CN110779372A - Water-cooled tube plate heat exchanger with variable cylindrical fin spacing - Google Patents
Water-cooled tube plate heat exchanger with variable cylindrical fin spacing Download PDFInfo
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- CN110779372A CN110779372A CN201911102542.9A CN201911102542A CN110779372A CN 110779372 A CN110779372 A CN 110779372A CN 201911102542 A CN201911102542 A CN 201911102542A CN 110779372 A CN110779372 A CN 110779372A
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- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0015—Heat and mass exchangers, e.g. with permeable walls
Abstract
The invention provides a water-cooled tube plate heat exchanger with variable cylindrical fin intervals, which comprises a base plate and a cover plate, wherein the cover plate and the base plate are assembled together to form a fluid space; cylindrical fins are arranged between the second baffle plate and the third baffle plate, and the farther the distance from the center of the base plate is from the center of the base plate, the farther the distance between the adjacent cylindrical fins is. The invention aims to keep the flow velocity of fluid relatively stable by setting the farther the distance between adjacent cylindrical fins is, so that the overall heat exchange can be relatively uniform, and the local premature damage caused by nonuniform heating can be avoided.
Description
Technical Field
The invention belongs to the technical field of heat exchangers, and particularly relates to a plate heat exchanger with a flow guide structure and column ribs combined.
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.
Disclosure of Invention
The invention aims to provide a water-cooling plate heat exchanger, which changes 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 water-cooling plate, and is provided with column ribs to improve the heat dissipation characteristic of the water-cooling plate.
In order to achieve the purpose, the technical scheme of the invention is as follows:
a water-cooling plate heat exchanger with variable cylindrical fins comprises a base plate and a cover plate, wherein the cover plate and the base plate are assembled together to form a fluid space;
cylindrical fins are provided between the second base plate and the third base plate, and the farther from the center of the base plate, the farther between adjacent cylindrical fins.
Preferably, the distance between adjacent cylindrical fins increases continuously between the second base plate and the third base plate from the center of the base plate to the outside, the farther the distance from the center of the base plate.
Preferably, 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 also comprises fourth baffle plates arranged outside the third baffle plates, the fourth baffle plates are arranged in parallel, and the extension lines of the two third baffle plates pass through the middle point of one fourth baffle plate;
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, the farther the distance between the adjacent cylindrical fins 501 is, the relatively stable fluid flow speed is kept, the relatively uniform overall heat exchange can be realized, and the local premature damage caused by the non-uniform local heating can be avoided.
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.
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. the cover plate has blank regions 601 and 602 (where screw holes are processed and are matched and fastened with screw holes at positions corresponding to the substrate through screws to prevent leakage of refrigerant). 10 base plate, 20 apron.
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 the heating component is large, the cooling capacity is strong, and the temperature of the hot spot area of the CPU packaging structure 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 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 CPU package 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 dimension of the CPU 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 as
L 1 And the length of the second baffle is set to
L 2 And the length of the third baffle is set to
L 3 The length of the fourth baffle is set to
L 4 And the thickness of each baffle is consistent and uniformly set as
w；
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 be
dAnd the cylindrical rib between the third baffle and the fourth baffle is arranged as follows: the water cooling plate outlets 201 and 202 are connected in a plurality of rows of cylindrical fins in the direction of the line of the axes, adjacent rows are all fork rows, and the distance between the central axes of the column ribs of the same row of adjacent cylindrical fins
S 1 Distance of central axes of cylindrical ribs of adjacent rows
S 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 fins
S 1 Distance of central axes of cylindrical ribs of adjacent rows
S 2 。
S 1 、
S 2 And the remaining structural dimensional parameters are labeled as shown in fig. 4. When in use
S 1 、
S 2 When it is changed, i.e. not a fixed value, adopt
S 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 above; the respective physical quantities are defined as follows:
in formula 5
ρFor 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 8
QThe 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 (3)
1. A water-cooled tube plate heat exchanger with variable cylindrical fin intervals comprises a base plate and a cover plate, wherein the cover plate and the base plate are assembled together to form a fluid space;
cylindrical fins are arranged between the second baffle plate and the third baffle plate, and the farther the distance from the center of the base plate is from the center of the base plate, the farther the distance between the adjacent cylindrical fins is.
2. The heat exchanger of claim 1 wherein the further the distance from the center of the base plate, the further the distance between adjacent cylindrical fins increases in magnitude between the second baffle and the third baffle from the center of the base plate outward.
3. The heat exchanger of claim 1, wherein the first baffle plates comprise four, adjacent first baffle plates are spaced apart from one another, adjacent first baffle plates are in a perpendicular relationship with one another, 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 also comprises fourth baffle plates arranged outside the third baffle plates, the fourth baffle plates are arranged in parallel, and the extension lines of the two third baffle plates pass through the middle point of one fourth baffle plate;
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.
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