CN111156841B - Plate heat exchanger intelligently controlled according to outlet temperature - Google Patents
Plate heat exchanger intelligently controlled according to outlet temperature Download PDFInfo
- Publication number
- CN111156841B CN111156841B CN201911278812.1A CN201911278812A CN111156841B CN 111156841 B CN111156841 B CN 111156841B CN 201911278812 A CN201911278812 A CN 201911278812A CN 111156841 B CN111156841 B CN 111156841B
- Authority
- CN
- China
- Prior art keywords
- fluid
- temperature
- baffle
- plate
- flow
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
- F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/24—Arrangements for promoting turbulent flow of heat-exchange media, e.g. by plates
Abstract
The invention provides a plate heat exchanger intelligently controlled according to outlet temperature, wherein a second temperature sensor and a third temperature sensor are respectively arranged at a fluid outlet and are respectively used for detecting the fluid temperature of the two outlets, and the second temperature sensor and the third temperature sensor are respectively in data connection with a controller; the controller automatically controls the flow of the fluid at the inlet according to the detected fluid temperatures at the two outlets; when the detected temperature is higher than the set first temperature, the controller controls the opening of the first valve to increase, so that the flow of the fluid entering the heat exchanger is increased; when the detected temperature is lower than the set second temperature, the controller controls the opening of the first valve to be reduced, so that the flow of the fluid entering the heat exchanger is reduced. The invention avoids the problems that the heat exchange fluid is too much or too little to cause that the heat exchange and the heat dissipation can not be carried out in time, and the operation of the heat source is influenced because the temperature of the heat source is too high or too low.
Description
Technical Field
The invention relates to a further improvement of the prior application, relates to the technical field of heat exchangers, and particularly relates to an intelligent control plate heat exchanger with a flow guide structure combined with a column rib.
Background
The flat plate type heat exchanger is a heat exchanger with the highest heat exchange efficiency in various heat exchangers at present, and has the advantages of small occupied space and convenience in mounting and dismounting. The high-pressure resistant staggered circulation structure of the plate heat exchanger is formed by combining concave-convex lines between two adjacent plates in a vacuum welding mode, and the staggered circulation structure enables cold and hot fluid in the plate heat exchanger to generate strong turbulence to achieve a high heat exchange effect.
Flat tubes have found widespread use in automotive air conditioning units and residential or commercial air conditioning heat exchangers in recent years. The flat tubes are provided with a plurality of small passages therein through which, in use, a heat exchange fluid flows. Because the flat tube heat exchange area is big, consequently can improve heat transfer effect greatly.
The flat plate heat exchanger is widely applied to industries such as chemical industry, petroleum industry, refrigeration industry, nuclear energy industry and power industry, and due to the worldwide energy crisis, the demand of the heat exchanger in industrial production is more and more, and the quality requirement of the heat exchanger is higher and more. In recent decades, although compact heat exchangers (plate type, plate fin type, pressure welded plate type, etc.), heat pipe type heat exchangers, direct contact type heat exchangers, etc. have been rapidly developed, because the shell and tube type heat exchangers have high reliability and wide adaptability, they still occupy the domination of yield and usage, and according to relevant statistics, the usage of the shell and tube type heat exchangers in the current industrial devices still accounts for about 70% of the usage of all heat exchangers.
After the flat plate type heat exchanger is scaled, the heat exchanger is cleaned by adopting conventional modes of steam cleaning, back flushing and the like, and the production practice proves that the effect is not good. The end socket of the heat exchanger can only be disassembled, and a physical cleaning mode is adopted, but the mode is adopted for cleaning, so that the operation is complex, the consumed time is long, the investment of manpower and material resources is large, and great difficulty is brought to continuous industrial production.
Immersion heat exchangers are one type of dividing wall heat exchangers. The high-pressure fluid cooling and condensing device has the advantages of simple structure, convenience in manufacturing, mounting, cleaning and maintaining, low price and capability of being particularly suitable for cooling and condensing high-pressure fluid, so that the high-pressure fluid cooling and condensing device is still widely applied in modern times. Such heat exchangers are often wound from metal tubing or made to conform to the container and immersed in the liquid in the container.
Research and engineering applications show that the immersed liquid cooling and the heat pipe respectively have excellent heat exchange performance. In addition, the phase-change material has stable temperature in the heat absorption and heat release process, so that the whole system can achieve the temperature equalization effect, and the phase-change material is widely applied to the field of heat exchange.
In the indirect liquid cooling scheme, a water-cooled plate heat exchanger is used for heat exchange. The water cooled plate is a metal heat transfer device with a flow channel structure therein, and is usually made of copper or aluminum. The heat exchange fluid is directly contacted with the bottom surface of the base plate of the water cooling plate, the heat transferred is conducted to the water cooling plate, and then the water cooling plate and the internal refrigerant carry out convective heat exchange to take away the heat. The whole liquid cooling system utilizes the pump to provide power for the circulation of the working medium, and compared with an air cooling system, the liquid cooling system is more compact in structure. And the used refrigerants are mainly deionized water compatible with cold plate materials, ethylene glycol-deionized water with specified percentage, nanofluid and other media, have higher specific heat capacity and heat conductivity coefficient than air, and are superior to air cooling in heat dissipation effect. In addition, compared with an air cooling system, the noise level of the indirect liquid cooling system is obviously reduced.
In recent years, in order to meet the heat exchange requirement, research on an indirect liquid cooling system has been carried out, and the research relates to various aspects such as a cold plate structure, refrigerant selection, pipeline arrangement and the like. The water cooling plate can be divided into three parts of a base plate, a flow passage and a cover plate. The cover plate and the hose joint have no unified standard, different manufacturers have different structural forms, and the base plate and the flow channel can be configured in various ways according to equipment and thermal design power consumption, which is also a main factor influencing the heat dissipation performance of the water cooling plate.
Column ribs: the addition of fins helps to increase the heat exchange area and can enhance the disturbance of the flow field. Enhanced heat exchange by the addition of fins has been widely used in heat exchangers. However, the design cannot consider the heat dissipation effect singly, and from the viewpoint of system economy, the situation that the heat dissipation improvement effect is extremely small due to the fact that the pressure drop is increased sharply after the fins are added is avoided as much as possible. And considering the relatively lower temperature of the refrigerant inlet, no rib is arranged in the central high-flow-velocity area to improve the pressure drop of the cold plate, and cylindrical ribs are arranged in the peripheral low-flow-velocity area to strengthen disturbance and increase the heat exchange area, so that the loss of the heat dissipation capacity caused by the temperature rise of the refrigerant is compensated.
The flow guide structure comprises: in order to avoid the flowing dead zone in the convective heat exchange process of the refrigerant and the cold plate, a baffle plate which is widely adopted in a heat exchanger is used for reference, a plurality of long and straight baffles are distributed in the cold plate to be used as a flow guide structure, and the flow direction of the refrigerant is changed in some areas of a flow field so as to improve the flow field distribution of the refrigerant in the cold plate.
In conclusion, the water cooling plate combined with the flow guide structure and the column rib is introduced into the heat exchanger from the middle inlet and the two-side outlet of the cover plate, so that efficient heat exchange is purposefully carried out, certain temperature uniformity is ensured, and the normal working requirement of the heat exchanger is met. Therefore, in the prior invention, the inventor improves the situation and invents a plate heat exchanger with a flow guide structure combined with a column rib. But in practical application, the intelligent degree of the heat exchanger is not high, intelligent control cannot be realized, and uniform heat exchange cannot be realized, so that a plate heat exchanger which is intelligently controlled needs to be designed.
Disclosure of Invention
The invention aims to provide a plate heat exchanger, which can change the refrigerant inlet and outlet mode of a common water cooling plate, is additionally provided with a baffle plate to improve the flow uniformity of the refrigerant in the cooling plate, is provided with column ribs to improve the heat dissipation characteristic of the water cooling plate, can realize intelligent control and realizes uniform heat exchange of the plate heat exchanger.
In order to achieve the purpose, the technical scheme of the invention is as follows:
a plate heat exchanger intelligently controlled according to outlet temperature comprises a base plate, a cover plate, a fluid inlet and a fluid outlet, wherein the cover plate and the base plate are assembled together to form a fluid space; the device is characterized in that the fluid outlets are respectively provided with a second temperature sensor and a third temperature sensor which are respectively used for detecting the fluid temperatures of the two outlets, and the second temperature sensor and the third temperature sensor are respectively in data connection with the controller; the controller automatically controls the flow of the fluid at the inlet according to the detected fluid temperatures at the two outlets; when the detected temperature is higher than the set first temperature, the controller controls the opening of the first valve to increase, so that the flow of the fluid entering the heat exchanger is increased; when the detected temperature is lower than the set second temperature, the controller controls the opening of the first valve to be reduced, so that the flow of the fluid entering the heat exchanger is reduced.
Preferably, a first valve is arranged on a pipeline of the inlet, the first valve is in data connection with the controller, and the flow of the inlet is controlled by controlling the opening degree of the first valve.
Preferably, the fluid temperature of the two outlets is calculated from the average temperature of the two outlets.
Preferably, the baffle plates include a first baffle plate positioned at the center of the substrate, a second baffle plate surrounding the outside of the first baffle plate, and a third baffle plate surrounding the outside of the second baffle plate;
the first baffle plates comprise four blocks, intervals are arranged between every two adjacent first baffle plates, the adjacent first baffle plates are in a vertical relation, and extension lines of the four first baffle plates form a first square;
the second baffle plates comprise four blocks, intervals are arranged between every two adjacent second baffle plates, the adjacent second baffle plates are in a vertical relation, the extension lines of the four second baffle plates form a second square, and the extension line of each first baffle plate passes through the middle point of the two second baffle plates;
the third baffle plates comprise four, intervals are arranged between every two adjacent third baffle plates, the adjacent third baffle plates are in a vertical relation, extension lines of the four third baffle plates form a third square, and the extension line of each second baffle plate passes through the middle point of the two third baffle plates;
a plurality of cylindrical fins are arranged between the second baffle plate and the third baffle plate;
the base plate further comprises fourth baffles arranged outside the third baffles, the fourth baffles are arranged in parallel, and the extension lines of the two third baffles pass through the middle point of one fourth baffle.
Preferably, the fluid inlet and the fluid outlet are located on the same line.
The heat exchanger comprises a fluid inlet and a fluid outlet which are arranged on the cover plate, the cold fluid inlet is arranged at the center of the first square, and the two fluid outlets are respectively arranged at the outer positions of parallel lines formed by the two fourth baffles.
Preferably, the fluid inlet and the fluid outlet are located on the same line, and the fluid inlet is located at a position intermediate the two fluid outlets.
Preferably, the base plate and the cover plate are of rectangular configuration.
Preferably, the substrate is provided with a groove, the cover plate is provided with a convex column, and the substrate and the cover plate are connected through the matching of the groove and the convex column.
Preferably, the groove is arranged at a diagonal position of the substrate and is positioned at an outer position of a parallel line formed by the two fourth baffles.
Preferably, the recess is a hole.
Preferably, the lower part of the side wall of the cover plate is provided with an outward extending part perpendicular to the side wall, and the extending part is provided with a screw hole to be matched with a screw hole at a corresponding position on the base plate.
The invention has the following advantages:
1) according to the invention, through the automatic detection and control of the opening degree of the first valve, the heat exchange condition of the heat exchanger can be automatically detected through the temperature of the output fluid, the heat absorption condition of the heat exchanger can be detected, if the output temperature is too high, the heat exchange condition is not good, the flow needs to be increased for heat exchange, and if the output temperature is too low, the fluid flow is too high, so that the loss is easily caused, the fluid flow can be reduced, and meanwhile, the temperature of a heat source is prevented from being too low. The measures avoid too much or too little heat exchange fluid to cause the incapability of carrying out heat exchange and heat dissipation in time, and avoid the phenomenon that the temperature of the heat source is too high or too low to influence the operation of the heat source.
2) In the scheme, the refrigerant flows in from the central area of the cover plate, and when the refrigerant just enters the cold plate, the temperature is low, the temperature difference with the heat exchange area is large, the cooling capacity is strong, and the temperature of the heat exchange area can be controlled more effectively.
3) In this scheme, the inside water conservancy diversion structure that is equipped with of cold drawing effectively reduces the refrigerant and flows the blind spot, further improves the temperature uniformity of hot flow face.
4) Adopt the cylinder type fin in this scheme, strengthened the disturbance to the flow field to expanded heat transfer area, do benefit to and strengthen the heat transfer.
5) The scheme adopts a single-inlet and double-outlet flow mode, improves the phenomenon that the temperature is gradually increased along the flow direction caused by the traditional single-inlet and single-outlet flow mode, and further improves the temperature uniformity of heat dissipation.
6) According to the invention, the structure of the heat exchanger is simulated through a large amount of researches, formulas such as the Nussel number and the like of the structure are determined for the first time, and the heat radiation performance and the pumping power consumption of the water cooling plate can be estimated through the formulas.
Description of the drawings:
the accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the application and, together with the description, serve to explain the application and are not intended to limit the application.
FIG. 1 is an exploded view of the configuration of the center diffusion cold plate;
FIG. 2 is a schematic diagram of a cold plate substrate configuration;
FIG. 3 is a schematic view of a cold plate cover plate;
FIG. 4 is a schematic illustration of cold plate cover plate dimensions;
FIG. 5 is a schematic diagram of a bypass pulsation configuration;
FIG. 6 is another schematic diagram of a bypass pulsing arrangement;
FIG. 7 is a schematic view of a valve control structure;
FIG. 8 is a schematic diagram of a flow control configuration based on outlet temperature.
In the figure: 1. a water-cooled plate inlet; 2. a water-cooled plate outlet (201, 202); 3. positioning structures (301 and 303, 302 and 304 cooperate with each other when the base plate and the cover plate are assembled); 4. the flow guide structures (the first baffle 401, the second baffle 402, the third baffle 403 and the fourth baffle 404) are all baffles; 5. cylindrical fins (501, 502); 6. cover blank areas 601 and 602 (threaded holes are processed here, and are matched and fastened with threaded holes at corresponding positions of the base plate through screws to prevent refrigerant leakage), 71 a first valve, 72 a second valve, 73 a third valve, 74 a bypass valve, 75 a main circuit valve, 8 a pulsation generating device, 10 a base plate, 11 a main circuit, 12 a bypass circuit and 20 a cover plate.
Detailed Description
The present disclosure is further described with reference to the following detailed description of illustrative embodiments and accompanying drawings.
1-3 a water-cooled plate heat exchanger comprising a base plate 10 and a cover plate 20, the cover plate 20 and the base plate 10 being assembled together to form a cavity in which a cooling fluid, preferably water, flows, said base plate 10 being provided with baffles 401 and 404 and cylindrical fins 501, 502, said baffles comprising a first baffle 401 centrally located in the base plate, a second baffle 402 surrounding the exterior of the first baffle 401 and a third baffle 403 surrounding the exterior of the second baffle 402;
preferably, as shown in fig. 1-2, the first baffle 401 includes four blocks, a space is provided between adjacent first baffles 401, the adjacent first baffles 401 are in a perpendicular relationship, and extension lines of the four first baffles 401 form a first square;
the second baffle plates 402 comprise four blocks, an interval is arranged between every two adjacent second baffle plates 402, the adjacent second baffle plates 402 are in a vertical relation, the extension lines of the four second baffle plates 402 form a second square, and the extension line of each first baffle plate 401 passes through the middle point of the two second baffle plates 402;
the third baffles 403 comprise four, a gap is formed between every two adjacent third baffles 403, every two adjacent third baffles 403 are in a vertical relation, the extension lines of the four third baffles 403 form a third square, and the extension line of each second baffle 402 passes through the midpoint of the two third baffles 403;
a plurality of cylindrical ribs 501 are arranged between the second baffle 402 and the third baffle 403;
the substrate further comprises fourth baffles 404 arranged outside the third baffles 403, the number of the fourth baffles 404 is two, the four baffles 404 are arranged in parallel, and the extension lines of the two third baffles 403 pass through the middle point of one fourth baffle 404;
the heat exchanger comprises a fluid inlet 1 and a fluid outlet 2 which are arranged on the cover plate 20, wherein the fluid inlet 1 is arranged at the center of a first square, and the two fluid outlets 2 are respectively 201 and 202 and are respectively arranged at the outer positions of parallel lines formed by the two fourth baffles 404.
Through the structure, the refrigerant flows in from the central area of the cover plate, and when the refrigerant just enters the cold plate, the temperature is still low, the temperature difference with a heat source is large, the cooling capacity is strong, and the temperature of a hot spot area of the heat source can be more effectively controlled.
The inside water conservancy diversion structure that is equipped with of cold drawing of this application of heat exchanger especially through setting up the multilayer square baffle for fluid flow range is extensive, effectively reduces the refrigerant dead zone that flows, further improves the temperature uniformity of hot flow face.
In the heat exchanger of this application, through at second and third baffle, set up the cylinder type fin between third and fourth baffle, do not set up the cylinder type fin between first baffle inside and first and second baffle, make the flow resistance in the region that the inner space is little (between first baffle inside and first and second baffle) little, the disturbance is strengthened in the outer space increase region, the disturbance to the flow field has been strengthened promptly, and heat transfer area has been expanded, do benefit to and strengthen the heat transfer, it is too big also to avoid the flow resistance, accommodation is extensive.
The single-inlet and double-outlet flow mode is adopted, so that cold fluid flows from the middle to two sides, the phenomenon that the temperature gradually rises along the flow direction due to the single-inlet and single-outlet flow mode in the prior art is improved, and the heat-dissipation temperature uniformity is further improved.
The baffle 401 and 404 are used as a flow guiding structure and can be regarded as long straight fins with larger size. By arranging the baffles, the effects of turbulent flow and enhanced heat transfer can be achieved.
Preferably, the water cooling plate inlet 1 and the water cooling plate outlets 201 and 202 are respectively provided with a first temperature sensor, a second temperature sensor and a third temperature sensor, which are respectively used for detecting the fluid temperatures of the inlet 1 and the two outlets 201 and 202, and the first temperature sensor, the second temperature sensor and the third temperature sensor are respectively in data connection with the controller.
Preferably, the pipelines of the water cooling plate inlet 1 and the water cooling plate outlets 201 and 202 are respectively provided with a first valve 71, a second valve 72 and a third valve 73, the first valve 71, the second valve 72 and the third valve 73 are respectively in data connection with a controller, and the controller controls the opening and closing of the first valve 71, the second valve 72 and the third valve 73 and the size of the opening, so as to control the flow of the fluid of the inlet 1 and the two outlets 201 and 202.
As a preference, the controller automatically controls the flow rate of the fluid at the inlet 1 according to the sensed fluid temperatures at the two outlets 201, 202. Preferably, the flow rate of the inlet 1 is controlled by controlling the opening degree of the first valve 71. The fluid temperature of the two outlets 201, 202 is calculated from the average temperature of the two outlets 201, 202.
Preferably, when the detected temperature is higher than the set first temperature, the controller controls the opening of the first valve 71 to increase, thereby increasing the flow rate of the fluid entering the heat exchanger; when the sensed temperature is lower than the set second temperature, the controller controls the opening of the first valve 71 to be decreased, thereby reducing the flow of the fluid into the heat exchanger. The first temperature is higher than the second temperature.
Through the above-mentioned automatic detection and control of the opening of the first valve 71, the heat exchange condition of the heat exchanger can be automatically detected through the temperature of the output fluid, and the heat absorption condition of the heat exchanger can be detected, if the output temperature is too high, this indicates that the heat exchange condition is not good, and the flow needs to be increased for heat exchange, and if the output temperature is too low, it indicates that the fluid flow is too large, and the loss is easily caused, so the fluid flow can be reduced, and meanwhile, the temperature is too low for preventing the heat source. The measures avoid too much or too little heat exchange fluid to cause the incapability of carrying out heat exchange and heat dissipation in time, and avoid the phenomenon that the temperature of the heat source is too high or too low to influence the operation of the heat source.
Preferably, the controller detects the temperatures of the second and third temperature sensors to automatically control the opening degrees of the second and third valves 72 and 73, thereby adjusting the fluid flow rates of the outlets 201 and 202. In actual operation, the situation that heat exchange on the left side and the right side is uneven may exist, so that temperatures on two sides are different, the overall output temperature can be kept balanced by adjusting the flow of the fluid, and the phenomenon that the local temperature is too high or too low is avoided.
Preferably, when the detected temperature of the outlet 201 is higher than the temperature of the outlet 202 by a certain value (preferably, 2 degrees centigrade or more), the controller automatically controls the opening degree of the second valve 72 to decrease, and the opening degree of the third valve 73 to increase, so that the second outlet fluid flow rate decreases, and the first outlet fluid flow rate increases; when the detected temperature of the outlet 202 is higher than the temperature of the outlet 201 by a certain value (preferably more than 2 degrees celsius), the controller automatically controls the opening degree of the third valve 73 to be reduced, and the opening degree of the second valve 72 to be increased, so that the fluid flow of the outlet 202 is reduced and the fluid flow of the outlet 201 is increased. The fluid flow of the outlets 202 and 201 is adjusted, so that the heat exchange quantity of the fluid participating in the two sides is adjusted, the temperature of the two sides is kept uniform, and the phenomenon that the local temperature is too high to cause that a heat source does not exchange heat in time is avoided.
Preferably, a fourth temperature sensor and a fifth temperature sensor are provided on the outer wall surface of the substrate (the outer wall surface of the lower portion of the substrate, that is, the wall surface of the heat source base), the fourth temperature sensor is provided on the outer wall surface of the substrate between the inlet 1 and the outlet 202, and the fifth temperature sensor is provided on the outer wall surface of the substrate between the inlet 1 and the outlet 201. The fourth temperature sensor and the fifth temperature sensor are in data connection with the controller, and the controller automatically controls the flow of the fluid of the two outlets 201 and 202 according to the data of the fourth temperature sensor and the fifth temperature sensor.
The temperature of the fourth temperature sensor and the temperature of the fifth temperature sensor are detected, the heat exchange amount of the left area and the heat exchange amount of the right area can be judged, fluid distribution of two sides is automatically controlled according to the heat exchange amount of the two sides, the heat exchange of the internal fluid is enabled to be uniform, and the temperature of the lower wall surface is enabled to be uniform.
Preferably, when the temperature detected by the fourth temperature sensor is higher than the temperature detected by the fifth temperature sensor by a certain value (preferably more than 2 ℃), the controller automatically controls the flow of the outlet 202 to be reduced, and the flow of the outlet 201 to be increased; when the temperature detected by the fifth temperature sensor is higher than the temperature detected by the fourth temperature sensor by a certain value (preferably more than 2 ℃), the controller automatically controls the flow of the outlet 202 to increase, and the flow of the outlet 201 to decrease.
Preferably, when the temperature detected by the fourth temperature sensor is higher than the temperature detected by the fifth temperature sensor by a certain value (preferably, more than 2 ℃), the controller automatically controls the opening degree of the second valve 72 to decrease, and the opening degree of the third valve 73 to increase, so that the flow rate of the second outlet fluid decreases, and the flow rate of the first outlet fluid increases; when the temperature detected by the fifth temperature sensor is higher than the temperature detected by the fourth temperature sensor by a predetermined value (preferably, 2 degrees celsius or higher), the controller automatically controls the opening degree of the third valve 73 to decrease and the opening degree of the second valve 72 to increase, so that the fluid flow rate at the outlet 202 decreases and the fluid flow rate at the outlet 201 increases. The fluid flow of the outlets 202 and 201 is adjusted, so that the heat exchange quantity of the fluid participating in the two sides is adjusted, the temperature of the two sides is kept uniform, and the phenomenon that the local temperature is too high to cause that a heat source does not exchange heat in time is avoided.
Preferably, a plurality of the fourth temperature sensors and a plurality of the fifth temperature sensors may be provided. The average value of the plurality of temperature sensors is used as control data.
Preferably, a temperature sensor is disposed on the outer wall surface of the substrate, the temperature sensor is in data connection with a controller, and the controller automatically controls the fluid flow rate of the inlet 1 according to the data of the temperature sensor.
Preferably, the controller extracts the temperature data according to the time sequence, obtains the temperature difference of the temperature data through the comparison of the temperature data of the adjacent time periods, and automatically controls the fluid flow of the inlet 1 according to the temperature difference.
If the temperature of the previous period is T1 and the temperature of the next following period is T2, if T1< T2, the controller controls the opening of the first valve 71 to be increased, thereby increasing the flow rate of the fluid into the heat exchanger; if T1> T2, the controller controls the first valve 71 to decrease in opening, thereby decreasing the fluid flow into the heat exchanger.
Through the above-mentioned automatic detection and control of the opening of the first valve 71, the heat exchange condition of the heat exchanger can be automatically detected through the wall surface temperature of the substrate, the flow rate can be adjusted according to the output temperature condition of the heat source, if the output temperature is too high, this indicates that the heat exchange condition is not good, the flow rate needs to be increased for heat exchange, if the output temperature is too low, it indicates that the flow rate of the fluid is too large, and the loss is easily caused, so that the flow rate of the fluid can be reduced, and meanwhile, the temperature of the heat source is. The measures avoid too much or too little heat exchange fluid to cause the incapability of carrying out heat exchange and heat dissipation in time, and avoid the phenomenon that the temperature of the heat source is too high or too low to influence the operation of the heat source.
A pulsation generating device 8 is arranged on the pipe of the inlet 1, and the fluid entering the plate heat exchanger is made to pulsate flow by the pulsation generating device 8.
Preferably, the cylindrical fins are elastic structures, and the elastic structures can enable fluid to flow to wash the cylindrical fins, and the fins can oscillate in a pulsating mode, so that descaling is promoted.
Preferably, the cylindrical rib-like element may be a spring.
Preferably, the pipe line of the inlet 1 includes a main pipe line 11 and a bypass pipe line 12, the main pipe line 11 is provided with the bypass pipe line 12 in parallel, the pulsation generating device 8 is provided with the bypass pipe line 12, the main pipe line 11 and the bypass pipe line 12 connected in parallel with the bypass pipe line 12 are provided with a main valve 75 and a bypass valve 74, respectively, and whether or not the pulsation flow and the magnitude of the pulsation flow need to be generated is determined by opening and closing the main valve 75 and the bypass valve 74.
The pulsation generating device 8 is preferably an electromagnetic pump.
When the heat exchange capacity of the heat exchanger is reduced or the descaling is needed under other conditions, the bypass valve is opened, the main path valve is closed, and water passes through the electromagnetic pump to generate pulsating flow. And the bypass valve 74 is used for adjusting the generation time and generation intensity of the pulsating flow, so that the pulsating flow is induced and controlled to wash the cylindrical ribs, and the heat exchange efficiency is improved. Bypass valve 74 is configured to close and main valve 75 is configured to open for conditions not requiring pulsating flow oscillations.
The system further comprises a controller, wherein the electromagnetic pump, the main path valve 75 and the bypass valve 74 are in data connection with the controller, and the controller can control the frequency of the electromagnetic pump and the opening, closing and amplitude of the main path valve 75 and the bypass valve 74.
Under normal operating conditions, the main valve 75 is opened, the bypass valve 74 is closed, and the fluid normally enters the heat exchanger for heat exchange. When vibration descaling is needed or the heat exchange effect is improved, for example, the heat exchange efficiency is reduced, the controller controls the bypass valve to be opened, the main path valve to be closed, and the controller controls the electromagnetic pump to generate pulsating flow.
It is of course preferred that the heat exchange is always carried out by means of a pulsating flow.
Preferably, the sizes of the pulsating flow and the normal flow are automatically adjusted by controlling the sizes of the opening degrees of the bypass valve and the main valve.
The controller can control the magnitude of the pulsating flow as desired. For example, when the vibration noise of the heat exchange assembly is too large, or the heat exchange effect is relatively good, the scaling condition is not serious, the controller automatically controls the frequency or the flow of the pulsating flow to be reduced, and the equipment damage is avoided.
When the vibration noise of the heat exchanger is too large, the opening degree of the bypass valve can be controlled to be reduced, and the opening degree of the main path valve is increased, so that the flow of pulsating flow and normal flow is adjusted, the whole heat exchange flow is kept unchanged, and the whole heat exchange efficiency is kept.
If the vibration noise is reduced to a certain degree, the opening degree of the bypass valve can be controlled to be increased, and the opening degree of the main path valve is reduced, so that the flow of pulsating flow and normal flow is adjusted, the whole heat exchange flow is kept unchanged, and the whole heat exchange efficiency is kept.
Preferably, the noise level is detected by an instrument, the instrument is in data connection with the controller, and the opening degree of the bypass valve and the opening degree of the main valve are automatically adjusted through the data detected by the controller.
Preferably, the adjustment can be performed manually.
By means of the above-mentioned intelligent control, the generation of pulsating flows in the heat exchanger and the frequency and speed of the generation can be achieved.
Preferably, the fluid inlet 1 and the fluid outlets 201, 202 are located on the same line, and the fluid inlet 1 is located at a position intermediate the two fluid outlets 201, 202. Through the arrangement, the fluid distribution is more uniform, and the heat dissipation performance is more uniform.
Preferably, the base plate 10 and the cover plate 20 have a rectangular structure. Further preferred is a forward direction structure.
Preferably, the substrate 10 is provided with grooves 303 and 304, the cover plate 20 is provided with bosses 301 and 302, and the substrate and the cover plate are connected through the matching of the grooves and the bosses.
Preferably, the grooves 303, 304 are provided at diagonal positions of the substrate 10, at positions outside the parallel line formed by the two fourth baffles 404.
Preferably, the recesses 303, 304 are holes.
Preferably, the convex columns 301 and 302 are provided with threaded holes. The cover plate 10 and the base plate 20 are coupled by means of a screw connection.
Preferably, the lower portion of the sidewall of the cover plate 20 is provided with an outward extension perpendicular to the sidewall, and the extension is provided with a screw hole to match with a screw hole at a corresponding position on the base plate.
Between the second and third baffles, the farther from the center of the base plate, the farther between adjacent cylindrical ribs 501, from the center of the base plate. Mainly along with being farther away from the center of base plate, being closer to the third baffle more, the flow space of fluid is the less, and the velocity of flow can be fast relatively, and is farther away through setting up between the adjacent cylindrical fin 501 for the fluid velocity of flow keeps relative stability, makes whole heat transfer can reach relative even, avoids local inhomogeneous, causes local too early damage.
Further preferably, the further the distance between adjacent cylindrical ribs 501 from the center of the base plate, the further outward the distance from the center of the base plate, between the second baffle and the third baffle, increases continuously. The distribution also accords with the distribution rule change of fluid flow and heat exchange, and the heat exchange efficiency can be further improved through numerical simulation and experimental discovery.
Between the third and fourth baffles, the farther from the center of the base plate, the closer the adjacent cylindrical ribs 501 are from the center of the base plate. Mainly along with being farther away from the center of base plate, the flow space of fluid is bigger, and the velocity of flow can slow down relatively, and is more near through setting up between the adjacent cylindrical fin 501 for the fluid velocity of flow keeps relative stability, makes whole heat transfer can reach relative even, avoids local inhomogeneous being heated, causes local too early damage.
Further preferably, the closer the distance between the adjacent cylindrical ribs 501 is, the further the distance from the center of the base plate is, the more outward the center of the base plate, between the third baffle and the fourth baffle, the more gradually the distance is increased. The distribution also accords with the distribution rule change of fluid flow and heat exchange, and the heat exchange efficiency can be further improved through numerical simulation and experimental discovery.
A heat source, such as a CPU, is provided on the lower portion of the cover plate. Other hot fluids, such as other hot fluids, may also be provided to exchange heat with the water-cooled plate heat exchanger.
Adopt central diffusion type water-cooling board to carry out radiating liquid cooling system of indirect liquid cooling to the heat source includes: pump, pipeline system, water cooling plate, refrigerant, heat exchanger etc. Wherein the water cooling plate consists of a base plate, a cover plate and a flow passage. The bottom surface of the substrate is in direct contact with the heat source packaging structure (the contact surface is called as a hot flow surface), and the heat generated by the cold medium flowing through the water cooling plate is taken away. The refrigerant is selected from deionized water, ethylene glycol-deionized water with specified percentage and other media. In the designed central diffusion type cold plate, a refrigerant enters the cavity of the water cooling plate from the inlet of the central area of the cover plate, passes through the base plate flow guide structure, gradually flows to the periphery of the cavity of the cold plate from the central inlet area of the cold plate, and carries out convection heat exchange with the surfaces of various flow channels (including column ribs) in the flowing process, and finally flows out from the outlets at two sides of the cover plate of the water cooling plate after converging at the corners of the cold plate to take away heat generated by a heat source.
Further, the cover plate is provided with an inlet and an outlet of the refrigerant. The inside diameter of the cold plate inlet is about 2mm, the cold plate inlet is processed in the central area of the cover plate, and the specific structural form of the interface ensures that the refrigerant is not leaked. The cover plate should furthermore be provided with positioning and fastening means which can cooperate with the base plate in order to facilitate assembly.
Furthermore, the inner diameter of the outlet of the cold plate is consistent with the size of the inlet, but compared with the traditional water cooling plate, the central diffusion type cold plate changes the flowing mode that the refrigerant flows in and out singly, and replaces the flowing mode that the refrigerant flows in and out singly, so that the outlets are processed on two sides of the cover plate in the design, and the temperature uniformity of the hot flow surface of the cold plate can be effectively improved. However, this requires a three-way valve or the like to be added to the liquid cooling system.
Further, the diversion structure, actually some baffles, can be regarded as longer straight fins with larger size, and in order to reduce the flow resistance, the diversion structure is subjected to fillet treatment. The refrigerant flows in from the cover plate of the central diffusion type cold plate, passes through the flow guide structure, and gradually flows to the corner areas, so that the dead flowing area of the four corner areas of the cold plate can be avoided.
Further, the stud ribs are disposed in a low flow rate, high temperature region of the cold plate cavity. In the structural design of the secondary cold plate, the column ribs are uniformly designed into cylindrical column ribs. The height of the column ribs is set to be 4.7mm, and the arrangement mode of the column ribs is determined to be in a fork row or a straight row according to the general flow direction of the refrigerant in each area needing to be provided with the fins.
In addition, when the cover plate and the base plate are designed, a certain margin is left for generating a positioning and fastening structure by processing such as drilling, tapping and the like, besides considering the size of the heat source packaging structure.
When the indirect liquid cooling system operates, deionized water flows into the cold plate from the cold plate inlet 1, is shunted by the baffle plates (the baffle plates are symmetrically distributed about the axis of the cold plate, the same below) 401 which are symmetrically distributed, and flows around from four directions in a divergent manner; when the deionized water flows through the baffle 402, the deionized water is divided again and guided to the area of the column rib 501 (the column ribs are also symmetrically distributed about the axis of the cold plate) by the baffles 402 and 403, after passing through the baffle 403, the deionized water flowing out from the horizontal direction is divided at the baffles 404 on the left side and the right side, the deionized water flowing out from the vertical direction is divided at the inner wall of the cover plate, and after passing through the area of the column rib 502, the deionized water flows to the corner areas of the four outermost peripheries of the water-cooled plate, so that the flow dead zone is effectively reduced. Finally, the deionized water is converged at the outer sides of the left baffle 404 and the right baffle 404, and then flows out of the water cooling plate through the two outlets 201 and 202 of the cover plate. In the process of flowing inside the cold plate, the deionized water absorbs heat from a thin power assembly (CPU) and guided to the water cooling plate through the hot flow surface, and finally the heat is taken away along with the deionized water flowing out of the water cooling plate. The deionized water flowing out of the water cooling plate is cooled again to the required temperature through the external heat exchanger, and flows into the water cooling plate again to participate in heat dissipation, so that a cycle is completed.
The invention further researches the structure and the heat exchange condition of the structure.
The length of the first baffle is set asL 1 And the length of the second baffle is set toL 2 And the length of the third baffle is set toL 3 The length of the fourth baffle is set toL 4 And the thickness of each baffle is consistent and uniformly set asw；
A plurality of cylindrical fins are arranged between the second baffle plate and the third baffle plate and between the third baffle plate and the fourth baffle plate, and the diameters of the cylindrical fins are uniformly set to bedAnd the cylindrical rib between the third baffle and the fourth baffle is arranged as follows: of outlets 201, 202 from the water-cooled panelsMultiple rows of cylindrical fins in the direction of the axis line, wherein adjacent rows are all fork rows, and the distance of the central axis of the column ribs of the same row of adjacent cylindrical finsS 1 Distance of central axes of cylindrical ribs of adjacent rowsS 2 ；
The cylindrical fins between the second baffle and the third baffle are arranged as follows: multiple rows of cylindrical fins are arranged between the two opposite third baffles, the multiple rows of cylindrical fins are arranged in parallel with the third baffles, adjacent rows are all arranged in a fork manner, and the distance between the central axes of the column ribs of the same row of adjacent cylindrical fins is equal to the distance between the central axes of the column ribs of the same row of adjacent cylindrical finsS 1 Distance of central axes of cylindrical ribs of adjacent rowsS 2 。
S 1 、S 2 And the remaining structural dimensional parameters are labeled as shown in fig. 4. When in useS 1 、S 2 When it is changed, i.e. not a fixed value, adoptS 1 、S 2 Average value of (a).
The flow heat exchange performance of the cold plate and the size parameters of the flow passage structure of the cold plate are subjected to simulation calculation and fit to obtain a relation as follows:
in the above formulas:Nu f is the average number of knoop-sels,Dp w is the pressure drop of the inlet and the outlet of the cold plate,Reis the Reynolds number of the inlet of the refrigerant,D e is the equivalent diameter of the baffle plate,N baffle 、P baffle in order to correct the factor(s),S 1 ，S 2 ，d，L 1 ，L 2 ，L 3 ，L 4 ，wthe relative structural dimensions of the cold plate flow passage are as described aboveThe method comprises the following steps of; the respective physical quantities are defined as follows:
in formula 5ρFor the heat transfer fluid (deionized water) density,uin order to obtain the inlet velocity of the heat exchange fluid,d 1 is the pipe diameter of a heat exchange fluid inlet,μis a heat exchange hydrodynamic viscosity;
in the above-mentioned formula 7, the,hin order to obtain an average heat transfer coefficient,λheat conductivity coefficient of the heat exchange fluid;
in formula 8QThe power consumption is thermally designed for the electronic components,Afor the total area of the contact surface of the substrate and the refrigerant (including the extended surface of the column rib), the maximum temperature of the device is a concern in the electronic component heat management occasion of the water cooling plate application, so in the formula fitting process, the difference between the maximum temperature of the cooling plate and the temperature of the inlet refrigerant is adopted in the temperature difference definition mode:
the heat dissipation performance and the pumping power consumption of the water cooling plate can be estimated according to the above types.
Although the present invention has been described with reference to the preferred embodiments, it is not limited thereto. Various changes and modifications may be effected therein by one skilled in the art without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (4)
1. A plate heat exchanger intelligently controlled according to outlet temperature comprises a base plate, a cover plate, a fluid inlet and a fluid outlet, wherein the cover plate and the base plate are assembled together to form a fluid space; the device is characterized in that the fluid outlets are respectively provided with a second temperature sensor and a third temperature sensor which are respectively used for detecting the fluid temperatures of the two outlets, and the second temperature sensor and the third temperature sensor are respectively in data connection with the controller; the controller automatically controls the flow of the fluid at the inlet according to the detected fluid temperatures at the two outlets; when the detected temperature is higher than the set first temperature, the controller controls the opening of the first valve to increase, so that the flow of the fluid entering the heat exchanger is increased; when the detected temperature is lower than a set second temperature, the controller controls the opening of the first valve to be reduced, so that the flow of the fluid entering the heat exchanger is reduced; the baffle plates comprise a first baffle plate positioned in the center of the substrate, a second baffle plate surrounding the outside of the first baffle plate and a third baffle plate surrounding the outside of the second baffle plate;
the first baffle plates comprise four blocks, intervals are arranged between every two adjacent first baffle plates, the adjacent first baffle plates are in a vertical relation, and extension lines of the four first baffle plates form a first square;
the second baffle plates comprise four blocks, intervals are arranged between every two adjacent second baffle plates, the adjacent second baffle plates are in a vertical relation, the extension lines of the four second baffle plates form a second square, and the extension line of each first baffle plate passes through the middle point of the two second baffle plates;
the third baffle plates comprise four, intervals are arranged between every two adjacent third baffle plates, the adjacent third baffle plates are in a vertical relation, extension lines of the four third baffle plates form a third square, and the extension line of each second baffle plate passes through the middle point of the two third baffle plates;
a plurality of cylindrical fins are arranged between the second baffle plate and the third baffle plate;
the base plate further comprises fourth baffles arranged outside the third baffles, the fourth baffles are arranged in parallel, and the extension lines of the two third baffles pass through the middle point of one fourth baffle.
2. The heat exchanger of claim 1, wherein the inlet is piped with a first valve, the first valve being in data communication with the controller, and wherein the flow to the inlet is controlled by controlling the opening of the first valve.
3. The heat exchanger of claim 1, wherein the fluid temperatures of the two outlets are calculated from the average temperature of the two outlets.
4. The heat exchanger of claim 1, wherein the fluid inlet and the fluid outlet are collinear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911278812.1A CN111156841B (en) | 2019-12-13 | 2019-12-13 | Plate heat exchanger intelligently controlled according to outlet temperature |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911278812.1A CN111156841B (en) | 2019-12-13 | 2019-12-13 | Plate heat exchanger intelligently controlled according to outlet temperature |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111156841A CN111156841A (en) | 2020-05-15 |
| CN111156841B true CN111156841B (en) | 2020-10-16 |
Family
ID=70557236
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911278812.1A Active CN111156841B (en) | 2019-12-13 | 2019-12-13 | Plate heat exchanger intelligently controlled according to outlet temperature |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111156841B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113758312B (en) * | 2020-06-06 | 2023-02-03 | 青岛科技大学 | Heat exchanger with four fluid flow rates in cooperation with communication memory control |
| CN114264171A (en) * | 2021-12-09 | 2022-04-01 | 沈阳铝镁设计研究院有限公司 | Semen cooling device and process for two-stage decomposition |
| CN115371461A (en) * | 2022-01-26 | 2022-11-22 | 昆明理工大学 | Multi-parameter digital visual heat exchange system |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7597135B2 (en) * | 2006-05-23 | 2009-10-06 | Coolit Systems Inc. | Impingement cooled heat sink with low pressure drop |
| CN104344762B (en) * | 2013-07-25 | 2017-10-31 | 浙江三花汽车零部件有限公司 | The plate and its heat exchanger of heat exchanger |
| CN204375724U (en) * | 2015-02-05 | 2015-06-03 | 杭州沈氏节能科技股份有限公司 | A kind of microchannel cooling |
| WO2017059382A1 (en) * | 2015-09-30 | 2017-04-06 | Microfabrica Inc. | Micro heat transfer arrays, micro cold plates, and thermal management systems for cooling semiconductor devices, and methods for using and making such arrays, plates, and systems |
| CN206918963U (en) * | 2017-06-29 | 2018-01-23 | 湖南明和光电设备有限公司 | A kind of heat sink |
| CN109671688B (en) * | 2017-10-16 | 2020-08-28 | 中车株洲电力机车研究所有限公司 | Refrigerant phase change cold plate |
| CN208045481U (en) * | 2018-02-28 | 2018-11-02 | 爱美达（上海）热能系统有限公司 | A kind of central processing unit liquid cooling plate |
| CN208425113U (en) * | 2018-07-26 | 2019-01-22 | 贵州浪潮英信科技有限公司 | A kind of distributed liquid cooling plate for server |
| CN110779373B (en) * | 2019-11-12 | 2021-01-29 | 山东大学 | Water-cooled tube plate heat exchanger |
-
2019
- 2019-12-13 CN CN201911278812.1A patent/CN111156841B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN111156841A (en) | 2020-05-15 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110779373B (en) | Water-cooled tube plate heat exchanger | |
| CN111156841B (en) | Plate heat exchanger intelligently controlled according to outlet temperature | |
| CN111238265B (en) | Water-cooling plate heat exchanger with pulsating vibration | |
| CN111457763A (en) | Capillary heat exchanger for cooling variable-property fluid | |
| CN111336843B (en) | Water-cooling plate heat exchanger with circular structure | |
| CN111336844B (en) | Circular structure plate heat exchanger with adjacent temperature comparison control flow | |
| CN110793370B (en) | Design method of water-cooled tube plate heat exchanger | |
| CN110779371B (en) | Water-cooling tube-plate heat exchanger with optimally distributed fluid inlet and outlet | |
| CN110631302B (en) | Shell-and-tube heat exchanger with heat pipe combined with phase-change material | |
| CN112240716B (en) | Structure optimization method of liquid cooling plate type heat exchanger | |
| CN111156840B (en) | Water-cooling plate heat exchanger with uniform heat exchange | |
| CN111238264B (en) | Water-cooling plate heat exchanger capable of distributing flow according to wall surface temperature | |
| CN112033189B (en) | Plate heat exchanger cooled by liquid | |
| CN103629953A (en) | Water cooler | |
| CN110779372B (en) | Water-cooled tube plate heat exchanger with variable cylindrical fin spacing | |
| CN112344773B (en) | Temperature equalizing control method of liquid cooling plate type heat exchanger | |
| CN112461022B (en) | Liquid cooling plate heat exchanger with variable intervals | |
| CN112097551B (en) | Liquid cooling plate heat exchanger with multiple outlets distributed | |
| CN111076595B (en) | Plate-tube type fused salt heat storage component and heat storage tank thereof | |
| CN212274702U (en) | Capillary heat exchanger for cooling variable-property fluid | |
| CN209639306U (en) | Circulation drinks liquid refrigerating heat exchanger and refrigeration equipment | |
| CN213627920U (en) | Waste heat recovery system of air-cooled air compressor | |
| CN210537207U (en) | Radiator, air conditioner frequency converter with radiator and electronic equipment | |
| CN209246770U (en) | A kind of mini pipe diameter heat exchanger | |
| CN207635915U (en) | A kind of multitube distance tubular heat exchange device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |