeration chamber under different working conditions can be met. Therefore, the phase change temperature slip characteristic of the non-azeotropic mixed working medium in the Lorentz circulation refrigerating system is fully utilized, and the mixed working medium with large temperature slip is adopted to obtain a wide-range continuous evaporation curve, so that the proper hot end working temperature is provided for the free piston type Stirling refrigerator, the operation is simple and easy, the temperature control precision is high, and the refrigerating performance of the Stirling refrigerating system is effectively improved. Therefore, the high-efficiency operation of the refrigeration system in a wider working range is realized, and the operation flexibility and the energy efficiency level of the system are increased.
Example 3
Fig. 3 is a schematic structural diagram of a coupled multi-temperature-zone refrigeration system according to embodiment 3 of the present invention.
The difference from the coupled multi-temperature-zone refrigeration system provided in embodiment 2 is that, in order to effectively utilize the surplus refrigeration capacity of the lorentz cycle at the high-temperature zone, the coupled multi-temperature-zone refrigeration system provided in embodiment 3 realizes gas-liquid separation and parallel refrigeration of the refrigerant by additionally arranging the gas-liquid separator 12. The outlet of the low-temperature side of the low-temperature section heat regenerator 3 is connected with the inlet of a gas-liquid separator 12, the gas-phase outlet of the gas-liquid separator 12 is connected with the inlet of a hot-end heat exchanger 8, the liquid-phase outlet of the gas-liquid separator 12 is connected with the inlet of a refrigeration evaporator 11, and the outlet of the hot-end heat exchanger 8 is converged with the outlet of the refrigeration evaporator 11 and is connected with the inlet of the low-temperature side of the high-temperature section heat regenerator 4.
When the system is in operation, the non-azeotropic mixed refrigerant absorbs heat in the refrigeration evaporator 1 and the low-temperature section heat regenerator 3 and is partially evaporated into a gas-liquid two-phase mixture, the evaporation temperature of the non-azeotropic mixed refrigerant rises due to the phenomenon of phase change temperature slippage of the non-azeotropic mixed refrigerant, and then the gas-liquid two-phase mixture enters the gas-liquid separator 12 and is divided into two paths: one path is a gas phase and provides cold energy for heat dissipation of the hot end of the free piston type Stirling refrigerator 7; the other path is liquid phase and is used for providing refrigerating capacity for a refrigerating temperature zone at 4 ℃. In this embodiment, the gas-liquid separator 12 can realize automatic distribution of the flow in the hot-side heat exchanger 8 and the cold storage evaporator 11 according to the system working pressure, and has the advantages of simple structure, high efficiency in operation and the like.
Furthermore, the coupling multi-temperature-zone refrigeration system provided by the invention can adjust the coupling mode of the Lorentz cycle refrigeration system and the Stirling refrigeration system according to the actual use requirement, including but not limited to placing the hot-end heat exchanger 8 at the low-temperature side outlet of the high-temperature-section heat regenerator 4 or the low-temperature-section heat regenerator 3 in the Lorentz cycle refrigeration system, thereby providing different hot-end working temperatures for the free piston type Stirling refrigerator and realizing the high-efficiency operation of the system.
Claims (9)
1. Coupled multi-temperature-zone refrigerating system, its characterized in that: the system comprises a Lorentz circulating refrigeration system and a free piston type Stirling refrigeration system;
the Lorentz circulating refrigeration system comprises a freezing evaporator (1), an electronic expansion valve (2), a low-temperature section heat regenerator (3), a high-temperature section heat regenerator (4), a condenser (5), a compressor (6) and a refrigeration evaporator (11); the free piston type Stirling refrigerating system comprises a free piston type Stirling refrigerating machine (7), and a hot end heat exchanger (8) and a cold end heat exchanger (9) which are respectively arranged at the hot end and the cold end of the free piston type Stirling refrigerating machine (7);
the low-temperature side outlet of the low-temperature section heat regenerator (3) is connected with the inlet of a hot end heat exchanger (8) through a refrigeration evaporator (11), the outlet of the hot end heat exchanger (8) is connected with the low-temperature side inlet of the high-temperature section heat regenerator (4), the low-temperature side outlet of the high-temperature section heat regenerator (4) is connected with the high-temperature side inlet of the high-temperature section heat regenerator (4) through a compressor (6) and a condenser (5) in sequence, the high-temperature side outlet of the high-temperature section heat regenerator (4) is connected with the high-temperature side inlet of the low-temperature section heat regenerator (3), and the high-temperature side outlet of the low-temperature section heat regenerator (3) is connected with the low-temperature side inlet of the low-temperature section heat regenerator (3) through an electronic expansion valve (2) and a freezing evaporator (1).
2. The coupled multi-temperature zone refrigeration system of claim 1, wherein: the refrigerant adopted by the Lorentz circulating refrigeration system is a non-azeotropic mixed working medium with the phase-change temperature slippage more than 20 ℃.
3. The coupled multi-temperature zone refrigeration system of claim 2, wherein: the non-azeotropic mixed working medium is refrigerant R32/R600a or refrigerant R170/R600 a.
4. Coupled multi-temperature-zone refrigerating system, its characterized in that: the system comprises a Lorentz circulating refrigeration system and a free piston type Stirling refrigeration system;
the Lorentz circulating refrigeration system comprises a freezing evaporator (1), an electronic expansion valve (2), a low-temperature section heat regenerator (3), a high-temperature section heat regenerator (4), a condenser (5), a compressor (6) and a refrigeration evaporator (11); the free piston type Stirling refrigerating system comprises a free piston type Stirling refrigerating machine (7), and a hot end heat exchanger (8) and a cold end heat exchanger (9) which are respectively arranged at the hot end and the cold end of the free piston type Stirling refrigerating machine (7);
the low-temperature side outlet pipeline of the low-temperature section heat regenerator (3) is divided into two paths, one path of pipeline is connected with the inlet of the hot end heat exchanger (8) after being provided with the electronic regulating valve (10), and the other path of pipeline is connected with the low-temperature side inlet of the high-temperature section heat regenerator (4) after being converged with the outlet of the hot end heat exchanger (8) through the refrigeration evaporator (11); the low-temperature side outlet of the high-temperature section heat regenerator (4) is connected with the high-temperature side inlet of the high-temperature section heat regenerator (4) through a compressor (6) and a condenser (5) in sequence, the high-temperature side outlet of the high-temperature section heat regenerator (4) is connected with the high-temperature side inlet of the low-temperature section heat regenerator (3), and the high-temperature side outlet of the low-temperature section heat regenerator (3) is connected with the low-temperature side inlet of the low-temperature section heat regenerator (3) through an electronic expansion valve (2) and a freezing evaporator (1).
5. The coupled multi-temperature zone refrigeration system of claim 4, wherein: the refrigerant adopted by the Lorentz circulating refrigeration system is a non-azeotropic mixed working medium with the phase-change temperature slippage more than 20 ℃.
6. The coupled multi-temperature zone refrigeration system of claim 5, wherein: the non-azeotropic mixed working medium is refrigerant R32/R600a or refrigerant R170/R600 a.
7. Coupled multi-temperature-zone refrigerating system, its characterized in that: the system comprises a Lorentz circulating refrigeration system and a free piston type Stirling refrigeration system;
the Lorentz circulating refrigeration system comprises a freezing evaporator (1), an electronic expansion valve (2), a low-temperature section heat regenerator (3), a high-temperature section heat regenerator (4), a condenser (5), a compressor (6) and a refrigeration evaporator (11); the free piston Stirling refrigerating system comprises a free piston Stirling refrigerator (7), and a hot end heat exchanger (8) and a cold end heat exchanger (9) which are respectively arranged at the hot end and the cold end of the free piston Stirling refrigerator (7);
the outlet of the low-temperature side of the low-temperature section heat regenerator (3) is connected with the inlet of a gas-liquid separator (12), the gas-phase outlet of the gas-liquid separator (12) is connected with the inlet of a hot-end heat exchanger (8), the liquid-phase outlet of the gas-liquid separator (12) is connected with the inlet of a refrigeration evaporator (11), and the outlet of the hot-end heat exchanger (8) is converged with the outlet of the refrigeration evaporator (11) and connected with the inlet of the low-temperature side of the high-temperature section heat regenerator (4); the low-temperature side outlet of the high-temperature section heat regenerator (4) is connected with the high-temperature side inlet of the high-temperature section heat regenerator (4) through a compressor (6) and a condenser (5) in sequence, the high-temperature side outlet of the high-temperature section heat regenerator (4) is connected with the high-temperature side inlet of the low-temperature section heat regenerator (3), and the high-temperature side outlet of the low-temperature section heat regenerator (3) is connected with the low-temperature side inlet of the low-temperature section heat regenerator (3) through an electronic expansion valve (2) and a freezing evaporator (1).
8. The coupled multi-temperature zone refrigeration system of claim 7, wherein: the refrigerant adopted by the Lorentz circulating refrigeration system is a non-azeotropic mixed working medium with the phase-change temperature slippage more than 20 ℃.
9. The coupled multi-temperature zone refrigeration system of claim 8, wherein: the non-azeotropic mixed working medium is refrigerant R32/R600a or refrigerant R170/R600 a.
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