CN116817477B - Liquid cooling air conditioner refrigerating system and control method thereof - Google Patents
Liquid cooling air conditioner refrigerating system and control method thereof Download PDFInfo
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- CN116817477B CN116817477B CN202311109265.0A CN202311109265A CN116817477B CN 116817477 B CN116817477 B CN 116817477B CN 202311109265 A CN202311109265 A CN 202311109265A CN 116817477 B CN116817477 B CN 116817477B
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- 238000001816 cooling Methods 0.000 title claims abstract description 24
- 239000007788 liquid Substances 0.000 title claims abstract description 22
- 238000000034 method Methods 0.000 title claims abstract description 20
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 153
- 229910052731 fluorine Inorganic materials 0.000 claims abstract description 43
- 239000011737 fluorine Substances 0.000 claims abstract description 43
- YCKRFDGAMUMZLT-UHFFFAOYSA-N Fluorine atom Chemical compound [F] YCKRFDGAMUMZLT-UHFFFAOYSA-N 0.000 claims abstract description 42
- 230000001105 regulatory effect Effects 0.000 claims description 64
- 239000003507 refrigerant Substances 0.000 claims description 27
- 238000005057 refrigeration Methods 0.000 claims description 16
- 230000003828 downregulation Effects 0.000 claims description 4
- 230000003827 upregulation Effects 0.000 claims 1
- 238000010586 diagram Methods 0.000 description 7
- 238000004378 air conditioning Methods 0.000 description 4
- 238000002347 injection Methods 0.000 description 4
- 239000007924 injection Substances 0.000 description 4
- 101000927062 Haematobia irritans exigua Aquaporin Proteins 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 230000003287 optical effect Effects 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000001035 drying Methods 0.000 description 1
- 238000012983 electrochemical energy storage Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 125000001153 fluoro group Chemical group F* 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
Classifications
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- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M10/00—Secondary cells; Manufacture thereof
- H01M10/60—Heating or cooling; Temperature control
- H01M10/61—Types of temperature control
- H01M10/613—Cooling or keeping cold
-
- 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
-
- 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
- F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
-
- 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
- F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
-
- 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
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M10/00—Secondary cells; Manufacture thereof
- H01M10/60—Heating or cooling; Temperature control
- H01M10/65—Means for temperature control structurally associated with the cells
- H01M10/656—Means for temperature control structurally associated with the cells characterised by the type of heat-exchange fluid
- H01M10/6567—Liquids
- H01M10/6568—Liquids characterised by flow circuits, e.g. loops, located externally to the cells or cell casings
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M10/00—Secondary cells; Manufacture thereof
- H01M10/60—Heating or cooling; Temperature control
- H01M10/66—Heat-exchange relationships between the cells and other systems, e.g. central heating systems or fuel cells
- H01M10/663—Heat-exchange relationships between the cells and other systems, e.g. central heating systems or fuel cells the system being an air-conditioner or an engine
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M6/00—Primary cells; Manufacture thereof
- H01M6/50—Methods or arrangements for servicing or maintenance, e.g. for maintaining operating temperature
- H01M6/5038—Heating or cooling of cells or batteries
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- Engineering & Computer Science (AREA)
- Manufacturing & Machinery (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Electrochemistry (AREA)
- General Chemical & Material Sciences (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention discloses a liquid cooling air conditioner refrigerating system and a control method thereof, wherein a second waterway for independently performing water flow circulation heat exchange is added in a liquid cooling air conditioner unit, so that the second waterway is opened under the condition that the low pressure of a fluorine path part is high, and the water flow direction and the water flow rate of self-circulation flowing in the second waterway are controlled through a proportional flow three-way valve, a second water pump and a plurality of switches of electromagnetic valves, so as to reduce the water inlet temperature of a first plate change, thereby reducing the low pressure of a compressor.
Description
Technical Field
The invention relates to the technical field of liquid cooling air conditioner refrigeration, in particular to a liquid cooling air conditioner refrigeration system and a control method thereof.
Background
The current optical communication market has better prospect, the demand on the optical module in the market is very large, the battery temperature control scheme used in the current domestic and foreign electrochemical energy storage industry uses a liquid cooling scheme, the system mainly comprises a waterway and a fluorine path, the waterway is mainly used for carrying out heat exchange and cooling on the refrigerant in the fluorine path, and the cooled refrigerant flows back to the compressor and then cools the compressor.
The working principle is that when the system is in operation, heat absorbed by the evaporator from the refrigerant circulation system absorbs heat through evaporation of the refrigerant, the refrigerant enters the condenser after being compressed by the compressor, the heat is released to the surrounding air environment through condensation of the refrigerant, the condensed refrigerant returns to the evaporator through the expansion valve and is then evaporated, the refrigerant circulates and reciprocates in this way, after the heat absorbed by the battery cold plate is released through the evaporator, the power generated by the operation of the water pump is utilized by the refrigerant, and the heat generated in the battery charge and discharge process is absorbed in the cold plate again.
The evaporator is mainly a plate heat exchanger in practical application, one side of the plate heat exchanger is a waterway and the other side of the plate heat exchanger is a fluorine path, namely, the refrigerant in the other side of the plate heat exchanger is cooled by water flow in the waterway at one side. Only a single plate heat exchanger is arranged between a waterway and a fluorine path of the traditional liquid cooling air conditioning system, and the scheme can inhibit the operation of the system to cause that equipment cannot dissipate heat when the high water temperature is more than 30 ℃ in practical application so as to protect the reliability of a compressor; meanwhile, the scheme allows the system to operate, the temperature of the compressor is high at the moment and exceeds the allowable range of the compressor, the reliability of the compressor cannot be ensured, and the compressor is damaged when the compressor operates for a long time.
Disclosure of Invention
In order to overcome the problems in the related art, the invention provides a liquid cooling air conditioner refrigerating system and a control method thereof. The technical scheme is as follows:
according to an embodiment of the present invention, there is provided a liquid-cooled air conditioner refrigeration system, including: the first waterway, the second waterway and the fluorine path part are respectively connected with the first waterway and the fluorine path part; the first waterway comprises a first water pump; the fluorine path part comprises a first plate heat exchanger; the second waterway is provided with at least three flow paths, the upper flow path is provided with an upper flow solenoid valve, the lower flow path is provided with a lower flow solenoid valve, and the middle flow path comprises a second plate heat exchanger, a second water pump, a proportional three-way flow regulating valve and at least three middle flow solenoid valves.
Further, the first waterway comprises a water return port and a water outlet, and water flows from the water return port to the water outlet; the second waterway is independent of the first waterway and is a self-circulation waterway; the refrigerant of the fluorine path part exchanges heat with the water flow of the first waterway or the second waterway through the first plate heat exchanger.
Further, the proportional three-way flow regulating valve is divided into a left way, a right way and an upper way; the proportion range of the proportion three-way flow regulating valve is 0 to 1; when the proportion of the proportion three-way flow regulating valve is 0, the right path and the upper path are completely conducted; when the proportion of the proportion three-way flow regulating valve is 1, the left path and the right path are completely conducted; when the proportion of the proportion three-way flow regulating valve is between 0 and 1, the right way is completely conducted, and the left way and the upper way are partially conducted.
Further, the second waterway further comprises a backwater sensor; the fluorine circuit section also includes a compressor, a condenser, and an electronic expansion valve.
The embodiment of the invention also provides a liquid cooling air conditioner refrigeration control method which is applied to the liquid cooling air conditioner refrigeration system, and comprises the steps of starting the first water pump, the upper electromagnetic valve and the lower electromagnetic valve, and enabling the second water pump and the plurality of middle electromagnetic valves to be in a closed state; and acquiring backwater temperature through the first setting time, respectively adjusting the starting or closing of the first water pump, the second water pump, the upper solenoid valve, the plurality of middle solenoid valves and the lower solenoid valve, and setting the proportion of the proportion three-way flow regulating valve.
Further, the second setting time is used for obtaining the current low pressure value of the refrigerating system, and the adjustment proportion of the proportional three-way flow regulating valve is set according to the low pressure difference value between the current low pressure value and the set target low pressure value; if the low pressure difference value is larger than 0, the adjusting proportion is a positive value; if the low pressure difference value is smaller than 0, the adjusting proportion is a negative value; and if the low pressure difference value between the current low pressure and the set target low pressure is 0, the adjusting ratio is 0.
Further, when the backwater temperature is greater than or equal to the first temperature, setting the proportion of the proportion three-way flow regulating valve to be 0; when the temperature of the backwater is lower than the second temperature, setting the proportion of the proportion three-way flow regulating valve to be 1; the first temperature is greater than the second temperature; when the backwater temperature is between the second temperature and the first temperature, including the second temperature, a plurality of temperature intervals are arranged between the second temperature and the first temperature, and the plurality of temperature intervals are provided with the corresponding proportion of the proportion three-way flow regulating valve.
Further, if the low differential pressure value is smaller than the first differential value, setting the highest positive adjustment proportion; if the low pressure difference value is larger than the second difference value, setting a negative regulation proportion with the highest absolute value; the first difference is smaller than 0, and the second difference is larger than 0; if the low differential pressure value is between the first differential value and 0, setting a plurality of negative differential value intervals and corresponding positive adjustment proportions; if the low differential pressure value is between 0 and the second differential value, a plurality of positive differential value intervals and corresponding negative regulation proportion are set.
Further, different adjustment ratios are provided with corresponding adjustment periods; the higher the absolute value of the adjustment ratio, the shorter the time of the corresponding adjustment period.
Further, when the proportion of the proportion three-way flow regulating valve is smaller than 1, the first water pump, the second water pump and the plurality of middle-way electromagnetic valves are started, and the upper-way electromagnetic valve and the lower-way electromagnetic valve are closed; when the proportion of the proportion three-way flow regulating valve is 1, the first water pump, the upper-way electromagnetic valve and the lower-way electromagnetic valve are started, and the second water pump and the plurality of middle-way electromagnetic valves are closed.
The liquid cooling air conditioner refrigerating system and the control method thereof provided by the invention have the following beneficial effects:
according to the invention, the second waterway for independently performing water flow circulation heat exchange is added in the liquid cooling air conditioner unit, so that when the temperature of the compressor of the fluorine path part is too high, the second waterway is started, and the water flow direction and the water flow rate of self-circulation flowing in the second waterway are controlled through the proportional flow three-way valve, the second water pump and the switch of the plurality of electromagnetic valves, so that the heat exchange frequency between the self-circulation flowing water flow direction and the refrigerant of the fluorine path part flowing through the first plate heat exchanger is accelerated, the temperature of the refrigerant flowing back to the compressor is reduced, the temperature of the compressor is reduced, the low pressure of the compressor is correspondingly reduced, namely, the compressor is cooled and regulated through the invention, and the compressor is ensured to be in a stable working state for a long time.
It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the invention as claimed.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the invention and together with the description, serve to explain the principles of the invention. In the drawings:
FIG. 1 is a schematic diagram of a liquid cooled air conditioning refrigeration system according to the present invention;
FIG. 2 is a schematic diagram of the flow direction of waterways with different proportions of the proportional three-way flow regulating valve of the present invention;
FIG. 3 is a schematic diagram of the flow direction of the waterway of the liquid-cooled air-conditioning refrigeration system according to the present invention when the ratio of the proportional three-way flow regulating valve is 0;
FIG. 4 is a schematic diagram of the flow direction of the waterway of the liquid-cooled air-conditioning refrigeration system according to the present invention when the ratio of the proportional three-way flow regulating valve is 1;
FIG. 5 is a schematic diagram of the flow direction of the water path of the liquid-cooled air conditioner refrigerating system according to the present invention when the ratio of the proportional three-way flow regulating valve is between 0 and 1;
FIG. 6 is a flow chart of a method for controlling the cooling of a liquid-cooled air conditioner according to an embodiment of the present invention;
FIG. 7 is a flow chart of a method for controlling the cooling of a liquid-cooled air conditioner according to another embodiment of the present invention;
FIG. 8 is a detailed flow chart of the implementation step S2 of the present invention;
fig. 9 is a detailed flowchart of the implementation step S3 of the present invention.
The reference numerals in the drawings are as follows:
1. a first waterway; 11. a first water pump; 12. an expansion tank; 2. a fluorine path portion; 21. a first plate heat exchanger; 22. a compressor; 23. a condenser; 24. an expansion valve; 25. drying the filter; 3. a second waterway; 30. a second water pump; 31. a first electromagnetic valve; 32. a second electromagnetic valve; 33. a third electromagnetic valve; 34. a fourth electromagnetic valve; 35. a fifth electromagnetic valve; 36. a proportional three-way flow regulating valve; 37. a second plate heat exchanger; 38. a backwater temperature sensor; 39. drain valve (water filling port).
Detailed Description
Reference will now be made in detail to exemplary embodiments, examples of which are illustrated in the accompanying drawings. When the following description refers to the accompanying drawings, the same numbers in different drawings refer to the same or similar elements, unless otherwise indicated.
The implementations described in the following exemplary examples do not represent all implementations consistent with the invention.
The invention provides a liquid cooling air conditioner refrigerating system, which is shown in a structural schematic diagram in fig. 1, and comprises a first water channel 1, a second water channel 3 and a fluorine path part 2, wherein the second water channel 3 is respectively connected with the first water channel 1 and the fluorine path part 2.
The first waterway 1 comprises a first water pump 11 and an expansion tank 12; the water flow of the first waterway 1 flows from the water return port to the water outlet.
The fluorine line section 2 comprises a first plate heat exchanger 21, a compressor 22, a condenser 23, a drier-filter 25 and an expansion valve 24; the refrigerant in the fluorine line section 2 flows back to the compressor 22 after heat exchange with an external water line from the compressor 22, through the condenser 23, the dry filter 25, the expansion valve 24, and the first plate heat exchanger.
The second waterway 3 is independent of the first waterway 1 and the fluorine road part 2, the second waterway 3 is a self-circulation waterway realized by self-water injection, the second waterway 3 at least comprises three flow paths, an upper flow path is provided with an upper flow path electromagnetic valve, particularly a third electromagnetic valve 33, a lower flow path is provided with a lower flow path electromagnetic valve, particularly a fourth electromagnetic valve 34, and a middle flow path comprises a second plate heat exchanger 37, a second water pump 30, a proportional three-way flow regulating valve 36 and at least three middle flow path electromagnetic valves, particularly a first electromagnetic valve 31, a second electromagnetic valve 32 and a fifth electromagnetic valve 35; a drain valve 39 is provided between the second plate heat exchanger 37 and the second water pump 30. The water flow of the second waterway 3 is injected from the water injection port of the drain valve 39, and the second waterway 3 is a self-circulation waterway and is mainly used for being opened and performing heat exchange with the refrigerant flowing through the fluorine path part 2 when the temperature of the fluorine path part 2 is too high, wherein the water flow and the flow rate of the water flow are controllable.
A backwater temperature sensor 38 is arranged between the second waterway 3 and the first plate heat exchanger 21.
The first plate heat exchanger 21 and the second plate heat exchanger 37 in the embodiment of the invention are both in single heat exchange, namely, the fluid of the left part and the right part of the plate heat exchangers is not communicated and only carries out heat exchange.
According to the invention, the second waterway 3 for independently performing water flow circulation heat exchange is added in the liquid cooling air conditioner unit, so that when the temperature of the compressor 22 of the fluorine path part 2 is too high, the second waterway 3 is opened, the water flow direction and the water flow rate of self-circulation flowing in the second waterway 3 are controlled through the proportional flow three-way valve 36, the second water pump 30 and the switch of a plurality of electromagnetic valves arranged in the second waterway 3, so that the heat exchange frequency between the water flow and the refrigerant flowing through the fluorine path part 3 of the first plate heat exchanger 21 is accelerated, the temperature of the refrigerant flowing back into the compressor 22 is reduced, the temperature of the compressor 22 is reduced, the low pressure of the compressor 22 is correspondingly reduced, namely, the compressor 22 is subjected to temperature regulation, and the stable working state of the compressor 22 is realized.
The proportional three-way flow regulating valve 36 in the embodiment of the present invention is provided with different waterway directions at different proportions, and as shown in fig. 2, the proportional three-way flow regulating valve is divided into a left way, a right way and an upper way; the proportion range of the proportion three-way flow regulating valve is 0 to 1, when the proportion of the proportion three-way flow regulating valve is 0, the right path and the upper path are completely conducted, namely all water flows in from the right path and all water flows to the upper path; when the proportion of the proportion three-way flow regulating valve is 1, the left path and the right path are completely conducted, namely all water flows from the right path and all water flows to the left path; when the proportion of the proportion three-way flow regulating valve is between 0 and 1, the right way is completely conducted, the left way and the upper way are partially conducted, namely, all water flows from the right way into the left way according to the set proportion, and part of water flows into the upper way.
Fig. 3 to 5 are schematic diagrams of the waterway flow direction of the liquid cooling air conditioner refrigerating system according to the present invention when the proportional three-way flow regulating valve is set in different proportions, and at the same time, the first water pump 11, the second water pump 30, and the first electromagnetic valve to the fifth electromagnetic valve (31-35) are respectively provided with different on-off states.
Fig. 3 shows a schematic water path flow direction of the refrigeration system when the ratio of the proportional three-way flow regulating valve is 0, and the first water pump 11 is turned on, the second water pump 30 is turned on, the first electromagnetic valve 31 is turned on, the second electromagnetic valve 32 is turned on, the third electromagnetic valve 33 is turned off, the fourth electromagnetic valve 34 is turned off, and the fifth electromagnetic valve 35 is turned on.
The water flow of the first waterway 1 flows out from the water outlet after passing through the expansion tank 12, the first water pump 11 and the fifth electromagnetic valve 35 from the water return port;
the refrigerant in the fluorine path part 2 flows back to the compressor 22 after heat exchange between the compressor 22, the condenser 23, the dry filter 25, the expansion valve 24 and the water flow from the second water path 3;
the water injected from the water injection port of the drain valve 39 in the second water path 3 is pumped to the second electromagnetic valve 32 by the second water pump 30, exchanges heat with the refrigerant on the right side of the first plate heat exchanger 21 of the fluorine path portion 2, and then returns to the second water pump 30 by the first electromagnetic valve and the proportional three-way flow regulating valve with the proportion of 0 to start self-circulation flow.
Fig. 4 shows a schematic water path flow direction of the refrigeration system when the ratio three-way flow regulating valve ratio is 1, and the first water pump 11 is turned on, the second water pump 30 is turned off, the first electromagnetic valve 31 is turned off, the second electromagnetic valve 32 is turned off, the third electromagnetic valve 33 is turned on, the fourth electromagnetic valve 34 is turned on, and the fifth electromagnetic valve 35 is turned off.
The water flow of the first waterway 1 passes through the expansion tank 12 and the first water pump 11 from the water return port, then passes through the third electromagnetic valve 33 of the second waterway 3, and directly exchanges heat with the refrigerant flowing through the fluorine path part 2, and then passes through the fourth electromagnetic valve of the second waterway 3 and then flows out from the water outlet;
the refrigerant in the fluorine path section 2 flows back to the compressor 22 after heat exchange between the refrigerant in the fluorine path section 2 and the water flow from the first water path 1 through the condenser 23, the dry filter 25, the expansion valve 24, and the first plate heat exchanger 21;
the second waterway 3 does not work at this time, i.e. the second waterway 3 does not start self-circulation water flow at this time and does not participate in heat exchange work with the refrigerant of the fluorine path part 2.
Fig. 5 shows the waterway flow direction of the refrigeration system when the ratio of the proportional three-way flow regulating valve is between 0 and 1, and the first water pump 11 is turned on, the second water pump 30 is turned on, the first electromagnetic valve 31 is turned on, the second electromagnetic valve 32 is turned on, the third electromagnetic valve 33 is turned off, the fourth electromagnetic valve 34 is turned off, and the fifth electromagnetic valve 35 is turned on.
The water flow of the first waterway 1 flows out from the water outlet after passing through the expansion tank 12, the first water pump 11 and the fifth electromagnetic valve 35 from the water return port;
the refrigerant in the fluorine path section 2 flows back to the compressor 22 after heat exchange between the refrigerant in the fluorine path section 2 and the water flow from the second water path 3 through the condenser 23, the dry filter 25, the expansion valve 24, and the first plate heat exchanger 21;
the water flow injected through the water injection port of the drain valve 39 in the second waterway 3 is pumped to the second electromagnetic valve 32 by the second water pump 30, exchanges heat with the refrigerant on the right side of the first plate heat exchanger 21 of the fluorine path part 2, then passes through the first electromagnetic valve, and is conducted by the left path and the upper path of the proportional three-way flow regulating valve, the water flow in the second waterway 3 is circulated back to the second water pump 30 to exchange heat with the fluorine path part 2 according to the proportional size, and the left path water flow is circulated to the upper path water flow after flowing through the second plate heat exchanger 37, and is circulated to the upper path water flow after being circulated, and self-circulated from the second water pump 30.
At this time, the temperature of the left water flow split from the left path of the proportional three-way flow regulating valve will rise after heat exchange with the water path of the first water path 1, and the efficiency of heat exchange with the fluorine path part 2 will be reduced after merging with the upper water flow loop.
Therefore, as can be seen from the three water channel flow direction conditions in fig. 3-5, when the temperature of the fluorine path portion 2 is too high, the second water channel 3 and the fluorine path portion 2 are completely opened to exchange heat according to the condition in fig. 3; when the temperature of the fluorine path part is not high, the whole second waterway 3 is disconnected according to the situation shown in fig. 4, and only the heat exchange is carried out through the original first waterway 1; when the temperature of the fluorine path part is high and needs to be adjusted, the second water path 3 is started according to the situation shown in fig. 5, wherein the proportion of the upper water flow which does not exchange heat and the left water flow which exchanges heat with the water flow of the first water path 1 are controlled by adjusting the proportion of the proportion three-way flow adjusting valve 36, so that the temperature after the two water paths are converged is controlled to control the heat exchange efficiency with the fluorine path part 2.
According to the invention, the proportional three-way flow regulating valve 36 is arranged at different positions through the second waterway 3, and partial water flow is controlled to directly enter the first plate heat exchanger 21 without heat exchange of the second plate heat exchanger 37, so that the temperature of water entering the first plate heat exchanger 21 becomes low, and the low pressure of the compressor 22 becomes low after the temperature of water entering the first plate heat exchanger 21 becomes low.
The invention also provides a liquid cooling air conditioner refrigeration control method, which is applied to the liquid cooling air conditioner refrigeration system, and according to the figure 6, the control method comprises the following steps:
step S1, starting a first water pump 11, an upper-path electromagnetic valve and a lower-path electromagnetic valve, wherein a second water pump 30 and a plurality of middle-path electromagnetic valves are in a closed state;
step S2, acquiring backwater temperature after the first setting time, respectively adjusting the starting or closing of the first water pump 11, the second water pump 30, the upper-way electromagnetic valve, the plurality of middle-way electromagnetic valves and the lower-way electromagnetic valve, and setting the proportion of the proportion three-way flow regulating valve 36.
As can be seen from fig. 3, 4-5, the above-mentioned upper-path electromagnetic valve is specifically a third electromagnetic valve 33, the above-mentioned lower-path electromagnetic valve is a fourth electromagnetic valve 34, and the above-mentioned plurality of middle-path electromagnetic valves are a first electromagnetic valve 31, a second electromagnetic valve 32, and a fifth electromagnetic valve 35, respectively.
Specifically, the detailed flow of step S2 described above includes, as shown in fig. 8:
s22, judging whether the backwater temperature is greater than or equal to the first temperature, if so, executing the step S24, namely setting the proportion of the proportional three-way flow regulating valve to be 0;
s23, judging whether the backwater temperature is lower than a second temperature, if so, executing the step S26, namely setting the proportion of the proportion three-way flow regulating valve to be 1;
if no in the above steps S23 and S24, step S25 is performed, i.e. the three-way flow control valve is adjusted according to the proportions corresponding to the temperature intervals set between the second temperature and the first temperature.
TABLE 1 Critical component settings at different backwater temperatures
The terms in Table 1 above are defined as:
thc represents the return water temperature; three-way Valve represents the setting proportion of the proportional Three-way flow regulating Valve; pump1 represents the first water Pump 11; pump2 represents the second water Pump 30; SV1 to SV5 represent the first solenoid valve to the fifth solenoid valve (31-35) in this order.
The above table shows a specific embodiment of adjusting the starting or closing of the first water pump 11, the second water pump 30, the upper solenoid valve, the plurality of middle solenoid valves, the lower solenoid valve, and the proportion of the proportional three-way flow control valve 36 in step S2 when the return water temperatures are different, wherein the upper solenoid valve is the third solenoid valve 33, the lower solenoid valve is the fourth solenoid valve 34, and the plurality of middle solenoid valves are the first solenoid valve 31, the second solenoid valve 32, and the fifth solenoid valve 35.
The backwater temperature in the embodiment of the present invention is the water flow temperature flowing through the backwater temperature sensor 38, and the water flow can come from the first waterway 1 or the second waterway 3 under different conditions, and can be the water flow temperature of the first waterway 1 or the water flow temperature of the second waterway 3.
In the embodiment, the minimum value of the backwater temperature is set to be 20 ℃ and the maximum value is set to be 40 ℃; when the temperature of the backwater is lower than the lowest value, setting the proportion of the proportion three-way flow regulating valve to be 1; when the backwater value is higher than or equal to the highest value, setting the proportion of the proportion three-way flow regulating valve to be 0;
dividing the backwater temperature between the lowest 20 ℃ and the highest 40 ℃ into four temperature intervals according to each 5 ℃, wherein each temperature interval corresponds to the setting proportion of the three-way flow regulating valve with different proportions, and the setting conditions in the embodiment are as follows:
setting the proportion of the proportional three-way flow regulating valve to be 0.9 when the temperature is more than or equal to 20 ℃ and less than 25 ℃;
setting the proportion of the proportional three-way flow regulating valve to be 0.7 when the temperature is more than or equal to 25 ℃ and less than 30 ℃;
setting the proportion of the proportional three-way flow regulating valve to be 0.4 when the temperature is more than or equal to 30 ℃ and less than 35 ℃;
the ratio of the proportional three-way flow regulating valve is set to be 0.2 when the temperature is more than or equal to 35 ℃ and less than 40 ℃.
Meanwhile, according to the table, the ratio three-way flow regulating valve has different ratios, and the first water pump 11, the second water pump 20, and the first to fifth electromagnetic valves (31-35) are provided with different switch states.
When the ratio of the proportional three-way flow regulating valve is smaller than 1 (comprising 0), the first water pump 11 is started, the second water pump 30 is started, the first electromagnetic valve 31 is started, the second electromagnetic valve 32 is started, the third electromagnetic valve 33 is closed, the fourth electromagnetic valve 34 is closed, and the fifth electromagnetic valve 35 is started;
when the ratio of the proportional three-way flow regulating valve is 1, the first water pump 11 is turned on, the second water pump 30 is turned off, the first electromagnetic valve 31 is turned off, the second electromagnetic valve 32 is turned off, the third electromagnetic valve 33 is turned on, the fourth electromagnetic valve 34 is turned on, and the fifth electromagnetic valve 35 is turned off.
The control method of the invention further comprises the step S3 of obtaining the current low pressure value of the refrigerating system through the second setting time and setting the adjusting proportion of the proportion three-way flow regulating valve according to the low pressure difference value between the current low pressure value and the set target low pressure value.
Specifically, the detailed flow of step S3 described above includes, as shown in fig. 9:
s31, judging whether the low pressure difference value is 0; if yes, executing step S33, namely setting the adjustment ratio to be 0;
s32, if not, judging whether the low pressure difference value is larger than 0; if yes, go to step 34, i.e. set the adjustment ratio to be negative; if not, step S35 is performed, i.e. the adjustment ratio is set to a positive value.
Table 2 proportional adjustment of amplitude and period of different low pressure differences
In table 2 above, Δt is the low pressure difference between the current low pressure of the compressor and the target low pressure.
Setting different low pressure difference value intervals according to specific values, wherein each low pressure difference value interval corresponds to the adjustment proportion of the three-way flow regulating valve with different proportions, and meanwhile, when the absolute value deviation of the low pressure difference value is larger, the corresponding adjustment period is shorter, and the following setting conditions are distinguished in the embodiment:
setting the adjusting proportion to be +20% and the adjusting period to be 30 seconds when DeltaT is < -5 >;
-3 is less than or equal to delta T < -5, setting the adjusting proportion to +10% and the adjusting period to 45 seconds;
-1 is less than or equal to delta T < -3, setting the adjusting proportion to be +5% and the adjusting period to be 1 minute;
setting the adjustment ratio to +3% and the adjustment period to 2 min if delta T is less than or equal to-1 and less than 0;
Δt=0, then the adjustment ratio is set to 0, i.e. not adjusted;
setting the adjusting proportion to be-3% and the adjusting period to be 2 minutes when delta T is more than or equal to 0 and less than 1;
setting the adjusting proportion to be-5% and the adjusting period to be 1 min if delta T is less than or equal to 1 and less than 3;
setting the adjusting ratio to-10% and the adjusting period to 45 seconds if delta T is more than or equal to 3 and less than 5
And if delta T is more than 5, setting the adjusting proportion to be-20% and setting the adjusting period to be 30 seconds.
In the embodiment of the present invention, the low pressure is a low pressure value of the compressor 22, and the low pressure value is in positive correlation with the temperature of the compressor 22, that is, the higher the temperature of the compressor 22 is, the larger the low pressure value is, whereas the lower the low pressure value is, that is, the lower the temperature of the compressor 22 is, the lower the low pressure of the compressor 22 is.
Other embodiments of the invention will be apparent to those skilled in the art from consideration of the specification and practice of the invention disclosed herein. This invention is intended to cover any variations, uses, or adaptations of the invention following, in general, the principles of the invention and including such departures from the present disclosure as come within known or customary practice within the art to which the invention pertains.
It is to be understood that the invention is not limited to the precise arrangements and instrumentalities shown in the drawings, which have been described above, and that various modifications and changes may be effected without departing from the scope thereof.
Claims (8)
1. The liquid cooling air conditioner refrigerating system is characterized in that:
the device comprises a first waterway, a second waterway and a fluorine path part, wherein the second waterway is respectively connected with the first waterway and the fluorine path part;
the first waterway comprises a first water pump; the first waterway comprises a water return port and a water outlet, and water flows from the water return port to the water outlet; a second plate heat exchanger is arranged between the first waterway and the second waterway; the fluorine path part comprises a first plate heat exchanger; the refrigerant of the fluorine path part exchanges heat with the water flow of the first waterway or the second waterway through the first plate heat exchanger;
the second waterway is independent of the first waterway and is a self-circulation waterway;
the second waterway comprises at least three flow paths,
the upper path is provided with an upper path electromagnetic valve, the lower path is provided with a lower path electromagnetic valve,
the middle path flow path comprises a second plate heat exchanger, a second water pump, a proportional three-way flow regulating valve and at least three middle path electromagnetic valves; the proportional three-way flow regulating valve is divided into a left way, a right way and an upper way; the left path is connected with the first end of the second plate heat exchanger, and the right path is connected with a first electromagnetic valve;
the upper path is connected to a flow path between the second water pump and the second end of the second plate heat exchanger; the second water pump is connected with a second electromagnetic valve;
one end of the upper flow path is connected to the flow path between the first water pump and the water return port of the second plate heat exchanger, and the other end of the upper flow path is connected to the flow path between the second electromagnetic valve and the first plate heat exchanger;
one end of the lower path flow path is connected to the flow path between the second plate heat exchanger and the water outlet of the first waterway, and the other end of the lower path flow path is connected to the flow path between the first electromagnetic valve and the first plate heat exchanger;
setting the adjusting proportion of the proportion three-way flow regulating valve according to a low pressure difference value between the current low pressure value of the system and a set target low pressure value;
different adjusting ratios are provided with corresponding adjusting periods; the higher the absolute value of the adjustment ratio, the shorter the corresponding time of the adjustment period.
2. A refrigeration system as set forth in claim 1 wherein:
the proportion range of the proportion three-way flow regulating valve is 0 to 1;
when the proportion of the proportional three-way flow regulating valve is 0, the right path and the upper path are completely conducted;
when the proportion of the proportional three-way flow regulating valve is 1, the left path and the right path are completely conducted;
when the proportion of the proportion three-way flow regulating valve is between 0 and 1, the right way is completely conducted, and the left way and the upper way are partially conducted.
3. A refrigeration system as set forth in claim 2 wherein:
the second waterway further comprises a backwater temperature sensor;
the fluorine path section also includes a compressor, a condenser, and an electronic expansion valve.
4. The liquid cooling air conditioner refrigeration control method is characterized in that: the control method is applied to the liquid-cooled air conditioner refrigerating system according to any one of claims 1 to 3;
the control method comprises the following steps:
starting the first water pump, the upper path electromagnetic valve and the lower path electromagnetic valve, wherein the second water pump and the plurality of middle path electromagnetic valves are in a closed state;
acquiring backwater temperature through a first setting time, respectively adjusting the starting or closing of the first water pump, the second water pump, the upper-way electromagnetic valve, the plurality of middle-way electromagnetic valves and the lower-way electromagnetic valve, and setting the proportion of the proportion three-way flow regulating valve;
acquiring a current low pressure value of the liquid cooling air conditioner refrigerating system through a second setting time, and setting the adjusting proportion of the proportion three-way flow regulating valve according to a low pressure difference value between the current low pressure value and a set target low pressure value;
different adjusting ratios are provided with corresponding adjusting periods; the higher the absolute value of the adjustment ratio, the shorter the corresponding time of the adjustment period.
5. The control method according to claim 4, characterized in that:
if the low pressure difference value is larger than 0, the adjusting proportion is a negative value;
if the low pressure difference value is smaller than 0, the adjusting proportion is a positive value;
and if the low pressure difference value between the current low pressure and the set target low pressure is 0, the adjusting ratio is 0.
6. The control method according to claim 4, wherein,
when the backwater temperature is greater than or equal to the first temperature, setting the proportion of the proportion three-way flow regulating valve to be 0;
when the backwater temperature is lower than the second temperature, setting the proportion of the proportion three-way flow regulating valve to be 1;
the first temperature is greater than the second temperature;
when the backwater temperature is between the second temperature and the first temperature, including the second temperature, a plurality of temperature intervals are arranged between the second temperature and the first temperature, and the plurality of temperature intervals are used for setting the proportion of the corresponding proportional three-way flow regulating valve.
7. The control method according to claim 5, wherein,
if the low pressure difference value is smaller than the first difference value, setting the highest positive regulation proportion;
if the low pressure difference value is larger than the second difference value, setting a negative regulation proportion with the highest absolute value;
the first difference is smaller than 0, and the second difference is larger than 0;
if the low differential pressure value is between the first differential value and 0, setting a plurality of negative differential value intervals and the corresponding positive adjustment proportion;
and if the low pressure difference value is between 0 and the second difference value, setting a plurality of positive number difference value intervals and the corresponding negative regulation proportion.
8. The control method according to claim 7, characterized in that:
when the proportion of the proportion three-way flow regulating valve is smaller than 1, the first water pump, the second water pump and the plurality of middle-way electromagnetic valves are started, and the upper-way electromagnetic valve and the lower-way electromagnetic valve are closed;
when the proportion of the proportion three-way flow regulating valve is 1, the first water pump, the upper-way electromagnetic valve and the lower-way electromagnetic valve are started, and the second water pump and the plurality of middle-way electromagnetic valves are closed.
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Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202797185U (en) * | 2012-08-23 | 2013-03-13 | 浙江吉利汽车研究院有限公司杭州分公司 | Thermal management system for battery |
| CN103129349A (en) * | 2011-11-23 | 2013-06-05 | 杭州三花研究院有限公司 | Electric vehicle air conditioner system |
| CN107014013A (en) * | 2017-04-20 | 2017-08-04 | 广东申菱环境***股份有限公司 | A kind of secondary cycle formula evaporative condenser natural cooling cooling-water machine and its control method |
| CN107014016A (en) * | 2017-04-20 | 2017-08-04 | 广东申菱环境***股份有限公司 | A kind of fluorine pump natural cooling evaporating type condensing cooling-water machine and its control method |
| CN107192055A (en) * | 2017-04-20 | 2017-09-22 | 广东申菱环境***股份有限公司 | The cooling-water machine and its control method of a kind of separate modular |
| CN207677039U (en) * | 2018-01-24 | 2018-07-31 | 福建省汽车工业集团云度新能源汽车股份有限公司 | A kind of water-cooled battery temperature regulating device |
| CN110103665A (en) * | 2019-05-07 | 2019-08-09 | 上海理工大学 | The new-energy automobile heat pump air conditioning system of charged pool and electric control heat management |
| CN111952826A (en) * | 2020-09-03 | 2020-11-17 | 中国久远高新技术装备有限公司 | High-energy laser thermal management system based on cold accumulation mode and control method thereof |
| CN212677604U (en) * | 2020-08-20 | 2021-03-09 | 北京硅基远航科技有限公司 | Liquid cooling heat exchange unit and liquid cooling heat exchange system of server |
-
2023
- 2023-08-31 CN CN202311109265.0A patent/CN116817477B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103129349A (en) * | 2011-11-23 | 2013-06-05 | 杭州三花研究院有限公司 | Electric vehicle air conditioner system |
| CN202797185U (en) * | 2012-08-23 | 2013-03-13 | 浙江吉利汽车研究院有限公司杭州分公司 | Thermal management system for battery |
| CN107014013A (en) * | 2017-04-20 | 2017-08-04 | 广东申菱环境***股份有限公司 | A kind of secondary cycle formula evaporative condenser natural cooling cooling-water machine and its control method |
| CN107014016A (en) * | 2017-04-20 | 2017-08-04 | 广东申菱环境***股份有限公司 | A kind of fluorine pump natural cooling evaporating type condensing cooling-water machine and its control method |
| CN107192055A (en) * | 2017-04-20 | 2017-09-22 | 广东申菱环境***股份有限公司 | The cooling-water machine and its control method of a kind of separate modular |
| CN207677039U (en) * | 2018-01-24 | 2018-07-31 | 福建省汽车工业集团云度新能源汽车股份有限公司 | A kind of water-cooled battery temperature regulating device |
| CN110103665A (en) * | 2019-05-07 | 2019-08-09 | 上海理工大学 | The new-energy automobile heat pump air conditioning system of charged pool and electric control heat management |
| CN212677604U (en) * | 2020-08-20 | 2021-03-09 | 北京硅基远航科技有限公司 | Liquid cooling heat exchange unit and liquid cooling heat exchange system of server |
| CN111952826A (en) * | 2020-09-03 | 2020-11-17 | 中国久远高新技术装备有限公司 | High-energy laser thermal management system based on cold accumulation mode and control method thereof |
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