CN112594966B - Composite refrigeration system and control method thereof - Google Patents
Composite refrigeration system and control method thereof Download PDFInfo
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- CN112594966B CN112594966B CN202011559584.8A CN202011559584A CN112594966B CN 112594966 B CN112594966 B CN 112594966B CN 202011559584 A CN202011559584 A CN 202011559584A CN 112594966 B CN112594966 B CN 112594966B
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 210
- 239000002131 composite material Substances 0.000 title claims abstract description 62
- 238000000034 method Methods 0.000 title claims abstract description 19
- 238000001816 cooling Methods 0.000 claims abstract description 89
- 239000012530 fluid Substances 0.000 claims abstract description 65
- 239000000463 material Substances 0.000 claims abstract description 25
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 39
- 238000005507 spraying Methods 0.000 claims description 23
- 150000001875 compounds Chemical class 0.000 claims description 22
- 239000007921 spray Substances 0.000 claims description 16
- 238000005086 pumping Methods 0.000 claims description 6
- 238000004891 communication Methods 0.000 claims description 2
- 230000001276 controlling effect Effects 0.000 description 39
- 230000009471 action Effects 0.000 description 9
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 238000005516 engineering process Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 238000012546 transfer Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 239000003507 refrigerant Substances 0.000 description 3
- 238000011161 development Methods 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 230000005389 magnetism Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000696 magnetic material Substances 0.000 description 1
- 239000003595 mist Substances 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
- F25B19/00—Machines, plants or systems, using evaporation of a refrigerant but without recovery of the vapour
- F25B19/02—Machines, plants or systems, using evaporation of a refrigerant but without recovery of the vapour using fluid jet, e.g. of steam
- F25B19/04—Machines, plants or systems, using evaporation of a refrigerant but without recovery of the vapour using fluid jet, e.g. of steam using liquid jet, e.g. of water
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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
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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
- 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 an evaporative cooling system (6) and a magnetic refrigeration system, wherein the magnetic refrigeration system comprises a first pump (1), a first heat exchanger (2), a first cold accumulator (3), a second heat exchanger (4) and a second cold accumulator (5) which are sequentially connected, the evaporative cooling system (6) is configured to perform evaporative cooling on the first heat exchanger (2) so as to adjust the temperature of heat exchange fluid in the first heat exchanger (2), and an outlet of the first pump (1) can be selectively communicated with the first heat exchanger (2) or the second heat exchanger (4). According to the composite refrigeration system, the working temperature of the magnetocaloric material can be improved, the problems of large cold quantity 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 improve the working temperature of a magnetocaloric material, 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 above problems, the present application provides a composite refrigeration system, including an evaporative cooling system and a magnetic refrigeration system, the magnetic refrigeration system includes a first pump, a first heat exchanger, a first regenerator, a second heat exchanger and a second regenerator connected in sequence, the evaporative cooling system is configured to perform evaporative cooling on the first heat exchanger to adjust the temperature of heat exchange fluid in the first heat exchanger, and an outlet of the first pump can be selectively communicated with the first heat exchanger or the second heat exchanger.
Preferably, the first pump is a bi-directional pump.
Preferably, the magnetic refrigeration system further comprises a control valve configured to regulate the flow path of the heat exchange fluid at the outlet of the first pump to enable the outlet of the first pump to selectively communicate with either the first heat exchanger or the second heat exchanger.
Preferably, the evaporative cooling system includes a water tank, a second pump configured to pump water from the water tank to the spray device, the spray device disposed above the first heat exchanger, and the spray device configured to spray the first heat exchanger.
Preferably, the water tank is disposed below the first heat exchanger and recovers spray water of the spray device.
Preferably, the evaporative cooling system further comprises an air inlet and an air outlet, and the first heat exchanger is arranged between the air inlet and the air outlet.
Preferably, the evaporative cooling system further comprises a fan, the air outlet is arranged above the spraying device, the air inlet is arranged corresponding to the bottom of the first heat exchanger, and the fan is arranged at the air outlet.
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; and/or 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 real-time temperature T1 of a refrigerating area;
acquiring a target temperature T3 of a refrigerating area;
judging the relation between the I T3-T1 and a;
when the absolute value T3-T1 is more than a, controlling the composite refrigeration system to operate in a composite refrigeration mode;
when the absolute value T3-T1 is less than or equal to a, controlling the composite refrigeration system to operate in a magnetic refrigeration mode or an evaporative cooling refrigeration mode.
Preferably, the step of controlling the compound refrigeration system to operate in the compound refrigeration mode includes:
Controlling the operation of the evaporative cooling system;
acquiring inlet working temperature ranges T4-T5 of the first regenerator and the second regenerator when the first regenerator and the second regenerator are in a demagnetized state;
Acquiring a real-time temperature T2 of heat exchange fluid in the first heat exchanger;
detecting whether T2 meets T4 and T2 and T5;
If T4 is not more than or equal to T2 and not more than or equal to T5, stopping or not starting the magnetic refrigeration system;
Detecting the real-time temperature T2 of the heat exchange fluid at intervals of delta T2, and judging again until the real-time temperature T2 of the heat exchange fluid meets the condition T4-T2-T5;
If T4 is less than or equal to T2 and less than or equal to T5 is met, starting the magnetic refrigeration system or continuously operating the magnetic refrigeration system;
And reading the real-time temperature T2 of the heat exchange fluid at intervals of delta T3, and judging whether the real-time temperature T2 of the heat exchange fluid meets the condition T4-T2-T5.
Preferably, the step of controlling the compound refrigeration system to operate in a magnetic refrigeration mode or an evaporative cooling refrigeration mode comprises:
Acquiring a real-time temperature T6 of a non-refrigeration area;
Judging the relation between T6 and the set temperature b;
When T6 is less than or equal to b, controlling the composite refrigeration system to operate in an evaporative cooling refrigeration mode;
And when T6 is more than b, controlling the composite refrigeration system to operate in a magnetic refrigeration mode.
Preferably, the step of controlling the compound refrigeration system to operate in an evaporative cooling refrigeration mode includes:
Controlling the first regenerator and the second regenerator to stop working;
Controlling the first pump to operate;
controlling the second pump to run, pumping the water in the water tank to a spraying device above the first heat exchanger, and spraying the first heat exchanger through the spraying device to perform evaporative cooling;
The heat exchange fluid is enabled to flow through the first pump, the first heat exchanger and the second heat exchanger in sequence, so that a flowing cycle is formed.
Preferably, the step of controlling the compound refrigeration system to operate in an evaporative cooling refrigeration mode includes:
Controlling the first regenerator and the second regenerator to stop working;
controlling the first bypass pipeline to be communicated with the second bypass pipeline;
Controlling the first pump to operate;
controlling the second pump to run, pumping the water in the water tank to a spraying device above the first heat exchanger, and spraying the first heat exchanger through the spraying device to perform evaporative cooling;
The heat exchange fluid is enabled to flow through the first pump, the first heat exchanger and the second heat exchanger in sequence, so that a flowing cycle is formed.
Preferably, the step of controlling the compound refrigeration system to operate in the magnetic refrigeration mode includes:
Controlling the evaporative cooling system to stop working;
Acquiring working states of the first regenerator and the second regenerator;
when the first regenerator is demagnetized and the second regenerator is magnetized, the first pump is controlled to operate;
controlling heat exchange fluid to sequentially flow through the first pump, the first heat exchanger, the first regenerator, the second heat exchanger and the second regenerator to form a flowing cycle;
When the first regenerator is magnetized and the second regenerator is demagnetized, the first pump is controlled to operate;
And controlling the heat exchange fluid to sequentially flow through the first pump, the second regenerator, the second heat exchanger, the first regenerator and the first heat exchanger to form a flowing cycle.
The application provides a composite refrigeration system, which comprises an evaporative cooling system and a magnetic refrigeration system, wherein the magnetic refrigeration system comprises a first pump, a first heat exchanger, a first cold accumulator, a second heat exchanger and a second cold accumulator which are sequentially connected, and the evaporative cooling system is configured to perform evaporative cooling on the first heat exchanger. The composite refrigeration system can control the temperature of the fluid in the first heat exchanger through the evaporative cooling system, so that the temperature of the fluid in the first heat exchanger can be regulated to a temperature range in which the magnetocaloric material is suitable for working, the refrigeration efficiency of the composite refrigeration system can be improved, large cold quantity and large temperature span are realized, and the working efficiency of the composite refrigeration system is improved.
Drawings
FIG. 1 is a system configuration diagram of a compound refrigeration system according to one embodiment of the present application;
FIG. 2 is a schematic diagram of a magnetic refrigeration mode of a compound refrigeration system according to an embodiment of the present application;
FIG. 3 is a schematic diagram of an evaporative cooling mode of a compound refrigeration system according to one embodiment of the present application;
FIG. 4 is a system configuration diagram of a compound refrigeration system according to one embodiment of the present application;
fig. 5 is a flowchart illustrating a control method of a composite refrigeration system according to an embodiment of the present application.
The reference numerals are expressed as:
1. a first pump; 2. a first heat exchanger; 3. a first regenerator; 4. a second heat exchanger; 5. a second regenerator; 6. an evaporative cooling system; 61. a water tank; 62. a second pump; 63. a spraying device; 64. a blower; 65. an air inlet; 66. and an air outlet.
Detailed Description
Referring to fig. 1 to 4 in combination, according to an embodiment of the present application, a hybrid refrigeration system includes an evaporative cooling system 6 and a magnetic refrigeration system, the magnetic refrigeration system includes a first pump 1, a first heat exchanger 2, a first regenerator 3, a second heat exchanger 4, and a second regenerator 5 connected in this order, the evaporative cooling system 6 is configured to perform evaporative cooling on the first heat exchanger 2 to adjust a temperature of a heat exchange fluid within the first heat exchanger 2, and an outlet of the first pump 1 is capable of selectively communicating with the first heat exchanger 2 or the second heat exchanger 4.
The working principle of the magnetic refrigeration system in the prior art 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 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.
Because the magnetic refrigeration system is influenced by the existing magnetic refrigeration material, the problem of high difficulty in building a large-temperature span exists, and the popularization and the application of the magnetic refrigeration system are greatly hindered. The present application addresses this problem that exists in magnetic refrigeration systems.
The composite refrigeration system can control the temperature of the fluid in the first heat exchanger 2 through the evaporative cooling system, so that the temperature of the fluid in the first heat exchanger 2 can be regulated to a temperature range in which the magnetocaloric material is suitable for working, the refrigeration efficiency of the composite refrigeration system can be improved, large cold capacity and large temperature span are realized, and the working efficiency of the composite refrigeration system is improved.
In one embodiment, the first pump 1 is a bi-directional pump.
In one embodiment, the first pump 1 may be a unidirectional pump, and the magnetic refrigeration system further comprises a control valve configured to regulate the flow path of the heat exchange fluid at the outlet of the first pump 1 to enable the outlet of the first pump 1 to selectively communicate with the first heat exchanger 2 or the second heat exchanger 4. The first pump 1 adjusts the outlet communication direction by controlling a valve.
The control valve can be formed by a plurality of three-way valves, and can also be realized by adopting a single two-position four-way valve.
In the present application, each embodiment will be described by taking the first pump 1 as a bi-directional pump as an example.
The evaporative cooling system 6 comprises a water tank 61, a second pump 62 and a spray device 63, the second pump 62 being configured to pump water from the water tank 61 to the spray device 63, the spray device 63 being arranged above the first heat exchanger 2, the spray device 63 being configured to spray the first heat exchanger 2.
The water tank 61 is disposed below the first heat exchanger 2, and recovers shower water of the shower device 63.
The evaporative cooling system 6 further includes an air inlet 65 and an air outlet 66, with the first heat exchanger 2 disposed between the air inlet 65 and the air outlet 66.
The evaporative cooling system 6 further includes a fan 64, an air outlet 66 is provided above the shower device 63, an air inlet 65 is provided corresponding to the bottom of the first heat exchanger 2, and the fan 64 is provided at the air outlet 66.
The composite refrigeration system of the embodiment comprises three working modes, namely a magnetic refrigeration mode, an evaporative cooling refrigeration mode and a composite refrigeration mode. Three modes of cooling are described below.
(1) Magnetic refrigeration mode
The working principle of the magnetic refrigeration system in the composite refrigeration system is as follows:
Based on the magnetocaloric effect, when the magnetic field generator magnetizes the regenerator, the magnetocaloric material in the regenerator releases heat outwards, and when the magnetic field generator demagnetizes the regenerator, the magnetocaloric material in the regenerator releases cold outwards. The magnetic field generator of the magnetic refrigeration system in the application carries out the magnetizing action and the demagnetizing action on the first regenerator 3 and the second regenerator 5 according to a preset rule, and the action on the second regenerator 5 is demagnetizing when the magnetic field generator magnetizes the first regenerator 3, whereas the action on the second regenerator 5 is magnetizing when the magnetic field generator demagnetizes the first regenerator 3. Therefore, one half of the cold accumulator in the magnetic refrigeration loop is in a state of magnetism heating and the other half of the cold accumulator is in a state of magnetism removing and cooling at the same time, and the two states can be periodically switched, so that one period of magnetic refrigeration of the loop can be divided into two stages.
The first stage: the magnetic field generator demagnetizes the first regenerator 3 and simultaneously magnetizes the second regenerator 5. When the first regenerator 3 demagnetizes to generate cold energy, the heat exchange fluid flows along the directions of the first pump 1, the first heat exchanger 2, the first regenerator 3 and the second heat exchanger 4 under the action of the first pump 1, so that the heat exchange fluid can transfer the cold energy in the first regenerator 3 to the second heat exchanger 4, and then the heat exchange is carried out between the second heat exchanger 4 and the air in the refrigerating area so as to gradually reduce the temperature in the refrigerating area; at the same time, the second regenerator 5 is magnetized to generate heat, and the heat exchange fluid flows along the direction from the second regenerator 5 to the first pump 1 to the first heat exchanger 2 under the drive of the first pump 1, so that the heat exchange fluid can transfer the heat in the second regenerator 5 to the first heat exchanger 2 and then radiate the heat to a non-refrigeration area through the first heat exchanger 2.
And a second stage: the magnetic field generator magnetizes the first regenerator 3 and simultaneously demagnetizes the second regenerator 5. When the first regenerator 3 is magnetized to generate heat, the heat exchange fluid flows along the direction from the second heat exchanger 4 to the first regenerator 3 to the first heat exchanger 2 under the action of the first pump 1, so that the heat exchange fluid can transfer the heat in the first regenerator 3 to the first heat exchanger 2, and then the heat exchange is performed on the air in the non-refrigeration area through the first heat exchanger 2, so that the heat generated by the system can be dissipated to the non-refrigeration area; at the same time, the second regenerator 5 demagnetizes to generate cold, and the heat exchange fluid flows along the directions of the first pump 1, the second regenerator 5 and the second heat exchanger 4 under the drive of the first pump 1, so that the heat exchange fluid can transfer the cold in the second regenerator 5 to the second heat exchanger 4, and then the heat exchange is performed between the second heat exchanger 4 and the air in the refrigerating area, so that the temperature in the refrigerating area is gradually reduced.
(2) Evaporative cooling mode
When the evaporative cooling system 6 is started, the second pump 62 starts to operate, and lifts the water in the water tank 61 to the spraying device 63 above the first heat exchanger 2 through the pump pressure, the sprayed water is sprayed to the first heat exchanger 2 below through the spraying device 63, the sprayed water falls downwards under the action of gravity in the form of water mist or small water drops, contacts with the outer surface of the first heat exchanger 2 and is attached to the outer surface of the first heat exchanger 2, after the water drops attached to the outer surface of the first heat exchanger 2 evaporate, heat is absorbed from the outside due to phase change, so that the temperature of the first heat exchanger 2 is gradually reduced, and the real-time temperature of the heat exchange fluid inside the first heat exchanger 2 is reduced. In order to accelerate the evaporation rate of the water droplets on the surface of the first heat exchanger 2, a fan 64 is arranged above the first heat exchanger 2, which is started when the evaporative cooling system starts to operate. Under the action of the fan 64, air can enter from an air inlet 65 arranged below the evaporative cooling system, is discharged from an air outlet 66 of the fan 64 after passing through the first heat exchanger 2, improves the evaporation efficiency of the outer surface of the first heat exchanger 2 in a forced air flow mode, and further enables the temperature of heat exchange fluid in the first heat exchanger 2 to be reduced more quickly. At the same time, the first pump 1 is started, and the heat exchange fluid in the magnetic refrigeration system is driven to reciprocate through the pump pressure, so that the cold energy generated by evaporative cooling is transmitted to the second heat exchanger 4, and the refrigeration area is refrigerated.
Wherein the water tank 61 serves to provide a source of water for the second pump 62 and also to receive water dripping from the first heat exchanger 2 above it.
(3) Composite refrigeration mode
Firstly, an evaporative cooling system is started, after the evaporative cooling system starts to operate, the temperature of the first heat exchanger 2 starts to gradually decrease, and meanwhile, the first pump 1 is started to drive heat exchange fluid in the magnetic refrigeration system to reciprocate, so that the temperature of the heat exchange fluid can be reduced more quickly. When the temperature of the heat exchange fluid is reduced to a temperature suitable for the working of the magneto-caloric material of the magnetic refrigeration system, a magnetic field generator of the magnetic refrigeration system is started to magnetize and demagnetize the cold accumulator, the heat exchange fluid transmits cold generated by the magnetic refrigeration to the second heat exchanger 4 under the action of a pump to refrigerate a refrigeration area, and transmits heat generated by the magnetic refrigeration to the first heat exchanger 2 to carry away the heat through evaporative cooling, so that the pre-cooling of the magnetic refrigeration system by the evaporative cooling is realized, the magnetic refrigeration system can work at a proper working temperature of the magneto-caloric material of the magnetic refrigeration system, and the overall efficiency is optimal; meanwhile, when the evaporative cooling system and the magnetic refrigeration system are operated simultaneously, the temperature of the first heat exchanger 2 of the magnetic refrigeration system can be reduced by using the evaporative cooling system, so that the magnetic refrigeration system can obtain a lower cold end temperature.
In order to enable the compound 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 real-time temperature of the heat exchange fluid is arranged in a heat exchange fluid pipeline of the magnetic refrigerating system, and the real-time temperature of the heat exchange fluid detected by the temperature sensor is T2. In addition, the system needs to set the target temperature T3 of the refrigerating area at the starting time and the working temperature range T4-T5 of the magnetocaloric materials used by the system is contained in the controller memory.
Referring to fig. 4 in combination, in another embodiment, which is substantially the same as the first embodiment, except that in this embodiment, a first bypass line A1 is provided in parallel outside the first regenerator 3, and a first control valve S1 is provided on the first bypass line; a second bypass pipeline A2 is arranged outside the second cold accumulator 5 in parallel, and a second control valve S1 is arranged on the second bypass pipeline.
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 A1, and the second control valve S2 to switch on the second bypass pipeline A2, so that the refrigerant can pass through the first bypass pipeline A1 and the second bypass pipeline A2, thereby reducing the pressure resistance of the system and reducing the power consumption of the system.
Referring to fig. 5 in combination, according to an embodiment of the present application, the control method of the above-mentioned composite refrigeration system includes: acquiring a real-time temperature T1 of a refrigerating area; acquiring a target temperature T3 of a refrigerating area; judging the relation between the I T3-T1 and a; when the absolute value T3-T1 is more than a, controlling the composite refrigeration system to operate in a composite refrigeration mode; when the absolute value T3-T1 is less than or equal to a, controlling the composite refrigeration system to operate in a magnetic refrigeration mode or an evaporative cooling refrigeration mode.
The step of controlling the composite refrigeration system to operate in the composite refrigeration mode comprises the following steps: controlling the operation of the evaporative cooling system 6; acquiring the working temperature ranges T4-T5 of inlet magnetocaloric materials of the first regenerator 3 and the second regenerator 5 when the first regenerator is in a demagnetized state; acquiring a real-time temperature T2 of the heat exchange fluid in the first heat exchanger 2; detecting whether T2 meets T4 and T2 and T5; if T4 is not more than or equal to T2 and not more than or equal to T5, stopping or not starting the magnetic refrigeration system; detecting the real-time temperature T2 of the heat exchange fluid at intervals of delta T2, and judging again until the real-time temperature T2 of the heat exchange fluid meets the condition T4-T2-T5; if T4 is less than or equal to T2 and less than or equal to T5 is met, starting the magnetic refrigeration system or continuously operating the magnetic refrigeration system; and reading the real-time temperature T2 of the heat exchange fluid at intervals of delta T3, and judging whether the real-time temperature T2 of the heat exchange fluid meets the condition T4-T2-T5.
The step of controlling the composite refrigeration system to operate in a magnetic refrigeration mode or an evaporative cooling refrigeration mode comprises the following steps: acquiring a real-time temperature T6 of a non-refrigeration area; judging the relation between T6 and the set temperature b; when T6 is less than or equal to b, controlling the composite refrigeration system to operate in an evaporative cooling refrigeration mode; and when T6 is more than b, controlling the composite refrigeration system to operate in a magnetic refrigeration mode.
The step of controlling the composite refrigeration system to operate in an evaporative cooling refrigeration mode comprises the following steps: the first regenerator 3 and the second regenerator 5 are controlled to stop working; controlling the first pump 1 to operate; controlling the second pump 62 to operate, pumping the water in the water tank 61 to a spraying device 63 above the first heat exchanger 2, and spraying the first heat exchanger 2 through the spraying device 63 for evaporative cooling; the heat exchange fluid is caused to flow through the first pump 1, the first heat exchanger 2 and the second heat exchanger 4 in this order, forming a flow cycle.
The step of controlling the composite refrigeration system to operate in an evaporative cooling refrigeration mode comprises the following steps: the first regenerator 3 and the second regenerator 5 are controlled to stop working; controlling the first bypass pipeline to be communicated with the second bypass pipeline; controlling the first pump 1 to operate; controlling the second pump 62 to operate, pumping the water in the water tank 61 to a spraying device 63 above the first heat exchanger 2, and spraying the first heat exchanger 2 through the spraying device 63 for evaporative cooling; the heat exchange fluid is caused to flow through the first pump 1, the first heat exchanger 2 and the second heat exchanger 4 in this order, forming a flow cycle.
The step of controlling the composite refrigeration system to operate in a magnetic refrigeration mode comprises the following steps: controlling the evaporative cooling system 6 to stop working; acquiring the working states of the first regenerator 3 and the second regenerator 5; when the first regenerator 3 is demagnetized and the second regenerator 5 is magnetized, the first pump 1 is controlled to operate; controlling heat exchange fluid to sequentially flow through the first pump 1, the first heat exchanger 2, the first regenerator 3, the second heat exchanger 4 and the second regenerator 5 to form a flowing cycle; when the first regenerator 3 is magnetized and the second regenerator 5 is demagnetized, the first pump 1 is controlled to operate; the heat exchange fluid is controlled to sequentially flow through the first pump 1, the second regenerator 5, the second heat exchanger 4, the first regenerator 3 and the first heat exchanger 2 to form a flow cycle.
After the composite refrigeration system is started, the controller reads the real-time temperature T1 of the refrigeration area obtained from the sensor, and simultaneously reads the target temperature value T3 of the refrigeration area set by a user and the working temperature ranges T4-T5 of the magnetocaloric materials stored in the storage unit in advance. Then the control program judges the running mode, when the difference value |T3-T1| > a between the real-time temperature T1 of the refrigerating area and the target temperature T3 of the refrigerating area, the controller starts the compound refrigerating mode of the third mode, namely, the evaporative cooling system 6 is firstly operated, the heat exchange fluid in the magnetic refrigerating system is pre-cooled through the evaporative cooling system 6, meanwhile, the pump 1 is started, when the real-time temperature T2 of the heat exchange fluid obtained by the controller does not meet the condition that T4 is less than or equal to T2 is less than or equal to T5, the magnetic refrigerating system is started or not started, the real-time temperature T2 of the heat exchange fluid is detected once at intervals of Deltat 2, and judgment is carried out again until the real-time temperature T2 of the heat exchange fluid meets the condition that T4 is less than or equal to T2 is less than or equal to T5. When the real-time temperature T2 of the heat exchange fluid meets the condition T4 and T2 and T5, the magnetic refrigeration system is started and operated, and the evaporative cooling system 6 and the magnetic refrigeration module are operated simultaneously at the moment, so that overlapping of the two refrigeration systems is realized. In the process, the controller can read the real-time temperature T2 of the heat exchange fluid at intervals of delta T3 and judge whether the real-time temperature T2 of the heat exchange fluid meets the condition T4-T2-T5.
After the compound cooling mode is initiated. And when the controller judges that the difference value |T3-T1| between the real-time temperature T1 of the refrigerating area and the target temperature T3 of the refrigerating area is less than or equal to a, starting a default running mode preset by a user. After that, the process is performed. The controller returns to the step of acquiring the real-time temperature T1 of the refrigerating area at intervals of delta T1, reads the temperature T1 of the refrigerating area, and judges the relation between the absolute value T3-T1 and the absolute value a again.
The default operation mode preset by the user refers to the current operation mode preset by the user at the terminal
A mode of default operation when |t3-t1| > a, which is one of an evaporative cooling mode and a magnetic cooling mode, and a user can make a selection setting according to actual conditions.
Specifically, it is determined which of the evaporative cooling mode and the magnetic cooling mode is selected based on the relationship between the real-time temperature T6 of the non-cooling region and the preset temperature b. In the process of selecting the control mode, the real-time temperature T6 of the non-refrigeration area needs to be acquired firstly; then 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 in an evaporative cooling refrigeration mode; when T2 is more than b, the composite refrigeration system is controlled to operate in a magnetic refrigeration mode, so that the composite refrigeration system selects a more proper working mode, the effective refrigeration capacity of the system can be ensured, and the energy consumption can be reduced as much as possible.
By the composite refrigeration system of magnetic refrigeration and evaporative cooling refrigeration and the control method thereof, the system has the following advantages compared with the prior art:
① The evaporative cooling system is used for pre-cooling the magnetic refrigeration system, so that the real-time temperature of heat exchange fluid in the magnetic refrigeration system is reduced to a temperature range where the magnetocaloric material is suitable for working, and the problem of low refrigeration efficiency caused by unsuitable working environment temperature of the magnetocaloric material of the magnetic refrigeration system in the prior art is solved;
② When the heat load is large, a mode of simultaneous operation of magnetic refrigeration and evaporative cooling can be adopted to realize large refrigeration capacity;
③ The method can utilize evaporative cooling to reduce the temperature of the magnetic refrigeration hot end, so that the composite system can realize overlapping of temperature spans, thereby compensating the limitation that the lowest temperature of the evaporative cooling cannot be lower than the wet bulb temperature, and simultaneously solving the problem of difficult realization of the large temperature span of the magnetic refrigeration system.
④ The magnetic refrigeration is a green, efficient and safe refrigeration mode, the evaporative cooling refrigeration is a low-energy, green and safe refrigeration mode utilizing a natural cold source, and a more efficient and green system is realized through the combination of the two modes.
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 (14)
1. A composite refrigeration system is characterized by comprising an evaporative cooling system (6) and a magnetic refrigeration system, wherein the magnetic refrigeration system comprises a first pump (1), a first heat exchanger (2), a first cold accumulator (3), a second heat exchanger (4) and a second cold accumulator (5) which are sequentially connected, the evaporative cooling system (6) is configured to perform evaporative cooling on the first heat exchanger (2) so as to adjust the temperature of heat exchange fluid in the first heat exchanger (2), and an outlet of the first pump (1) can be selectively communicated with the first heat exchanger (2) or the second heat exchanger (4);
The composite refrigeration system further comprises a magnetic field generator, the magnetic field generator can magnetize and demagnetize the first cold accumulator (3) and the second cold accumulator (5) according to a preset rule, when the magnetic field generator magnetizes the first cold accumulator (3), the magnetic field generator demagnetizes the second cold accumulator (5), when the magnetic field generator demagnetizes the first cold accumulator (3), the magnetic field generator magnetizes the second cold accumulator (5), and the states of the first cold accumulator (3) and the second cold accumulator (5) can be periodically switched.
2. A compound refrigeration system as claimed in claim 1, characterized in that the first pump (1) is a bi-directional pump.
3. A compound refrigeration system as claimed in claim 1, characterized in that the magnetic refrigeration system further comprises a control valve configured to regulate the flow path of the heat exchange fluid at the outlet of the first pump (1) so as to enable the outlet of the first pump (1) to be selectively in communication with the first heat exchanger (2) or the second heat exchanger (4).
4. The compound refrigeration system as set forth in claim 1, wherein the evaporative cooling system (6) includes a water tank (61), a second pump (62) and a spray device (63), the second pump (62) being configured to pump water from the water tank (61) to the spray device (63), the spray device (63) being disposed above the first heat exchanger (2), the spray device (63) being configured to spray the first heat exchanger (2).
5. A composite refrigeration system according to claim 4, characterized in that a water tank (61) is arranged below the first heat exchanger (2) and the shower water of the shower device (63) is recovered.
6. The composite refrigeration system of claim 4, wherein the evaporative cooling system (6) further comprises an air intake (65) and an air exhaust (66), and the first heat exchanger (2) is disposed between the air intake (65) and the air exhaust (66).
7. The composite refrigeration system of claim 6, wherein the evaporative cooling system (6) further comprises a fan (64), the air outlet (66) is disposed above the spraying device (63), the air inlet (65) is disposed corresponding to the bottom of the first heat exchanger (2), and the fan (64) is disposed at the air outlet (66).
8. A composite refrigeration system according to claim 1, wherein a first bypass line is arranged in parallel outside the first regenerator (3), the first bypass line being provided with a first control valve; and/or a second bypass pipeline is arranged outside the second cold accumulator (5) in parallel, and a second control valve is arranged on the second bypass pipeline.
9. A control method of a composite refrigeration system according to any one of claims 1 to 8, comprising:
Acquiring a real-time temperature T1 of a refrigerating area;
acquiring a target temperature T3 of a refrigerating area;
judging the relation between the I T3-T1 and a;
when the absolute value T3-T1 is more than a, controlling the composite refrigeration system to operate in a composite refrigeration mode;
when the absolute value T3-T1 is less than or equal to a, controlling the composite refrigeration system to operate in a magnetic refrigeration mode or an evaporative cooling refrigeration mode.
10. The control method of claim 9, wherein the step of controlling the compound refrigeration system to operate in the compound refrigeration mode comprises:
Controlling the operation of the evaporative cooling system (6);
Acquiring working temperature ranges T4-T5 of inlet magnetocaloric materials of the first regenerator (3) and the second regenerator (5) when the first regenerator and the second regenerator are in a demagnetized state;
acquiring a real-time temperature T2 of heat exchange fluid in the first heat exchanger (2);
detecting whether T2 meets T4 and T2 and T5;
If T4 is not more than or equal to T2 and not more than or equal to T5, stopping or not starting the magnetic refrigeration system;
Detecting the real-time temperature T2 of the heat exchange fluid at intervals of delta T2, and judging again until the real-time temperature T2 of the heat exchange fluid meets the condition T4-T2-T5;
If T4 is less than or equal to T2 and less than or equal to T5 is met, starting the magnetic refrigeration system or continuously operating the magnetic refrigeration system;
And reading the real-time temperature T2 of the heat exchange fluid at intervals of delta T3, and judging whether the real-time temperature T2 of the heat exchange fluid meets the condition T4-T2-T5.
11. The method of controlling according to claim 9, wherein the step of controlling the compound refrigeration system to operate in either a magnetic refrigeration mode or an evaporative cooling refrigeration mode comprises:
Acquiring a real-time temperature T6 of a non-refrigeration area;
Judging the relation between T6 and the set temperature b;
When T6 is less than or equal to b, controlling the composite refrigeration system to operate in an evaporative cooling refrigeration mode;
And when T6 is more than b, controlling the composite refrigeration system to operate in a magnetic refrigeration mode.
12. The method of claim 11, wherein the step of controlling the compound refrigeration system to operate in an evaporative cooling refrigeration mode comprises:
The first cold accumulator (3) and the second cold accumulator (5) are controlled to stop working;
Controlling the first pump (1) to operate;
Controlling the second pump (62) to run, pumping the water in the water tank (61) to a spraying device (63) above the first heat exchanger (2), and spraying the first heat exchanger (2) through the spraying device (63) for evaporative cooling;
the heat exchange fluid sequentially flows through the first pump (1), the first heat exchanger (2) and the second heat exchanger (4) to form a flow cycle.
13. The method of claim 11, wherein the step of controlling the compound refrigeration system to operate in an evaporative cooling refrigeration mode comprises:
The first cold accumulator (3) and the second cold accumulator (5) are controlled to stop working;
controlling the first bypass pipeline to be communicated with the second bypass pipeline;
Controlling the first pump (1) to operate;
Controlling the second pump (62) to run, pumping the water in the water tank (61) to a spraying device (63) above the first heat exchanger (2), and spraying the first heat exchanger (2) through the spraying device (63) for evaporative cooling;
the heat exchange fluid sequentially flows through the first pump (1), the first heat exchanger (2) and the second heat exchanger (4) to form a flow cycle.
14. The method of claim 11, wherein the step of controlling the compound refrigeration system to operate in the magnetic refrigeration mode comprises:
controlling the evaporative cooling system (6) to stop working;
acquiring the working states of the first regenerator (3) and the second regenerator (5);
when the first regenerator (3) is demagnetized and the second regenerator (5) is magnetized, the first pump (1) is controlled to operate;
controlling heat exchange fluid to sequentially flow through a first pump (1), a first heat exchanger (2), a first cold accumulator (3), a second heat exchanger (4) and a second cold accumulator (5) to form a flowing cycle;
when the first regenerator (3) is magnetized and the second regenerator (5) is demagnetized, the first pump (1) is controlled to operate;
The heat exchange fluid is controlled to sequentially flow through the first pump (1), the second regenerator (5), the second heat exchanger (4), the first regenerator (3) and the first heat exchanger (2) to form a flow cycle.
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Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2580385A1 (en) * | 1985-04-15 | 1986-10-17 | Commissariat Energie Atomique | Device for refrigeration or heat pumping with a regenerator |
| CN101532752A (en) * | 2009-04-09 | 2009-09-16 | 浙江科技学院 | Room temperature magnetic fluid refrigerating device |
| US20140290275A1 (en) * | 2011-11-24 | 2014-10-02 | Cooltech Applications S.A.S. | Magnetocaloric heat generator |
| CN106662373A (en) * | 2014-07-28 | 2017-05-10 | 美国宇航公司 | Magnetic refrigeration system with separated inlet and outlet flow |
| CN106839505A (en) * | 2017-03-09 | 2017-06-13 | 天津商业大学 | A kind of magnetic refrigerator of magnetic material circulation |
| CN109654765A (en) * | 2018-11-28 | 2019-04-19 | 珠海格力电器股份有限公司 | Magnetic refrigeration equipment and heat exchange system thereof |
| CN109764575A (en) * | 2018-12-15 | 2019-05-17 | 中国科学院理化技术研究所 | A kind of thermoelectric cooling and magnetic cooling couple device |
| CN110953760A (en) * | 2019-12-05 | 2020-04-03 | 珠海格力电器股份有限公司 | Magnetic refrigeration system |
| CN112066590A (en) * | 2020-08-31 | 2020-12-11 | 中国科学院理化技术研究所 | Magnetic refrigeration system capable of precooling magnetic hot working medium |
| CN214307680U (en) * | 2020-12-25 | 2021-09-28 | 珠海格力电器股份有限公司 | Composite refrigeration system |
-
2020
- 2020-12-25 CN CN202011559584.8A patent/CN112594966B/en active Active
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2580385A1 (en) * | 1985-04-15 | 1986-10-17 | Commissariat Energie Atomique | Device for refrigeration or heat pumping with a regenerator |
| CN101532752A (en) * | 2009-04-09 | 2009-09-16 | 浙江科技学院 | Room temperature magnetic fluid refrigerating device |
| US20140290275A1 (en) * | 2011-11-24 | 2014-10-02 | Cooltech Applications S.A.S. | Magnetocaloric heat generator |
| CN106662373A (en) * | 2014-07-28 | 2017-05-10 | 美国宇航公司 | Magnetic refrigeration system with separated inlet and outlet flow |
| CN106839505A (en) * | 2017-03-09 | 2017-06-13 | 天津商业大学 | A kind of magnetic refrigerator of magnetic material circulation |
| CN109654765A (en) * | 2018-11-28 | 2019-04-19 | 珠海格力电器股份有限公司 | Magnetic refrigeration equipment and heat exchange system thereof |
| CN109764575A (en) * | 2018-12-15 | 2019-05-17 | 中国科学院理化技术研究所 | A kind of thermoelectric cooling and magnetic cooling couple device |
| CN110953760A (en) * | 2019-12-05 | 2020-04-03 | 珠海格力电器股份有限公司 | Magnetic refrigeration system |
| CN112066590A (en) * | 2020-08-31 | 2020-12-11 | 中国科学院理化技术研究所 | Magnetic refrigeration system capable of precooling magnetic hot working medium |
| CN214307680U (en) * | 2020-12-25 | 2021-09-28 | 珠海格力电器股份有限公司 | Composite refrigeration system |
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