CN112594968B - Composite refrigeration system and control method thereof - Google Patents
Composite refrigeration system and control method thereof Download PDFInfo
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- CN112594968B CN112594968B CN202011560667.9A CN202011560667A CN112594968B CN 112594968 B CN112594968 B CN 112594968B CN 202011560667 A CN202011560667 A CN 202011560667A CN 112594968 B CN112594968 B CN 112594968B
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 204
- 239000002131 composite material Substances 0.000 title claims abstract description 64
- 238000000034 method Methods 0.000 title claims abstract description 19
- 230000002457 bidirectional effect Effects 0.000 claims abstract description 60
- 230000006835 compression Effects 0.000 claims abstract description 39
- 238000007906 compression Methods 0.000 claims abstract description 39
- 239000003507 refrigerant Substances 0.000 claims description 89
- 238000001816 cooling Methods 0.000 claims description 27
- 150000001875 compounds Chemical class 0.000 claims description 12
- 238000005086 pumping Methods 0.000 claims description 7
- 230000008901 benefit Effects 0.000 abstract description 8
- 239000000463 material Substances 0.000 description 10
- 239000007788 liquid Substances 0.000 description 7
- 238000005516 engineering process Methods 0.000 description 6
- 239000012530 fluid Substances 0.000 description 6
- 230000009471 action Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 230000005347 demagnetization Effects 0.000 description 4
- 230000005415 magnetization Effects 0.000 description 4
- 238000010438 heat treatment Methods 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 238000005260 corrosion Methods 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 239000000696 magnetic material Substances 0.000 description 1
- 230000008569 process 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
- 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
- F25B1/00—Compression machines, plants or systems with non-reversible 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
- F25B21/00—Machines, plants or systems, using electric or magnetic effects
-
- 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
- F25B2321/00—Details of machines, plants or systems, using electric or magnetic effects
- F25B2321/002—Details of machines, plants or systems, using electric or magnetic effects by using magneto-caloric effects
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
The application provides a composite refrigeration system and a control method thereof. The composite refrigeration system comprises a compression refrigeration system and a magnetic refrigeration system, wherein the compression refrigeration system comprises a first heat exchanger (2) of a compressor (1), a throttling device (3) and a second heat exchanger (4), the magnetic refrigeration system comprises a bidirectional pump (6), a first cold accumulator (7) and a second cold accumulator (8), the first cold accumulator (7) is connected with the throttling device (3) in parallel, the first cold accumulator (7) and the throttling device (3) can be selectively communicated with the first heat exchanger (2), a second pipeline is connected with the outside of a first pipeline where the compressor (1) is located in parallel, the bidirectional pump (6) and the second cold accumulator (8) are connected in series on the second pipeline, and the second cold accumulator (8) is located between the bidirectional pump (6) and the second heat exchanger (4). According to the composite refrigeration system provided by the application, the advantages of different refrigeration systems can be fully exerted, the problems of large cold capacity and large temperature span are considered, and the working efficiency of the composite refrigeration system is improved.
Description
Technical Field
The application relates to the technical field of refrigeration, in particular to a composite refrigeration system and a control method thereof.
Background
As the drawbacks of the conventional vapor compression refrigeration technology in terms of environmental unfriendly and heat exchange efficiency become apparent, the development of a new refrigeration technology (non-vapor compression refrigeration) is becoming urgent. The magnetic refrigeration technology is one of the novel refrigeration technologies with the best development prospect, and particularly has very outstanding advantages in the aspects of environmental friendliness and high efficiency, compared with the traditional vapor compression refrigeration, the refrigeration efficiency of the magnetic refrigeration can reach 40% -50% of the Karno cycle efficiency, and is about 30% higher than the traditional compression refrigeration mode; in addition, the magnetic refrigeration mode adopts a magnetic material to perform solid-liquid heat exchange, so that no gas harmful to the environment is generated; and the magnetic composite refrigerating system has low operating frequency and small noise. By virtue of the above-described advantages, the magnetic refrigeration technology is the new refrigeration technology of highest interest in recent years.
The magnetic composite refrigerating system is a device for refrigerating by utilizing the physical characteristics of a magnetocaloric material, and the technical basis of the device is the magnetocaloric effect of the magnetocaloric material, namely: when a variable magnetic field is applied to the magnetocaloric material, the temperature of the magnetocaloric material is increased or reduced, the magnetic entropy of the material is reduced, the heat is released, the temperature is increased when the magnetic field strength is increased, and the magnetic entropy of the material is increased, the heat is absorbed and the temperature is reduced when the magnetic field strength is reduced. However, due to the limitation of the material properties of the existing magnetocaloric materials, the application range of the environment temperature of the magnetic composite refrigeration system is greatly limited, and the problem that large cooling capacity and large temperature span cannot be achieved exists.
The patent document US20070240428A1 discloses a composite refrigeration system, which adopts a hybrid refrigeration system, the system comprises a vapor compression refrigeration cycle device for circulating a first refrigerant and a magnetic refrigeration cycle device for circulating a second refrigerant, and the technical scheme is that a heat exchange fluid in the magnetic refrigeration cycle system can be subjected to two-stage cooling by carrying out heat exchange on a hot end heat exchanger of the magnetic refrigeration cycle and a cold end heat exchanger of the vapor compression refrigeration cycle, so that the cold end heat exchanger in the magnetic refrigeration cycle system can reach lower temperature, and further deep refrigeration is realized.
The problem of poor popularization caused by small temperature span of the magnetic refrigeration system still cannot be solved in the prior art.
Disclosure of Invention
Therefore, the technical problem to be solved by the application is to provide a composite refrigeration system and a control method thereof, which can fully play the advantages of different refrigeration systems, give consideration to the problems of large cold capacity and large temperature span and improve the working efficiency of the composite refrigeration system.
In order to solve the problems, the application provides a composite refrigeration system which comprises a compression refrigeration system and a magnetic refrigeration system, wherein the compression refrigeration system comprises a first heat exchanger of a compressor, a throttling device and a second heat exchanger, the magnetic refrigeration system comprises a bidirectional pump, a first cold accumulator and a second cold accumulator, the first cold accumulator is connected with the throttling device in parallel, the first cold accumulator and the throttling device can be selectively communicated with the first heat exchanger, a second pipeline is connected with the outside of a first pipeline where the compressor is located in parallel, the bidirectional pump and the second cold accumulator are connected in series on the second pipeline, and the second cold accumulator is positioned between the bidirectional pump and the second heat exchanger.
Preferably, the first regenerator, the throttling device and the first heat exchanger are connected through a three-way valve.
Preferably, a first stop valve is arranged on the pipeline where the throttling device is located, and a second stop valve is arranged on the pipeline where the first regenerator is located.
Preferably, a first bypass pipeline is arranged outside the first cold accumulator in parallel, and a first control valve is arranged on the first bypass pipeline.
Preferably, a second bypass pipeline is arranged outside the second cold accumulator in parallel, and a second control valve is arranged on the second bypass pipeline.
According to another aspect of the present application, there is provided a control method of the above-mentioned composite refrigeration system, including:
Acquiring a set target temperature T0 of a refrigerating area;
acquiring a real-time temperature T1 of a refrigerating area and a real-time temperature T2 of a non-refrigerating area;
Judging the relation between the I T1-T0 and a;
When the absolute value T1-T0 is more than a, controlling the composite refrigeration system to operate in a vapor compression refrigeration mode;
When the absolute value of T1-T0 is less than or equal to a, judging the relation between T2 and the set temperature b;
when T2 is less than or equal to b, controlling the composite refrigeration system to operate a natural cold source refrigeration mode;
When T2 is more than b, the composite refrigerating system is controlled to operate in a magnetic refrigerating mode, and the refrigerant flow path is switched through the bidirectional pump.
Preferably, the step of controlling the compound refrigeration system to operate in the vapor compression refrigeration mode includes:
controlling the bidirectional pump to stop running;
controlling the magnetic field generator to stop working;
Controlling the first heat exchanger to be communicated with the throttling device;
Starting the compressor;
the refrigerant is controlled to sequentially flow through the compressor, the first heat exchanger, the three-way valve, the throttling device and the second heat exchanger to form refrigerant flowing circulation.
Preferably, the step of controlling the composite refrigeration system to operate the natural cold source refrigeration mode includes:
controlling the compressor to stop working;
controlling the magnetic field generator to stop working;
Controlling the first heat exchanger to be communicated with the throttling device;
Starting a bidirectional pump;
The refrigerant is controlled to sequentially flow through the bidirectional pump, the first heat exchanger, the throttling device and the second heat exchanger to form a first refrigerant flowing cycle.
Preferably, the step of controlling the composite refrigeration system to operate the natural cold source refrigeration mode further comprises:
acquiring the running time of the composite refrigeration system according to the first refrigerant flowing cycle;
when the running time reaches the preset time, the reversing of the bidirectional pump is controlled, so that the refrigerant flows through the bidirectional pump, the second heat exchanger, the throttling device and the first heat exchanger once to form a second refrigerant flowing cycle.
Preferably, the step of controlling the composite refrigeration system to operate the natural cold source refrigeration mode further comprises:
and controlling the first refrigerant flowing circulation and the second refrigerant flowing circulation to periodically switch.
Preferably, the step of controlling the composite refrigeration system to operate the natural cold source refrigeration mode includes:
controlling the compressor to stop working;
controlling the magnetic field generator to stop working;
Controlling the first heat exchanger to be communicated with a pipeline where the first regenerator is positioned;
controlling the first bypass pipeline to be communicated with the second bypass pipeline;
Starting a bidirectional pump;
the refrigerant is controlled to sequentially flow through the bidirectional pump, the first heat exchanger, the first bypass pipeline, the second heat exchanger and the second bypass pipeline to form a first refrigerant flowing cycle.
Preferably, the step of controlling the composite refrigeration system to operate in a magnetic refrigeration mode and switching the refrigerant flow path through the bi-directional pump comprises:
Controlling the compressor to stop running;
Controlling the first heat exchanger to be communicated with the first cold accumulator;
Controlling the start of the bidirectional pump;
And controlling the pumping direction of the bidirectional pump according to the working states of the first regenerator and the second regenerator.
Preferably, the step of controlling the pumping direction of the bidirectional pump according to the operating states of the first regenerator and the second regenerator includes:
when the first regenerator is magnetized and the second regenerator is demagnetized, the bidirectional pump is controlled to pump out in the first direction;
Controlling the refrigerant to sequentially flow through the bidirectional pump, the second cold accumulator, the second heat exchanger, the first cold accumulator and the first heat exchanger to form refrigerant flowing circulation;
when the first regenerator is demagnetized and the second regenerator is magnetized, the bidirectional pump is controlled to pump out in the second direction;
The refrigerant is controlled to sequentially flow through the bidirectional pump, the first heat exchanger, the first cold accumulator, the second heat exchanger and the second cold accumulator to form refrigerant flowing circulation.
The application provides a composite refrigeration system, which comprises a compression refrigeration system and a magnetic refrigeration system, wherein the compression refrigeration system comprises a first heat exchanger of a compressor, a throttling device and a second heat exchanger, the magnetic refrigeration system comprises a bidirectional pump, a first cold accumulator and a second cold accumulator, the first cold accumulator is connected in parallel with the throttling device, the first cold accumulator and the throttling device can be selectively communicated with the first heat exchanger, a second pipeline is connected in parallel with the outside of a first pipeline where the compressor is located, the bidirectional pump and the second cold accumulator are connected in series on the second pipeline, and the second cold accumulator is located between the bidirectional pump and the second heat exchanger. The composite refrigerating system couples the magnetic refrigerating system and the compression refrigerating system together, so that heat exchange fluid of the magnetic refrigerating system and heat exchange fluid of the compression refrigerating system use refrigerants of the vapor compression refrigerating system, and the composite refrigerating system has three working modes of vapor compression refrigerating, magnetic refrigerating and natural cold source refrigerating by controlling the switching of different flow paths, thereby fully playing the advantages of the systems and improving the refrigerating efficiency of the systems.
Drawings
FIG. 1 is a schematic diagram of a compound refrigeration system according to an embodiment of the present application;
FIG. 2 is a schematic diagram of the working flow path of a compound refrigeration system according to one embodiment of the present application in a compression refrigeration mode;
FIG. 3 is a schematic diagram of the working flow path of a compound refrigeration system according to an embodiment of the present application in a magnetic refrigeration mode;
FIG. 4 is a schematic diagram of a working flow path of a composite refrigeration system according to an embodiment of the present application in a natural cooling source refrigeration mode;
FIG. 5 is a schematic diagram of a compound refrigeration system according to an embodiment of the present application;
Fig. 6 is a flow chart of a control method of the composite refrigeration system according to an embodiment of the present application.
The reference numerals are expressed as:
1. A compressor; 2. a first heat exchanger; 3. a throttle device; 4. a second heat exchanger; 5. a three-way valve; 6. a bi-directional pump; 7. a first regenerator; 8. and a second regenerator.
Detailed Description
Referring to fig. 1 to 5 in combination, according to an embodiment of the present application, a composite refrigeration system includes a compression refrigeration system and a magnetic refrigeration system, the compression refrigeration system includes a first heat exchanger 2 of a compressor 1, a throttling device 3, and a second heat exchanger 4, the magnetic refrigeration system includes a bi-directional pump 6, a first regenerator 7, and a second regenerator 8, the first regenerator 7 is connected in parallel with the throttling device 3, the first regenerator 7 and the throttling device 3 can be selectively communicated with the first heat exchanger 2, a second pipeline is connected in parallel with the outside of the first pipeline where the compressor 1 is located, the bi-directional pump 6 and the second regenerator 8 are connected in series on the second pipeline, and the second regenerator 8 is located between the bi-directional pump 6 and the second heat exchanger 4.
The composite refrigerating system couples the magnetic refrigerating system and the compression refrigerating system together, so that heat exchange fluid of the magnetic refrigerating system and heat exchange fluid of the compression refrigerating system use refrigerants of the vapor compression refrigerating system, and the composite refrigerating system has three working modes of vapor compression refrigerating, magnetic refrigerating and natural cold source refrigerating by controlling the switching of different flow paths, thereby fully playing the advantages of the systems and improving the refrigerating efficiency of the systems.
The composite refrigeration system can utilize the vapor compression refrigeration system to perform rapid refrigeration, and utilize the magnetic refrigeration system or the natural cold source to realize low-power-consumption refrigeration, and can select different control modes according to different working states of the composite refrigeration system, so as to realize the energy efficiency maximization of the composite refrigeration system.
The first regenerator 7, the throttling device 3 and the first heat exchanger 2 are connected through a three-way valve 5. The first regenerator 7, the throttle device 3 and the first heat exchanger 2 may also be realized by other valves or combinations of valves.
For example, in one embodiment, the throttle device 3 is provided with a first shut-off valve in the line and the first regenerator 7 is provided with a second shut-off valve in the line.
The throttling device is an electronic expansion valve.
The compressor 1 and the bi-directional pump 6 can drive the refrigerant in the flow path of the system to circulate in the closed loop, the first heat exchanger 2 is arranged in the non-refrigeration area and used for radiating the heat generated by the system into the non-refrigeration area, and the second heat exchanger 4 is arranged in the refrigeration area and used for radiating the cold generated by the system into the refrigeration area so as to realize the refrigeration purpose.
In each of the above drawings, A0, A1, A2, B0, B1, B2, C1, C2 are flow paths; s1 is a first control valve, and S2 is a second control valve.
The system can switch different working modes according to the working requirements so as to achieve different refrigeration functions and system performances. By controlling the start and stop of the compressor 1 and the bi-directional pump 6, the compound refrigeration system shown in fig. 1 can have at least the following three modes of operation:
(1) Mode 1: vapor compression refrigeration mode
This mode is operated when the temperature of the non-cooling region is high, i.e., the ambient temperature differs greatly from the cooling target temperature. When the mode is started, the controller controls the compressor 1 to start to operate, simultaneously controls the bi-directional pump 6 to stop operating, and controls the three-way valve 5 to connect the pipeline A0 and the pipeline A1, so that a circulation flow path of the compressor 1, the first heat exchanger 2, the three-way valve 5, the throttling device 3, the second heat exchanger 4 and the compressor 1 is formed, as shown in fig. 2. This mode is substantially the same as a conventional vapor compression refrigeration system, and allows the temperature in the refrigeration zone to be reduced to a target temperature value in a short period of time.
More specifically, the working principle of the vapor compression refrigeration mode is as follows: the compressor 1 highly compresses the refrigerant circulated from the second heat exchanger 4, compresses the gaseous refrigerant into a high-temperature and high-pressure state, and sends the compressed refrigerant to the first heat exchanger 2, and dissipates heat to a non-cooling area to form a medium-temperature and high-pressure liquid refrigerant. The liquid refrigerant can be subjected to further depressurization and cooling through the throttling device 3 through the three-way valve 5 to become a low-pressure low-temperature gas-liquid mixed state, and then enters the second heat exchanger 4, the gas-liquid two-phase refrigerant is vaporized in the second heat exchanger 4, and the refrigerant absorbs a large amount of heat in the phase change process from liquid state to gas state, so that the refrigeration of a refrigeration area is realized. The refrigerant from the second heat exchanger 4 becomes superheated gaseous, and then the gaseous refrigerant returns to the compressor 1 to continue circulation.
(2) Mode 2: magnetic refrigeration mode
The working principle of the magnetic refrigeration system is as follows: the application of a varying magnetic field to the magnetocaloric material causes a magnetocaloric effect, i.e. the magnetocaloric material releases heat outwards when the magnetic field generator applies a magnetic field to the regenerator (magnetizing) and releases cold outwards when the magnetic field generator removes a magnetic field from the regenerator (demagnetizing). The mode of the magnetic field generator in the system for generating the changing magnetic field can be the changing magnetic field generated by an electromagnet, or the changing magnetic field generated by the movement of a permanent magnet and a cold accumulator.
This mode is operated when the temperature of the non-cooling region is low, i.e., the ambient temperature is less different from the cooling target temperature. When the mode is started, the controller controls the bi-directional pump 6 to start to operate, controls the compressor 1 to stop operating, and controls the three-way valve 5 to connect the pipeline A0 and the pipeline A2, so that a circulation flow path of the bi-directional pump 6-the first heat exchanger 2-the three-way valve 5-the first cold accumulator 7-the second heat exchanger 4-the second cold accumulator 8-the bi-directional pump 6 is formed, as shown in fig. 3. This mode is substantially the same as existing magnetic refrigeration systems, can operate at lower frequencies and achieve refrigeration under operating conditions with small temperature span requirements. Compared with a compression refrigeration mode, the mode fully exerts the advantages of the magnetic refrigeration system, namely high refrigeration efficiency, low operation frequency and low noise power consumption. After the rapid refrigeration is performed by using the compression refrigeration mode, the refrigeration balance of the small temperature span can be performed by using the magnetic refrigeration mode, so that the temperature in the refrigeration area is dynamically kept near the target temperature.
More specifically, the working principle of the magnetic refrigeration mode is as follows: the first regenerator 7 and the second regenerator 8 in the system can periodically perform magnetization and demagnetization under the action of the magnetic field generator, and the magnetization and demagnetization states of the first regenerator 7 and the second regenerator 8 are just opposite, namely, when the first regenerator 7 performs magnetization and heating, the second regenerator 8 performs demagnetization and cooling, otherwise, when the first regenerator 7 performs demagnetization and cooling, the second regenerator 8 performs magnetization and heating. When the mode works, the refrigerant in the pipeline flows back and forth under the drive of the bidirectional pump 6.
Each working cycle period of the mode is divided into a first stage and a second stage according to the flow direction of the refrigerant in the pipeline, and the specific working conditions are as follows:
the first stage: the magnetic field generator magnetizes the first regenerator 7 and demagnetizes the second regenerator 8. When the first regenerator 7 is magnetized to generate heat, the refrigerant flows along the directions of the first regenerator 7-pipeline A2-pipeline A0-first heat exchanger 2 under the action of the bidirectional pump, so that the refrigerant can transfer the heat in the first regenerator 7 to the first heat exchanger 2 for heat dissipation; at the same time, the second regenerator 8 demagnetizes to generate cold, the refrigerant flows along the direction from the bi-directional pump 6 to the pipeline B2 to the second regenerator 8 to the pipeline B0 to the second heat exchanger 4 under the drive of the bi-directional pump 6, so that the refrigerant can transfer the cold in the second regenerator 8 to the second heat exchanger 4, and then the temperature of the refrigerating area is gradually reduced through the heat exchange between the second heat exchanger 4 and the air in the refrigerating area.
And a second stage: the magnetic field generator demagnetizes the first regenerator 7 and magnetizes the second regenerator 8. When the first regenerator 7 demagnetizes to generate cold energy, the refrigerant flows along the direction of the first regenerator 7-second heat exchanger 4 under the action of the bidirectional pump 6, so that the refrigerant can transfer the cold energy in the first regenerator 7 to the second heat exchanger 4, and then the refrigerant exchanges heat with the air in the refrigerating area through the second heat exchanger 4 to gradually reduce the temperature in the refrigerating area; at the same time, the second regenerator 8 is magnetized to generate heat, and the refrigerant flows along the direction of the pipeline B0-the second regenerator 8-the pipeline B2-the bidirectional pump 6-the first heat exchanger 2 under the drive of the bidirectional pump 6, so that the refrigerant can transfer the heat in the second regenerator 8 to the first heat exchanger 2 and then radiate the heat to a non-refrigeration area through the first heat exchanger 2.
The above two cooling modes are operation modes in which cooling of the cooling region is required when the temperature of the non-cooling region is higher than the temperature of the cooling region. In addition, in the case that the temperature of the non-refrigeration area is lower than that of the refrigeration area, the refrigeration system of the present application can adopt the following operation modes:
(3) Mode 3: natural cold source refrigeration mode
In the refrigeration mode, the controller controls the bi-directional pump 6 to start to operate, simultaneously controls the compressor 1 to stop operating, simultaneously controls the magnetic field generator to stop operating, and controls the three-way valve 5 to connect the main flow path A0 and the branch flow path A1, so that the composite refrigeration system forms a system loop shown in fig. 4, namely the bi-directional pump 6-the first heat exchanger 2-the flow path A0-the three-way valve 5-the flow path A1-the throttling device 3-the second heat exchanger 4-the flow path B0-the flow path B2-the bi-directional pump 6.
More specifically, when the temperature of the non-cooling region is lower than that of the cooling region, the controller switches the system to a mode in which the refrigerant reciprocally flows by the bidirectional pump 6, and each flow cycle period of the mode can be divided into two stages according to the flow direction of the refrigerant:
The first stage: the two-way pump 6 drives the refrigerant into the first heat exchanger 2, the temperature of the refrigerant entering the first heat exchanger 2 is reduced because of lower temperature of the non-refrigeration area, then the refrigerant flows through the three-way valve 5 and the throttling device 3 under the action of the pumping pressure and flows into the second heat exchanger 4 to provide cold for the refrigeration area, and the refrigerant returns to the two-way pump after heat exchange is completed.
And a second stage: the two-way pump 6 drives the refrigerant into the second heat exchanger 4 to perform secondary heat exchange, further fully releases cold in the refrigerant into a refrigerating area, then flows into the first heat exchanger 2 through the throttling device 3 and the three-way valve 5, releases heat in the refrigerant into a non-refrigerating area to obtain cold, and flows into the two-way pump 6.
When the refrigerant in the first stage flows into the first heat exchanger 2 under the action of the pump pressure after passing through the second stage, secondary refrigeration is actually performed, so that the cooling capacity in the refrigerant is larger, and the heat exchange efficiency of the system is higher.
The mode is operated when the temperature of the non-refrigeration area is lower than that of the refrigeration area, and the natural cold source is fully utilized for refrigeration when the refrigeration area is required to be refrigerated, so that the system efficiency can be effectively improved.
The bidirectional pump 6 can be a double-acting piston pump with an anti-corrosion function, the piston pump realizes bidirectional driving of the refrigerant through reciprocating motion of the piston, and the liquid containing volumes at two sides of the piston are the same.
In order to enable the composite refrigeration system to meet the requirements of more efficient automatic temperature control and intelligent refrigeration, a plurality of sensors are arranged in the system and used as signal input sources of a control system. The temperature sensor for detecting the temperature of the refrigerating area is arranged in the refrigerating area, the real-time temperature value of the refrigerating area detected by the temperature sensor is T1, the temperature sensor for detecting the temperature of the non-refrigerating area is arranged in the non-refrigerating area, and the temperature value of the non-refrigerating area detected by the temperature sensor is T2. In addition, the system also needs to set a target temperature value T0 for the cooling zone.
Referring to fig. 5 in combination, there is shown a structure of another composite refrigeration system, which is basically the same as the structure of the foregoing composite refrigeration system, except that in this embodiment, a first bypass line C1 is provided in parallel outside the first regenerator 7, and a first control valve S1 is provided on the first bypass line. A second bypass pipeline C2 is arranged outside the second cold accumulator 8 in parallel, and a second control valve S2 is arranged on the second bypass pipeline. The first control valve S1 is a solenoid valve. The second control valve S2 is a solenoid valve.
In this embodiment, when the system is in the natural cold source refrigeration mode, the controller controls the first control valve S1 to switch on the first bypass pipeline C1, and the second control valve S2 to switch on the second bypass pipeline C2, so that the refrigerant can pass through the first bypass pipeline C1 and the second bypass pipeline C2, thereby reducing the pressure resistance of the system and reducing the power consumption of the system.
Referring to fig. 6 in combination, according to an embodiment of the present application, the control method of the above-mentioned composite refrigeration system includes: acquiring a set target temperature T0 of a refrigerating area; acquiring a real-time temperature T1 of a refrigerating area and a real-time temperature T2 of a non-refrigerating area; judging the relation between the I T1-T0 and a; when the absolute value T1-T0 is more than a, controlling the composite refrigeration system to operate in a vapor compression refrigeration mode; when the absolute value of T1-T0 is less than or equal to a, judging the relation between T2 and the set temperature b; when T2 is less than or equal to b, controlling the composite refrigeration system to operate a natural cold source refrigeration mode; when T2 is more than b, the composite refrigeration system is controlled to operate in a magnetic refrigeration mode, and the refrigerant flow path is switched through the bidirectional pump 6.
The step of controlling the compound refrigeration system to operate in a vapor compression refrigeration mode includes: controlling the bidirectional pump 6 to stop running; controlling the magnetic field generator to stop working; the first heat exchanger 2 is controlled to be communicated with the throttling device 3; starting the compressor 1; the refrigerant is controlled to sequentially flow through the compressor 1, the first heat exchanger 2, the three-way valve 5, the throttling device 3 and the second heat exchanger 4 to form refrigerant flowing circulation.
The step of controlling the composite refrigeration system to operate the natural cold source refrigeration mode comprises the following steps: the compressor 1 is controlled to stop working; controlling the magnetic field generator to stop working; the first heat exchanger 2 is controlled to be communicated with the throttling device 3; starting the bidirectional pump 6; the refrigerant is controlled to sequentially flow through the bidirectional pump 6, the first heat exchanger 2, the throttling device 3 and the second heat exchanger 4 to form a first refrigerant flowing cycle.
The step of controlling the composite refrigeration system to operate the natural cold source refrigeration mode further comprises the following steps: acquiring the running time of the composite refrigeration system according to the first refrigerant flowing cycle; when the running time reaches the preset time, the bidirectional pump 6 is controlled to change direction, so that the refrigerant flows through the bidirectional pump 6, the second heat exchanger 4, the throttling device 3 and the first heat exchanger 2 once to form a second refrigerant flowing cycle.
The step of controlling the composite refrigeration system to operate the natural cold source refrigeration mode further comprises the following steps: and controlling the first refrigerant flowing circulation and the second refrigerant flowing circulation to periodically switch.
The step of controlling the composite refrigeration system to operate the natural cold source refrigeration mode comprises the following steps: the compressor 1 is controlled to stop working; controlling the magnetic field generator to stop working; the first heat exchanger 2 is controlled to be communicated with a pipeline where the first cold accumulator 7 is positioned; controlling the first bypass pipeline to be communicated with the second bypass pipeline; starting the bidirectional pump 6; the refrigerant is controlled to sequentially flow through the bidirectional pump 6, the first heat exchanger 2, the first bypass pipeline, the second heat exchanger 4 and the second bypass pipeline to form a first refrigerant flowing cycle.
The step of controlling the composite refrigeration system to operate in the magnetic refrigeration mode and switching the refrigerant flow path through the bidirectional pump 6 comprises the following steps: controlling the compressor 1 to stop running; the first heat exchanger 2 is controlled to be communicated with the first cold accumulator 7; controlling the bi-directional pump 6 to start; the pumping direction of the bi-directional pump 6 is controlled according to the operating states of the first regenerator 7 and the second regenerator 8.
The step of controlling the pumping direction of the bidirectional pump 6 according to the operating states of the first regenerator 7 and the second regenerator 8 includes: when the first regenerator 7 is magnetized and the second regenerator 8 is demagnetized, the bidirectional pump 6 is controlled to pump out in the first direction; the refrigerant is controlled to sequentially flow through the bidirectional pump 6, the second regenerator 8, the second heat exchanger 4, the first regenerator 7 and the first heat exchanger 2 to form refrigerant flowing circulation; when the first regenerator 7 is demagnetized and the second regenerator 8 is magnetized, the bidirectional pump 6 is controlled to pump out in the second direction; the refrigerant is controlled to sequentially flow through the bidirectional pump 6, the first heat exchanger 2, the first cold accumulator 7, the second heat exchanger 4 and the second cold accumulator 8 to form refrigerant flowing circulation.
The operation control method of the composite refrigeration system is as follows:
After the composite refrigerating system is started, the controller reads a set target temperature value T0 of a refrigerating area, obtains real-time temperature T1 of the refrigerating area and real-time temperature T2 of a non-refrigerating area through a sensor, and judges whether the absolute value T1-T0 is larger than a: if the absolute temperature of the refrigerating area is higher than the absolute temperature of the refrigerating area (a), the controller starts and operates the mode 1, namely, the steam compression refrigerating mode is utilized to perform rapid cooling; if the absolute temperature T1-T0 is less than or equal to a, the real-time temperature of the current refrigeration area is not very high, the refrigeration can be performed without using a vapor compression refrigeration mode, and a natural cold source or a magnetic refrigeration mode is selected for stable cooling, so that the environment-friendly and efficient refrigeration balance is realized. Further, the controller judges whether the temperature T2 of the non-refrigeration area is smaller than or equal to the temperature value b, when the temperature T2 of the non-refrigeration area is smaller than or equal to the temperature value b, the temperature T2 of the non-refrigeration area is lower at present, refrigeration of the refrigeration area can be realized by utilizing a natural cold source mode, the controller starts and operates the natural cold source refrigeration mode of the mode 3, and the low-temperature cold quantity of the non-refrigeration area is brought into the refrigeration area through heat exchange fluid, so that a green and efficient refrigeration effect is realized; otherwise, if the temperature T2 of the non-refrigeration area is greater than b, the temperature T2 of the non-refrigeration area is higher at present, the refrigeration of the refrigeration area is not realized by using a natural cold source mode, the controller starts and operates the magnetic refrigeration mode of the mode 2, and the magnetic heating effect is utilized to realize the green and efficient refrigeration effect. Where a is the temperature difference set point and b is the temperature set point.
After the controller selects the start mode according to the above-described judgment control method, the temperatures of the cooling area and the non-cooling area are read again at intervals Δt1, and the above-described selection judgment of the operation mode is performed again. The composite refrigeration system can switch the refrigeration operation modes according to the real-time data values of the ambient temperature and the temperature of the refrigeration area, so that the composite refrigeration system has the best refrigeration performance and the best refrigeration economic benefit.
The value a is a temperature difference value for judging whether the refrigerating area needs to be refrigerated rapidly, and the value b is calculated according to a system and is used for judging whether the refrigerating can be performed by using a natural cold source or not under the current environment temperature.
It will be readily appreciated by those skilled in the art that the above advantageous ways can be freely combined and superimposed without conflict.
The foregoing description of the preferred embodiments of the application is not intended to be limiting, but rather is intended to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the application. The foregoing is merely a preferred embodiment of the present application, and it should be noted that it will be apparent to those skilled in the art that modifications and variations can be made without departing from the technical principles of the present application, and these modifications and variations should also be regarded as the scope of the application.
Claims (13)
1. The utility model provides a compound refrigerating system, its characterized in that includes compression refrigerating system and magnetic refrigerating system, compression refrigerating system includes compressor (1) first heat exchanger (2), throttling arrangement (3) and second heat exchanger (4), magnetic refrigerating system includes bi-directional pump (6), first regenerator (7) and second regenerator (8), first regenerator (7) with throttling arrangement (3) parallelly connected, first regenerator (7) with throttling arrangement (3) can selectively with first heat exchanger (2) intercommunication, the first pipeline that compressor (1) is located has connected in parallel the second pipeline outward, bi-directional pump (6) with second regenerator (8) are established ties on the second pipeline, second regenerator (8) are located between bi-directional pump (6) and second heat exchanger (4).
2. A composite refrigeration system according to claim 1, characterized in that the first regenerator (7), the throttling device (3) and the first heat exchanger (2) are connected by means of a three-way valve (5).
3. A composite refrigeration system according to claim 1, wherein a first shut-off valve is arranged on the line in which the throttling device (3) is located, and a second shut-off valve is arranged on the line in which the first regenerator (7) is located.
4. A composite refrigeration system according to claim 1, characterized in that a first bypass line is arranged in parallel outside the first regenerator (7), said first bypass line being provided with a first control valve.
5. A composite refrigeration system according to claim 1, characterized in that a second bypass line is arranged in parallel outside the second regenerator (8), and in that a second control valve is arranged on the second bypass line.
6. A control method of a composite refrigeration system according to any one of claims 1 to 5, comprising:
Acquiring a set target temperature T0 of a refrigerating area;
acquiring a real-time temperature T1 of a refrigerating area and a real-time temperature T2 of an ambient temperature;
Judging the relation between the I T1-T0 and a;
When the absolute value T1-T0 is more than a, controlling the composite refrigeration system to operate in a vapor compression refrigeration mode;
When the absolute value of T1-T0 is less than or equal to a, judging the relation between T2 and the set temperature b;
when T2 is less than or equal to b, controlling the composite refrigeration system to operate a natural cold source refrigeration mode;
When T2 is more than b, the composite refrigeration system is controlled to operate in a magnetic refrigeration mode, and the refrigerant flow path is switched through the bidirectional pump (6).
7. A control method according to claim 6, characterized in that the first regenerator (7), the throttling device (3) and the first heat exchanger (2) are connected by a three-way valve (5), and the step of controlling the composite refrigeration system to operate in a vapor compression refrigeration mode comprises:
controlling the bidirectional pump (6) to stop running;
controlling the magnetic field generator to stop working;
the first heat exchanger (2) is controlled to be communicated with the throttling device (3);
starting the compressor (1);
The refrigerant is controlled to sequentially flow through the compressor (1), the first heat exchanger (2), the three-way valve (5), the throttling device (3) and the second heat exchanger (4) to form refrigerant flowing circulation.
8. The control method of claim 6, wherein the step of controlling the compound refrigeration system to operate in a natural cooling source refrigeration mode comprises:
controlling the compressor (1) to stop working;
controlling the magnetic field generator to stop working;
the first heat exchanger (2) is controlled to be communicated with the throttling device (3);
Starting a bidirectional pump (6);
The refrigerant is controlled to sequentially flow through the bidirectional pump (6), the first heat exchanger (2), the throttling device (3) and the second heat exchanger (4) to form a first refrigerant flowing cycle.
9. The control method of claim 8, wherein the step of controlling the compound refrigeration system to operate in a natural cooling source refrigeration mode further comprises:
acquiring the running time of the composite refrigeration system according to the first refrigerant flowing cycle;
When the running time reaches the preset time, the bidirectional pump (6) is controlled to reverse, so that the refrigerant flows through the bidirectional pump (6), the second heat exchanger (4), the throttling device (3) and the first heat exchanger (2) once to form a second refrigerant flowing cycle.
10. The control method of claim 9, wherein the step of controlling the compound refrigeration system to operate in a natural cooling source refrigeration mode further comprises:
and controlling the first refrigerant flowing circulation and the second refrigerant flowing circulation to periodically switch.
11. The control method according to claim 6, wherein a first bypass line is arranged in parallel outside the first regenerator (7), a second bypass line is arranged in parallel outside the second regenerator (8), and the step of controlling the composite refrigeration system to operate in a natural cold source refrigeration mode includes:
controlling the compressor (1) to stop working;
controlling the magnetic field generator to stop working;
The first heat exchanger (2) is controlled to be communicated with a pipeline where the first cold accumulator (7) is positioned;
controlling the first bypass pipeline to be communicated with the second bypass pipeline;
Starting a bidirectional pump (6);
The refrigerant is controlled to sequentially flow through the bidirectional pump (6), the first heat exchanger (2), the first bypass pipeline, the second heat exchanger (4) and the second bypass pipeline to form a first refrigerant flowing cycle.
12. The control method according to claim 6, wherein the step of controlling the compound refrigeration system to operate in the magnetic refrigeration mode and switching the refrigerant flow path by the bidirectional pump (6) includes:
Controlling the compressor (1) to stop running;
Controlling the first heat exchanger (2) to be communicated with the first cold accumulator (7);
controlling the two-way pump (6) to start;
The pumping direction of the bidirectional pump (6) is controlled according to the working states of the first regenerator (7) and the second regenerator (8).
13. A control method according to claim 12, characterized in that the step of controlling the pumping direction of the bi-directional pump (6) in accordance with the operating conditions of the first regenerator (7) and the second regenerator (8) comprises:
when the first regenerator (7) is magnetized and the second regenerator (8) is demagnetized, the bidirectional pump (6) is controlled to pump out in a first direction;
The refrigerant is controlled to sequentially flow through the bidirectional pump (6), the second cold accumulator (8), the second heat exchanger (4), the first cold accumulator (7) and the first heat exchanger (2) to form refrigerant flowing circulation;
when the first regenerator (7) is demagnetized and the second regenerator (8) is magnetized, the bidirectional pump (6) is controlled to pump out in the second direction;
The refrigerant is controlled to sequentially flow through the bidirectional pump (6), the first heat exchanger (2), the first cold accumulator (7), the second heat exchanger (4) and the second cold accumulator (8) to form refrigerant flowing circulation.
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