CN110953740B - Refrigeration system for uniform-temperature cold plate and control method - Google Patents
Refrigeration system for uniform-temperature cold plate and control method Download PDFInfo
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- CN110953740B CN110953740B CN201911341052.4A CN201911341052A CN110953740B CN 110953740 B CN110953740 B CN 110953740B CN 201911341052 A CN201911341052 A CN 201911341052A CN 110953740 B CN110953740 B CN 110953740B
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 17
- 238000000034 method Methods 0.000 title claims abstract description 12
- 239000003507 refrigerant Substances 0.000 claims description 124
- 238000010622 cold drawing Methods 0.000 claims 1
- 239000007788 liquid Substances 0.000 description 15
- 239000012071 phase Substances 0.000 description 12
- 230000003247 decreasing effect Effects 0.000 description 10
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 6
- 229910052802 copper Inorganic materials 0.000 description 6
- 239000010949 copper Substances 0.000 description 6
- 230000017525 heat dissipation Effects 0.000 description 5
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 4
- 229910052782 aluminium Inorganic materials 0.000 description 4
- 229920006395 saturated elastomer Polymers 0.000 description 4
- 239000007791 liquid phase Substances 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 238000001035 drying Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 239000008358 core component Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000004519 grease Substances 0.000 description 1
- 238000003801 milling Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 229920001296 polysiloxane Polymers 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
- 238000004781 supercooling Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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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
- F25B2500/00—Problems to be solved
- F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
- Sorption Type Refrigeration Machines (AREA)
Abstract
The invention discloses a refrigeration system for a uniform temperature cold plate and a control method. Refrigerating system includes compressor, condenser, first throttling arrangement and evaporimeter, wherein, first throttling arrangement front end is equipped with first three-way valve, an export of three-way valve with the entry intercommunication of evaporimeter, another export through first branch road with the middle part pipeline intercommunication of evaporimeter, be equipped with second throttling arrangement on the first branch road. The condenser is characterized in that a second three-way valve is further arranged between the first three-way valve and the second throttling device, an outlet of the second three-way valve is converged with the condenser outlet pipeline through a second branch, and a one-way valve is arranged on the second branch. The temperature change of the evaporator in the whole pipe section is very small, so that the temperature of each part of the cold plate exchanging heat with the evaporator is uniform.
Description
Technical Field
The invention relates to the technical field of air conditioners, in particular to a refrigeration system for a uniform temperature cold plate and a control method.
Background
The photovoltaic inverter is used for converting direct current generated by solar energy into appropriate alternating current so as to meet the core equipment for normal operation of the photovoltaic centrifugal unit. And an Insulated Gate Bipolar Transistor (IGBT) is a core component for realizing current conversion, and the reliable operation of the IGBT determines the performance and the stability of the photovoltaic centrifugal unit.
The IGBT generally adopts a plurality of to work as a group, and single IGBT gives out heat when working great, need dispel the heat to it in order to guarantee that the IGBT is in stable operating condition. It is common practice to mount a set of IGBTs on a cold plate, which is mounted vertically in a control cabinet, and to cool the cold plate via refrigeration equipment.
The existing cold plate is formed by embedding a snakelike copper pipe into a slotted aluminum plate and then pressing the snakelike copper pipe, the snakelike copper pipe is formed by bending a single copper pipe, welding is not needed, and a refrigerant flows in the snakelike copper pipe; the surface of the aluminum plate is processed by a milling machine to form a snake-shaped groove, and a screw hole is processed on the aluminum plate by a drilling machine. IGBT leans on the screw to fasten on aluminum plate surface, and the coating has heat conduction silicone grease between IGBT and cold plate surface, and the heat that every IGBT produced is taken away by the refrigerant in the copper pipe. The surface temperature of the IGBT is required to be not higher than 85 ℃, and the surface of the cold plate cannot be condensed. A plurality of IGBTs, for example 6, are arranged on one cold plate in three rows and two columns. The IGBT is a key part for controlling power conversion of the photovoltaic solar air conditioner, and when the unit works at full load, the IGBT close to the refrigerant outlet can cause temperature exceeding due to insufficient heat dissipation, and cannot work normally. Because the existing cold plate is unreasonable in design, the temperature uniformity of the IGBT is difficult to control when the unit operates, the problem of surface condensation of the cold plate is caused, and the use safety of an electric appliance is seriously damaged.
Therefore, solving the temperature uniformity between the IGBTs in the heat dissipation process is an urgent technical problem to be solved in the industry.
Disclosure of Invention
The invention provides a refrigeration system for a uniform-temperature cold plate and a control method, which aim to solve the technical problem of non-uniform heat dissipation temperature of the cold plate in the prior art.
The technical scheme adopted by the invention is that the refrigerating system for the uniform temperature cold plate comprises a compressor, a condenser, a first throttling device and an evaporator, wherein a first three-way valve is arranged at the front end of the first throttling device, one outlet of the three-way valve is communicated with an inlet of the evaporator, the other outlet of the three-way valve is communicated with a middle pipeline of the evaporator through a first branch, and a second throttling device is arranged on the first branch.
Still be equipped with the second three-way valve between first three-way valve and the second throttling arrangement, an export of second three-way valve through the second branch road with condenser outlet pipeline joins, be equipped with the check valve on the second branch road.
Preferably, the heat recovery system further comprises a heat regenerator for exchanging heat with the refrigerant before throttling, a third three-way valve is arranged on an outlet pipeline of the evaporator, one outlet of the third three-way valve is communicated with an air inlet pipeline of the compressor, the other outlet of the third three-way valve is communicated with an inlet of the heat regenerator, and an outlet of the heat regenerator is converged with the air inlet pipeline of the compressor.
Preferably, the condensation rear end is provided with a reservoir and a dry filter.
And a first pressure sensor and a first temperature sensor are arranged in the middle of the evaporator.
And a second pressure sensor and a second temperature sensor are arranged on an outlet pipeline of the evaporator.
And a third pressure sensor and a third temperature sensor are arranged on the air inlet pipeline of the compressor.
The invention also provides a control method for the refrigeration system, which detects the pressure and the temperature of the refrigerant on the middle part of the evaporator and the outlet pipeline in real time, compares the detected value with a set target value, and controls the flow of the refrigerant entering the inlet of the evaporator and the flow of the refrigerant entering the middle part of the evaporator according to the comparison result.
In one embodiment, the control method includes:
(1) the flow of the first throttling device is controlled by a pressure value P1 at the middle part of the evaporator, and when the pressure value P1 is larger than a set target value PInWhen the first throttle valve is opened, the opening degree of the first throttle device is reduced; when the pressure value P1 is less than the set target value PInIncreasing the opening degree of the first throttling device; when pressure is appliedThe value P1 is equal to the set target value PInWhen the first throttling device is opened, the opening degree of the first throttling device is kept unchanged;
(2) controlling the flow rate of the first throttling device through a temperature value T1 at the middle part of the evaporator, and when the temperature value T1 is larger than a set target value TInWhen the refrigerant flows to the first throttling device, the flow of the refrigerant flowing to the first throttling device by the first three-way valve is increased; when temperature value T1 is equal to set target value TInWhen the refrigerant flows to the first throttling device, the flow of the refrigerant flowing to the first throttling device by the first three-way valve is reduced;
(3) controlling the flow rate of the second throttling device by the pressure value P2 when the pressure value P2 is larger than the set target value PGo outWhen the second throttle device is opened, the opening degree of the second throttle device is reduced; when the pressure value P2 is less than the set target value PGo outIncreasing the opening degree of the second throttling device; when the pressure value P2 is equal to the set target value PGo outWhen the opening degree of the second throttling device is not changed, the opening degree of the second throttling device is maintained;
(4) controlling the flow rate of the first throttling device through a temperature value T2 on an outlet pipeline of the evaporator, and when the temperature value T2 is larger than a set target value TGo outWhen the refrigerant flows to the second throttling device, the flow of the refrigerant flowing to the second throttling device by the second three-way valve is increased; when temperature value T2 is equal to set target value TGo outWhen the refrigerant flows to the second throttling device, the flow of the refrigerant flowing to the second throttling device by the second three-way valve is reduced.
The control method provided by the invention also comprises the step of controlling the superheat degree of the refrigerant at the air suction port of the compressor, and the specific steps are as follows:
(1) when the detected suction superheat degree of the refrigerant is less than the set superheat degree, the flow of the refrigerant flowing to the heat regenerator by the third three-way valve is increased;
(2) when the detected suction superheat degree of the refrigerant is larger than the set superheat degree, reducing the refrigerant flow of the third three-way valve flowing to the heat regenerator;
(3) when the detected degree of superheat of the sucked refrigerant is equal to the set degree of superheat, the opening degree of the third three-way valve is maintained.
Compared with the prior art, the invention has the following beneficial effects:
the temperature change of the refrigerating system in the whole pipe section of the evaporator is very small and uniform, so that the temperature of each part of the cold plate exchanging heat with the refrigerating system is uniform, and the uniform heat dissipation of the IGBT on the cold plate is ensured.
Drawings
Fig. 1 is a system diagram of a refrigeration system of the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in detail with reference to the accompanying drawings and examples. It should be understood that the following specific examples are only for illustrating the present invention and are not to be construed as limiting the present invention.
In the refrigeration system, the throttled refrigerant is in a low-temperature low-pressure gas-liquid two-phase state, the refrigerant absorbs heat of a cooled object in an evaporator, the low-temperature low-pressure liquid-phase refrigerant is continuously evaporated to be changed into a low-temperature low-pressure gas-phase refrigerant, the temperature of the refrigerant is kept unchanged during the period, and when the refrigerant is completely absorbed and evaporated to be changed into the low-temperature low-pressure gas-phase refrigerant, the heat of the cooled object is absorbed again, the temperature of the refrigerant is increased, and the reason for uneven temperature of the cold plate is also the reason for. In order to solve the problem, the refrigeration system provided by the invention is provided with a branch, and the refrigerant in a low-temperature and low-pressure gas-liquid two-phase state after partial throttling is introduced from the middle part of the evaporator, so that the refrigerant in the liquid-cooled plate evaporator is continuously kept in a gas-liquid two-phase state, and the temperature of the refrigerant is continuously kept unchanged during the period of absorbing the heat of a cooled object.
The refrigeration system for the temperature equalizing cold plate comprises a compressor 1, a condenser 2, a first throttling device 3 and an evaporator 4. The front end of the first throttling device is provided with a first three-way valve V1, one outlet of the three-way valve is communicated with the inlet of the evaporator, and the other outlet of the three-way valve is communicated with the middle position 6 of the evaporator through a first branch 5. The first branch is provided with a second three-way valve V2 and a second throttling device 7. One outlet of the second three-way valve V2 leads to a second throttling device, and the other outlet merges with the outlet pipe of the condenser 2 through a second branch 8, on which a one-way valve 9 is arranged. The outlet pipeline of the condenser is provided with a liquid storage device 10 and a drying filter 11.
The refrigerating system also comprises a heat regenerator 12 for exchanging heat with the refrigerant before throttling, a third three-way valve V3 is arranged on an outlet pipeline of the evaporator, one outlet of the third three-way valve V3 is communicated with an air inlet pipeline of the compressor, the other outlet of the third three-way valve V3 is communicated with an inlet of the heat regenerator, and the outlet of the third three-way valve V3 is converged with the air inlet pipeline of the compressor.
The middle part of the evaporator is provided with a first pressure sensor and a first temperature sensor, and the outlet pipeline is provided with a second pressure sensor and a second temperature sensor. And a third pressure sensor and a third temperature sensor are arranged on the air inlet pipeline of the compressor.
The three-way valve in the invention adopts an electric proportional control three-way valve, the throttling device adopts an electronic expansion valve, and the heat regenerator adopts a plate heat exchanger.
The refrigeration system for a cold plate according to the present invention operates in the following modes:
during the refrigerating operation of the system, the first three-way valve V1, the second three-way valve V2, the third three-way valve V3, the first throttle valve 3 and the second throttle valve 7 in the system are kept in an operating state. The first three-way valve V1 is used for adjusting and distributing the proportion of the refrigerant passing through the heat regenerator 12, and adjusting the proportion of the refrigerant flow to the corresponding pipeline of the first throttling device 3 according to the requirement; the second three-way valve V2 is used for readjusting and distributing the flow of the refrigerant flowing through the first three-way valve V1, and adjusting the flow of the refrigerant to the corresponding pipeline of the second throttling device 7 according to the demand; the third three-way valve V3 is used to proportionally adjust and distribute the refrigerant flowing out of the evaporator pipeline and proportionally adjust the flow of the refrigerant flowing to the corresponding pipeline of the heat regenerator according to the requirement.
High-temperature and high-pressure refrigerant gas from the compressor 1 flows through the condenser 2 for heat exchange and is condensed into medium-temperature and high-pressure refrigerant, and then the medium-temperature and high-pressure refrigerant gas passes through the liquid accumulator 10 and the drying filter 11 and then passes through the heat regenerator 12 for heat exchange with part of refrigerant introduced from the outlet of the evaporator, so that the supercooling degree of the gas at the inlet of the compressor is increased. The refrigerant at the outlet of the heat regenerator is divided into three paths by a first three-way valve V1 and a second three-way valve V2, wherein the two paths flow through the pipelines corresponding to the first throttling device 3 and the second throttling device 7, and the other path flows through a one-way valve 9 and then is converged into the liquid accumulator together with the refrigerant at the outlet pipeline of the condenser 2. The refrigerant passing through the first throttling device 3 enters from the inlet of the evaporator 4, and the refrigerant passing through the second throttling device 7 enters from the middle part of the evaporator, so that the temperature of the cold plates exchanging heat with the refrigerant is kept uniform. The refrigerant from the evaporator is divided into two paths after flowing through a third three-way valve V3, one path flows to the suction port of the compressor, and the other path flows through the heat regenerator 12 to absorb heat and then is converged with the refrigerant at the suction port of the compressor, so that the refrigerant at the inlet of the compressor is ensured to keep a certain superheat degree, and the phenomenon of liquid impact of the compressor is avoided. The refrigeration system is provided with sufficient refrigerant flow to ensure normal uniform temperature operation of the liquid cold plate, and when the heat load of the cold plate is relatively low, the redundant refrigerant flow can flow to the liquid accumulator 10 through the second three-way valve V2 and the second branch 8.
The temperature equalization of the evaporator exchanging heat with the cold plate is controlled as follows:
a temperature sensor and a pressure sensor are respectively arranged at the middle position 6 of the pipeline of the evaporator; a temperature sensor and a pressure sensor are arranged at the outlet pipe section of the evaporator. The refrigerant throttled by the first throttling device 3 is in a low-temperature and low-pressure gas-liquid two-phase state, enters from an inlet of the evaporator, exchanges heat with the cold plate, absorbs the heat of the IGBT on the cold plate, is continuously evaporated from a low-temperature and low-pressure liquid phase to become a low-temperature and low-pressure gas-phase refrigerant, the temperature of the refrigerant is kept unchanged during the period, and the temperature of the refrigerant is increased when the refrigerant is completely evaporated to become the low-temperature and low-pressure gas-phase refrigerant and then absorbs the heat of a cooled object. In order to keep the temperature of the cold plate uniform, the invention leads the low-temperature low-pressure gas-liquid two-phase state refrigerant throttled by the first branch 5 and the second throttling device 7 into the middle part of the evaporator to be merged with the refrigerant passing through the inlet of the evaporator, so that the refrigerant in the evaporator is continuously kept in the gas-liquid two-phase state, and the temperature of the refrigerant is kept unchanged during the heat exchange with the cold plate. The temperature equalization control mode is as follows:
(1) the flow rate of the first throttle device 3 is controlled by the refrigerant pressure value P1. An appropriate refrigerant pressure target value P is set for the middle position of the evaporator according to the requirementInThe target value corresponds to a refrigerant evaporation temperature greater than the air dew point temperature.If the pressure value P1 is detected to be greater than the target value PInThen, the opening degree of the first throttle device 3 is decreased so that the pressure value P1 is decreased to the target value PIn(ii) a If the detected pressure value P1 is equal to the target value PInThen, the opening degree of the first throttle device 3 is kept constant, so that the pressure value P1 is stabilized at the target value PIn(ii) a If the detected pressure value P1 is less than the target value PInThen, the opening degree of the first throttle device 3 is increased so that the pressure value P1 rises to the target value PIn。
(2) The flow rate of the first throttle 3 is controlled by the refrigerant temperature value T1. Setting a suitable target value T of the refrigerant temperature according to the requirementInThe temperature target value is equal to the refrigerant saturation temperature value corresponding to the pressure value P1, and the refrigerant state in the middle of the evaporator is ensured to be a saturated gas-liquid two-phase state. If the detected temperature value T1 is greater than the target temperature value TInAt this time, the flow rate of the refrigerant flowing to the first throttling device 3 by the first three-way valve is increased (while the flow rate flowing to the second three-way valve 7 is decreased) so that the temperature value T1 is decreased to the target value TIn(ii) a If the detected temperature value T1 is equal to the target value TInAt this time, the flow rate of the refrigerant flowing to the branch of the first throttle device 3 by the first three-way valve 1 is decreased (while the flow rate to the second three-way valve 7 is increased) until the temperature value T1 rises to the critical point, so that the temperature value T1 is maintained at the target value T1In. The refrigerant temperature T1 at the middle position of the evaporator is only saturated and superheated, so the temperature value of the temperature value T1 is only greater than or equal to the refrigerant saturation temperature corresponding to the pressure value P1.
(3) The flow rate of the second throttle device 7 is controlled by the refrigerant pressure value P2. An appropriate target pressure value P2 of the refrigerant is set according to the demand, and the target pressure value is equal to the target pressure value corresponding to the pressure value P1. If the detected pressure value P2 is greater than the pressure target value PGo outThen, the opening degree of the second throttle device 7 is decreased so that the pressure value P2 is decreased to the pressure target value PGo out(ii) a If the detected pressure value P2 is equal to the target pressure value PGo outThen, the opening degree of the second throttle device 7 is kept constant, so that the pressure value P2 is stabilized at the pressure targetValue PGo out(ii) a If the detected pressure value P2 is less than the target pressure value PGo outThen, the opening degree of the second throttle device 7 is increased so that the pressure value P2 rises to the pressure target value PGo out。
(4) The flow rate of the second throttle device 7 is controlled by the refrigerant temperature T2. Setting a suitable target value T of the refrigerant temperature according to the requirementGo outThe target temperature value is equal to the refrigerant saturation temperature corresponding to the pressure value P2, and the refrigerant temperature value T2 at the evaporator outlet is ensured to be in a saturated gas-liquid two-phase state. If the detected temperature value T2 is greater than the target temperature value TGo outAt this time, the flow rate of the refrigerant flowing through the branch of the second three-way valve 7 to the second throttle device 7 is increased (while the flow rate of the refrigerant flowing through the check valve line is decreased) so that the temperature value T2 is decreased to the target temperature value TGo out(ii) a If the detected temperature value T2 is equal to the target temperature value TGo outThen, the refrigerant flow rate of the branch of the second three-way valve V2 to the second throttling device 7 is decreased (while the refrigerant flow rate to the check valve line is increased) until the temperature value T2 rises to the critical point, so that the temperature value T2 at the evaporator outlet is maintained at the target value TGo out(ii) a The refrigerant at the outlet of the evaporator is saturated and superheated, so that the temperature value T2 is only equal to or higher than the saturation temperature of the refrigerant corresponding to the pressure P2.
The superheat degree of the refrigerant at the air suction port of the compressor is controlled as follows:
the refrigerant at the air suction port of the compressor needs to ensure a certain superheat degree to prevent the liquid-phase refrigerant from causing liquid impact on the compressor and further damaging the compressor. Typically, the unit will set an appropriate compressor suction refrigerant superheat. Suction superheat degree T of the systemFor treatingTemperature T3-the refrigerant saturation temperature for pressure P3.
(1) When the actual superheat degree of the refrigerant at the air suction port is less than the set superheat degree of the refrigerant at the air suction port, the refrigerant flow flowing to the heat regenerator by the third three-way valve V3 is increased, so that more heat is absorbed by the heat regenerator, the superheat degree of the refrigerant at the air suction port is improved, and the set superheat degree value of the refrigerant at the air suction port is reached;
(2) all right fruitsSuperheat T of the refrigerant at the inletFor treatingWhen the degree of superheat of the suction port refrigerant is set, the opening degree of the third three-way valve V3 is kept unchanged;
(3) when the actual degree of superheat T of the refrigerant in the suction portFor treatingWhen the superheat degree of the refrigerant at the air suction port is higher than the set superheat degree of the refrigerant at the air suction port, the flow of the refrigerant flowing to the heat regenerator by the third three-way valve V3 is reduced, so that the heat absorption of the refrigerant in the heat regenerator is reduced, the superheat degree of the refrigerant at the air suction port is reduced, and the superheat degree of the refrigerant at the air suction port is reduced to the set superheat degree value.
The refrigeration system and the control method provided by the invention enable the temperature of the cold plate on which the control element is arranged to be uniform during the heat dissipation of the evaporator, thereby ensuring that the photovoltaic centrifugal unit is in a good working state and stability.
The foregoing is considered as illustrative only of the embodiments of the invention. It should be understood that any modifications, equivalents and changes made within the spirit and framework of the inventive concept are intended to be included within the scope of the present invention.
Claims (8)
1. The utility model provides a refrigerating system for samming cold drawing, includes compressor, condenser, first throttling arrangement and evaporimeter, its characterized in that, first throttling arrangement front end is equipped with first three-way valve, an export of three-way valve with the entry intercommunication of evaporimeter, another export through first branch road with the middle part pipeline intercommunication of evaporimeter, be equipped with second throttling arrangement on the first branch road, first three-way valve with still be equipped with the second three-way valve between the second throttling arrangement, an export of second three-way valve pass through the second branch road with condenser outlet pipeline joins, be equipped with the check valve on the second branch road.
2. The refrigeration system according to claim 1 further comprising a regenerator for exchanging heat with the refrigerant prior to throttling, said evaporator outlet conduit having a third three-way valve with one outlet communicating with the compressor inlet conduit and another outlet communicating with said regenerator inlet and merging with the compressor inlet conduit at said regenerator outlet.
3. The refrigeration system of claim 1 wherein said condenser is provided with an accumulator and a dry filter at a rear end thereof.
4. The refrigeration system as set forth in claim 1, wherein said evaporator is provided at a middle portion thereof with a first pressure sensor and a first temperature sensor.
5. The refrigerant system as set forth in claim 1, wherein said evaporator outlet conduit is provided with a second pressure sensor and a second temperature sensor.
6. The refrigerant system as set forth in claim 1, wherein a third pressure sensor and a third temperature sensor are provided on said compressor inlet duct.
7. A control method of a refrigerating system as recited in any one of claims 1 to 6, wherein the pressure and temperature of the refrigerant in the central portion of the evaporator and the outlet pipe are detected in real time, the detected values are compared with a set target value, and the flow rate of the refrigerant into the inlet of the evaporator and the flow rate into the central portion of the evaporator are controlled based on the comparison result, comprising:
(1) the flow of the first throttling device is controlled by a pressure value P1 at the middle part of the evaporator, and when the pressure value P1 is larger than a set target value PInWhen the first throttle valve is opened, the opening degree of the first throttle device is reduced; when the pressure value P1 is less than the set target value PInIncreasing the opening degree of the first throttling device; when the pressure value P1 is equal to the set target value PInWhen the first throttling device is opened, the opening degree of the first throttling device is kept unchanged;
(2) controlling the flow rate of the first throttling device through a temperature value T1 at the middle part of the evaporator, and when the temperature value T1 is larger than a set target value TInWhen the refrigerant flows to the first throttling device, the flow of the refrigerant flowing to the first throttling device by the first three-way valve is increased; when temperature value T1 is equal to set target value TInWhen the refrigerant flows to the first throttling device, the flow of the refrigerant flowing to the first throttling device by the first three-way valve is reduced;
(3) controlling the flow rate of the second throttling device by the pressure value P2 when the pressure value P2 is larger than the set target value PGo outWhen the second throttle device is opened, the opening degree of the second throttle device is reduced; when the pressure value P2 is less than the set target value PGo outIncreasing the opening degree of the second throttling device; when the pressure value P2 is equal to the set target value PGo outWhen the opening degree of the second throttling device is not changed, the opening degree of the second throttling device is maintained;
(4) controlling the flow rate of the second throttling device through a temperature value T2 on an outlet pipeline of the evaporator, and when the temperature value T2 is larger than a set target value TGo outWhen the refrigerant flows to the second throttling device, the flow of the refrigerant flowing to the second throttling device by the second three-way valve is increased; when temperature value T2 is equal to set target value TGo outWhen the refrigerant flows to the second throttling device, the flow of the refrigerant flowing to the second throttling device by the second three-way valve is reduced.
8. The control method as set forth in claim 7, further comprising controlling a superheat of refrigerant at a suction port of the compressor by:
(1) when the detected suction superheat degree of the refrigerant is less than the set superheat degree, the flow of the refrigerant flowing to the heat regenerator by the third three-way valve is increased;
(2) when the detected suction superheat degree of the refrigerant is larger than the set superheat degree, reducing the refrigerant flow of the third three-way valve flowing to the heat regenerator;
(3) when the detected degree of superheat of the sucked refrigerant is equal to the set degree of superheat, the opening degree of the third three-way valve is maintained.
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08152202A (en) * | 1994-11-28 | 1996-06-11 | Sanyo Electric Co Ltd | Air conditioner |
| JPH10281580A (en) * | 1997-04-03 | 1998-10-23 | N T T Facilities:Kk | Absorption freezer |
| CN103363704A (en) * | 2013-06-26 | 2013-10-23 | 青岛澳柯玛超低温冷冻设备有限公司 | Connection system structure and operation method for evaporators in refrigeration equipment |
| CN108981246A (en) * | 2018-09-18 | 2018-12-11 | 长虹美菱股份有限公司 | A kind of refrigeration system and its control method |
-
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08152202A (en) * | 1994-11-28 | 1996-06-11 | Sanyo Electric Co Ltd | Air conditioner |
| JPH10281580A (en) * | 1997-04-03 | 1998-10-23 | N T T Facilities:Kk | Absorption freezer |
| CN103363704A (en) * | 2013-06-26 | 2013-10-23 | 青岛澳柯玛超低温冷冻设备有限公司 | Connection system structure and operation method for evaporators in refrigeration equipment |
| CN108981246A (en) * | 2018-09-18 | 2018-12-11 | 长虹美菱股份有限公司 | A kind of refrigeration system and its control method |
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Denomination of invention: Refrigeration system and control method for uniform temperature cooling plate Effective date of registration: 20230106 Granted publication date: 20201110 Pledgee: Agricultural Bank of China Limited Zhuhai Jida Sub-branch Pledgor: GREE ELECTRIC APPLIANCES,Inc.OF ZHUHAI Registration number: Y2022980029496 |