A double-sided manifold micro-channel heat exchanger

Abstract

This invention provides a double-sided manifold microchannel heat exchanger, comprising, from top to bottom, an upper shell cover, an upper fluid distribution plate, a middle manifold core, a lower fluid distribution plate, and a lower shell cover. The inlet chamber is connected to the central linear inlet grooves on the upper and lower fluid distribution plates, allowing coolant entering from the inlet to be distributed within the middle manifold layer to the central inlet grooves on both sides. Left and right wedge-shaped return chambers are respectively connected to the left and right linear return grooves on the upper and lower fluid distribution plates, collecting coolant that flows from the middle to both sides through the upper and lower microchannels and then converges into the return grooves. This coolant then merges inside the middle manifold core and is discharged from the outlet. This invention provides a heat exchanger with a novel heat exchange structure that simultaneously provides cooling for multiple heat sources without increasing the number of external pipes, simplifying system connections and reducing flow pressure drop.

Description

Technical Field

[0001] This invention relates to heat exchanger technology, and more particularly to a flat plate heat exchanger, belonging to the field of heat pipes, specifically F28d15 / 02. Background Technology

[0002] A heat exchanger is a device that exchanges heat between hot and cold fluids. Heat exchangers are widely used in many fields. In industries such as electronics, petrochemicals, communications, and aerospace, due to their unique operating environments, there are special requirements for the size and weight of heat exchangers, as well as a higher heat exchange capacity.

[0003] In 1981, some scholars proposed using microchannels for heat dissipation, which could reduce the size of the heat exchanger and significantly improve its heat exchange capacity by utilizing the high specific surface area of ​​the microchannels. However, although its heat exchange capacity is strong, the overall pressure loss is also high due to the small hydraulic diameter of the microchannels.

[0004] Microchannels are a highly efficient thermal management solution. Their basic principle is that fluid flows through a microchannel driven by a pump, carrying away heat generated by electronic devices and achieving a cooling effect. However, this high heat dissipation performance comes at the cost of significant pump power and electrical energy consumption. Manifold microchannels, due to their unique manifold structure, can not only significantly reduce the pump power consumption of traditional microchannel heat sinks but also further enhance their heat dissipation performance. However, numerous studies have shown that the fluid distribution within manifold microchannels is not uniform, leading to uneven temperature distribution. Therefore, it is crucial to further reduce the pump power consumption of manifold microchannel heat sinks while simultaneously enhancing their heat dissipation performance and improving their temperature distribution characteristics.

[0005] Patent CN201811088661.9 discloses a manifold jet microchannel heat exchanger that enhances heat transfer through jet-enhanced disturbance and improves the temperature distribution characteristics at its bottom. Patent CN202010790271.2 discloses a high aspect ratio manifold microchannel heat exchanger that increases the heat transfer area and effectively reduces pressure drop. However, neither of these patents achieves structural optimization of the manifold microchannel, thus offering limited solutions to its main problems.

[0006] Patent CN202111560703.6 discloses a manifold micropillar array plate heat exchanger, which consists of a fluid inlet / outlet layer, a manifold distribution layer, and a micropillar array layer arranged sequentially from top to bottom. The fluid inlet / outlet layer includes an upper surface and a lower surface. The upper surface has a fluid inlet and a fluid outlet, while the lower surface has a fluid inlet channel and a fluid outlet channel. The fluid inlet and the fluid outlet are connected. The fluid inlet channel is located at a first end of the lower surface and extends along a first direction. The fluid outlet channel is located at the middle of the lower surface and extends in a direction perpendicular to the fluid inlet channel. This plate heat exchanger can be miniaturized by setting two inlet manifold inflow channels, which allows the fluid to flow into the inlet manifold in two directions. The fluid then impacts within the inlet manifold, which enhances the impact of the fluid on the micropillar array layer and improves the overall heat dissipation performance.

[0007] However, most existing manifold microchannel cold plates only have microchannels arranged on one side and a sealed structure on the other side. They can only cool the heat source on one side and cannot efficiently cool the heat sources on both sides at the same time on the same cold plate. It is also difficult to achieve a compact flow path topology in a limited space, starting from a single inlet, splitting into two directions inside and exchanging heat with the heat sources in both directions before being discharged from a single outlet. Summary of the Invention

[0008] The purpose of this invention is to provide a single-inlet and single-outlet manifold assembly for a double-sided microchannel cooling structure. While maintaining a simple structure and compact size, this manifold assembly allows coolant to enter through a single inlet, then be split into upper and lower sides within the middle manifold layer. The coolant then flows from the center to both sides through the upper and lower microchannel structures, and after converging on both sides, it re-converges through the middle manifold layer and exits through a single outlet. This provides cooling for heat sources in two directions simultaneously without increasing the number of external pipes, simplifying system connections and reducing flow pressure drop.

[0009] To achieve the above objectives, the technical solution of the present invention is as follows: A double-sided manifold microchannel heat exchanger includes, from top to bottom, an upper shell cover plate, an upper fluid distribution plate, a middle manifold core, a lower fluid distribution plate, and a lower shell cover plate. Microchannel structures are provided on the inner sides of both the upper and lower shell cover plates. The upper and lower fluid distribution plates are respectively attached to their corresponding microchannel structures. A central linear inlet channel extending along its length is provided, along with left and right linear return channels arranged on either side of the inlet channel. The middle manifold core has a central wedge-shaped inlet cavity communicating with an external inlet, and is equipped with... The left and right wedge-shaped return chambers at both ends of the inlet chamber are connected to the external outlet. The inlet chamber and the return chamber are not directly connected. The inlet chamber is connected to the middle linear inlet groove on the upper and lower fluid distribution plates, so that the coolant entering from the inlet is distributed to the middle inlet groove on the upper and lower sides in the middle manifold layer. The left and right wedge-shaped return chambers are connected to the left and right linear return grooves on the upper and lower fluid distribution plates, respectively. They are used to collect the coolant that flows from the middle to the sides through the upper and lower microchannels and then merges into the return groove. After merging inside the middle manifold core, the coolant is discharged from the outlet.

[0010] As an improvement, the inlet and outlet are located on the front and rear sides of the intermediate manifold core, respectively.

[0011] As an improvement, the wedge-shaped wide portion of the wedge-shaped inlet cavity is connected to the inlet, while the wedge-shaped tip is located away from the inlet.

[0012] As an improvement, a connecting channel is provided between the left and right wedge-shaped return cavities. The connecting channel is connected to the liquid outlet. The wedge-shaped wide part of the wedge-shaped return cavity is connected to the connecting channel, and the wedge-shaped tip of the wedge-shaped return cavity is away from the connecting channel.

[0013] As an improvement, the outlet is positioned further back than the wedge-shaped wide portion of the wedge-shaped return cavity, thereby forming a bent structure in the direction of the return cavity.

[0014] As an improvement, the flow area of ​​the wedge-shaped inlet cavity and / or wedge-shaped return cavity gradually decreases from top to bottom.

[0015] As an improvement, the rate at which the flow area of ​​the wedge-shaped inlet cavity and / or wedge-shaped return cavity gradually decreases from top to bottom gradually increases.

[0016] As an improvement, the capillary suction of the microchannel structure on the inner side of the upper shell cover is greater than that of the microchannel structure on the inner side of the lower shell cover.

[0017] As an improvement, the microchannel structure is directly formed in the upper and lower shell cover plates.

[0018] As an improvement, the microchannel structure is a separate structure from the upper and lower housing cover plates. The inner sides of both the upper and lower housing cover plates are machined with grooves for placing the microchannel cooling structure.

[0019] Compared with existing technologies, the present invention has the following advantages: The present invention adopts a symmetrical double-sided microchannel heat exchange structure, and achieves single-inlet diversion and single-outlet convergence through a central manifold, allowing a single radiator to simultaneously cool heat sources in both the upper and lower directions. Compared with existing single-sided microchannel cold plates or structures with one side sealed, it significantly improves heat dissipation capacity and integration within the same plate area. Compared with cold plate solutions requiring multiple inlet and outlet interfaces, the present invention only requires one set of inlet and outlet to complete liquid supply and collection on both sides, simplifying external piping, reducing the number of interfaces, lowering leakage risk, and facilitating compact space arrangement. Simultaneously, the present invention adopts a "central liquid inlet—two..." The "side-flow manifold" flow channel organization, with a central inlet chamber and two side flow manifolds in the middle manifold, makes the pressure distribution along the length direction smoother, effectively suppressing near-end short circuits and far-end flow shortages, improving the consistency of pressure difference at the inlet of each microchannel, thereby improving the uniformity of flow distribution and enhancing the uniformity of chip surface temperature distribution. In addition, the use of linear grooves / cavities for distribution and collection avoids the processing difficulty and clogging sensitivity caused by a large number of tiny distribution holes, making the structure easier to process, assemble, and maintain. Furthermore, the inlet chamber and flow manifold are not directly connected in structure, which can reduce bypass flow, increase the effective heat transfer ratio, and further reduce the flow pressure drop caused by ineffective circulation while ensuring heat dissipation performance.

[0020] This invention provides a single-inlet and single-outlet manifold assembly for a double-sided microchannel cooling structure. While maintaining a simple structure and compact size, the manifold assembly allows coolant to enter through a single inlet, then split into upper and lower sides within the middle manifold layer. The coolant then flows from the center to both sides through the upper and lower microchannel structures, converges on both sides, re-converges through the middle manifold layer, and exits through a single outlet. This provides cooling for heat sources in two directions simultaneously without increasing the number of external pipes, simplifying system connections and reducing flow pressure drop. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the overall structure of the heat exchanger of the present invention; Figure 2 This is a schematic diagram of the layered structure of the heat exchanger of the present invention; Figure 3 This is a schematic diagram of the upper shell cover structure of the present invention; Figure 4 This is a schematic diagram of the upper groove type fluid distribution plate structure of the present invention; Figure 5 Schematic diagram of the double-sided manifold core plate structure; Figure 6 Schematic diagram of flow in a double-sided manifold core plate; Figure 7 This is a schematic diagram of the overall flow of the heat exchanger.

[0022] Reference numerals: 1 Upper shell cover plate, 11 Positioning screw hole, 12 Upper microchannel mounting groove; 2 Upper grooved fluid distribution plate, 21 Upper left return groove, 22 Upper middle inlet groove, 23 Upper right return groove; 3 Double-sided manifold core plate, 31 Left side return manifold cavity, 32 Outlet, 33 Right side return manifold cavity, 34 Inlet, 35 Inlet guide wedge, 36 Return cavity connecting channel; 4 Lower grooved fluid distribution plate, 41 Lower left return groove, 42 Lower middle inlet groove, 43 Lower right return groove; 5 Lower shell cover plate, 51 Lower microchannel mounting groove. Detailed Implementation

[0023] The specific embodiments of the present invention will now be described in detail with reference to the accompanying drawings.

[0024] Unless otherwise specified, in this article, " / " represents division, and "×" and "*" represent multiplication.

[0025] It should be noted that, unless otherwise specified, the directional terms "front," "rear," "left," and "right" in this invention do not represent actual directions, but are merely for convenience of description. "Front" and "rear" are based on the direction of liquid flow; "front" indicates the direction of the inlet, and "rear" indicates the direction of the outlet. "Left" and "right" are based on the two sides of the inlet guide wedge. Figure 2 , 5 The left and right sides of the inlet guide wedge when viewed from the inlet to the outlet.

[0026] Figure 1-7 A bi-faced manifold microchannel heat exchanger is demonstrated. For example... Figure 1As shown, the double-sided manifold microchannel heat exchanger includes, from top to bottom, an upper shell cover plate 1, an upper fluid distribution plate 2, a middle manifold core 3, a lower fluid distribution plate 4, and a lower shell cover plate 5. Microchannel structures are provided on the inner sides of both the upper shell cover plate 1 and the lower shell cover plate 5. The upper fluid distribution plate 2 and the lower fluid distribution plate 4 are respectively attached to the corresponding microchannel structures. A central linear inlet groove 22, 42 extending along the front-to-back length direction is provided in the center of the upper fluid distribution plate 2 and the lower fluid distribution plate 4, along with left and right linear return grooves 21, 23, 41, 43 arranged on both sides of the inlet groove. The middle manifold core 3 has an inlet groove that connects to the external inlet. The central wedge-shaped liquid inlet chamber 35 is connected to the port 34, and the left and right wedge-shaped return chambers 31 and 32 are arranged at the left and right ends of the liquid inlet chamber and connected to the external liquid outlet 32. The liquid inlet chamber and the return chamber are not directly connected. The liquid inlet chamber is connected to the central linear liquid inlet groove on the upper fluid distribution plate and the lower fluid distribution plate, so that the coolant entering from the liquid inlet is distributed to the central liquid inlet groove on the upper and lower sides in the middle manifold layer. The left and right wedge-shaped return chambers are connected to the left and right linear return grooves on the upper fluid distribution plate and the lower fluid distribution plate, respectively, and are used to collect the coolant that flows from the middle to the sides through the upper and lower microchannels and then merges into the return groove, and is discharged from the liquid outlet after merging inside the middle manifold core.

[0027] This invention provides a single-inlet and single-outlet manifold assembly for a double-sided microchannel cooling structure. While maintaining a simple structure and compact size, the manifold assembly allows coolant to enter through a single inlet, then split into upper and lower sides within the middle manifold layer. The coolant then flows from the center to both sides through the upper and lower microchannel structures, converges on both sides, re-converges through the middle manifold layer, and exits through a single outlet. This provides cooling for heat sources in two directions simultaneously without increasing the number of external pipes, simplifying system connections and reducing flow pressure drop.

[0028] With the above structure, the same set of inlet and outlet ports can complete the liquid supply and collection for the microchannel cooling structure on both sides, realizing synchronous cooling of the double-sided chip. The flow channel organization of "middle manifold diversion - liquid inlet in the middle of the top and bottom - liquid return on both sides - liquid merging and discharge in the middle" improves the uniformity of fluid distribution and temperature distribution.

[0029] As an improvement, such as Figure 5 As shown, the inlet 34 and outlet 32 ​​are respectively located on the front and rear sides of the intermediate manifold core.

[0030] As an improvement, such as Figure 5 As shown, the wedge-shaped wide portion of the wedge-shaped liquid inlet cavity 35 is connected to the liquid inlet, and the wedge-shaped tip is located away from the liquid inlet.

[0031] By connecting the wedge-shaped wide portion of the wedge-shaped inlet cavity 3445 to the inlet and arranging the wedge-shaped tip towards the direction away from the inlet, the coolant entering the radiator gradually transitions from a large cross-section to a small cross-section within the wedge-shaped inlet cavity. This avoids the strong impact and flow separation caused by the sudden narrowing of the channel, and facilitates the formation of a relatively gentle and uniform pressure distribution along the length of the wedge-shaped inlet cavity. This improves the flow distribution at the microchannel inlet at different locations and reduces the local flow resistance on the inlet side.

[0032] As an improvement, a connecting channel 36 is provided between the left and right wedge-shaped return cavities. The connecting channel is connected to the outlet 32. The wedge-shaped wide portion of the wedge-shaped return cavity is connected to the connecting channel, and the wedge-shaped tip of the wedge-shaped return cavity is away from the connecting channel. By providing a connecting channel 36 between the left and right wedge-shaped return cavities and connecting it to the outlet 32, and arranging the wedge-shaped wide portion of the wedge-shaped return cavity to be connected to the connecting channel and the wedge-shaped tip away from the connecting channel, the coolant flowing from each microchannel enters from the far end of the return cavity. As it flows towards the connecting channel, the channel cross-section gradually increases and the flow velocity gradually decreases. This reduces the local pressure drop and eddies on the outlet side, facilitating thorough mixing and uniform convergence of the return flows from both sides near the connecting channel area, thus improving the stability of the return flow and the consistency of the outlet flow distribution.

[0033] Because the cross-section of the wedge-shaped inlet chamber 35 gradually decreases in width along the main flow direction of the coolant, while the cross-section of the wedge-shaped return chambers 31 and 33 gradually increases in width along the main flow direction of the coolant, their wedge-shaped directions are opposite, forming a complementary pressure gradient distribution on the inlet and outlet sides of the microchannel. On the one hand, the tapering structure on the inlet side helps to suppress excessive flow near the inlet end of the channel and increase the supply pressure of the distal channel; on the other hand, the expanding structure on the return side weakens the excessive suction effect near the outlet end of the channel and improves the return capacity of the distal channel. Through this wedge-shaped combination in opposite directions, the flow distortion on both sides of the microchannel inlet and outlet can be improved simultaneously, allowing microchannels arranged in different positions to obtain a more uniform pressure differential driving force, thereby improving the uniformity of flow distribution within the channel and the temperature field on the chip surface.

[0034] As an improvement, such as Figure 5 As shown, the outlet is further back than the wedge-shaped wide portion of the wedge-shaped return cavity, thus forming a bent structure in the direction of the return cavity.

[0035] By positioning the outlet 32 ​​further back relative to the wedge-shaped width of the return cavity, the connecting channel 36 forms a bend towards the return cavity on the side closest to it. This extends the flow path of the coolant from the left and right wedge-shaped return cavities to the outlet and introduces appropriate local resistance at the bend. This structure, on the one hand, reduces the direct suction effect of the outlet on the return cavity on the side closest to it, avoiding a "short-circuit" phenomenon where the return flow on one side is significantly larger. On the other hand, it facilitates the remixing and balancing of the fluids from the left and right return cavities within the connecting channel, thereby further improving the uniformity of flow rate and temperature at the outlet.

[0036] As an improvement, the flow area of ​​the wedge-shaped inlet chamber and / or wedge-shaped return chamber gradually decreases from top to bottom. Since the heat exchanger is arranged vertically, the fluid flow direction is preferably downwards due to gravity. This application, by setting the flow area to gradually decrease vertically, reduces the lower flow area and increases the lower flow resistance, allowing the fluid to flow upwards during distribution. This ensures uniform distribution of the fluid vertically, enabling balanced heat release from both the upper and lower heat sources and avoiding uneven heat exchange caused by uneven vertical distribution.

[0037] As an improvement, the flow area of ​​the wedge-shaped inlet chamber and / or wedge-shaped return chamber gradually decreases from top to bottom, with the rate of decrease gradually increasing. This invention, through the variation in area size, can further achieve uniform fluid distribution between the upper and lower parts of the body, thereby ensuring effective heat exchange.

[0038] As an improvement, the capillary suction force of the microchannel structure inside the upper shell cover is greater than that of the microchannel structure inside the lower shell cover. Because the fluid enters the left and right linear return channels from the central linear inlet channels 22 and 42 through capillary suction, and because the heat exchanger is arranged vertically, the fluid flow direction is preferably downwards due to gravity. Therefore, by increasing the capillary suction force at the top, the liquid absorption capacity at the top can be increased, thereby ensuring a uniform distribution of the fluid in the vertical direction. This allows both the upper and lower heat sources to release heat evenly, avoiding uneven heat exchange caused by uneven distribution in the vertical direction.

[0039] As an improvement, the microchannel structure is directly formed in the upper and lower shell cover plates.

[0040] As an improvement, the microchannel structure is a separate structure from the upper and lower housing cover plates. The inner sides of both the upper and lower housing cover plates are machined with grooves for placing the microchannel cooling structure.

[0041] The work process is as follows: like Figure 6 , Figure 7As shown, during use, the coolant first flows into the device through the inlet located on the side wall of the intermediate manifold core 3, entering the central wedge-shaped inlet cavity 35 inside the intermediate manifold core 3. After spreading along the length direction within the central wedge-shaped inlet cavity 35, the coolant flows into the upper central inlet groove 22 in the middle of the upper fluid distribution plate 2 and the lower central inlet groove 42 in the middle of the lower fluid distribution plate 4 through the connecting holes provided on the upper and lower surfaces of the cavity, and is distributed along the length direction within the grooves. Subsequently, the coolant enters the upper and lower microchannel structures through the upper and lower central inlet grooves 22 and 42 through the upper and lower microchannel inlets on their opposite sides, flowing from the center to the left and right sides within the microchannels, exchanging heat with the chip surfaces arranged on both sides of the cold plate.

[0042] After heat exchange, the coolant flows sequentially from the upper microchannel outlet into the upper left return tank 21 and the upper right return tank 23, and from the lower microchannel outlet into the lower left return tank 41 and the lower right return tank 43, and then converges along the length of each return tank to both ends of the device. The converged fluid enters the left and right wedge-shaped return cavities 31 and 33 inside the intermediate manifold core 3 through the return communication holes set between the upper and lower fluid distribution plates 2 and 4 and the intermediate manifold core 3. After further merging in the left and right wedge-shaped return cavities 31 and 33, it is introduced into the outlet channel located in the middle, and finally discharged from the device through the outlet arranged on the side wall of the intermediate manifold core 3.

[0043] Through the above flow process, the coolant can simultaneously supply and collect liquid to the upper and lower microchannel structures inside the device using only a single inlet and a single outlet. This achieves a circulating flow where the coolant enters from the middle, exchanges heat from the middle to the sides through the upper and lower microchannels, flows back from the sides, and converges and discharges in the middle. This balances structural compactness, flow pressure drop, and uniformity of cooling for both sides of the chip.

[0044] While the present invention has been disclosed above with reference to preferred embodiments, it is not limited thereto. Any person skilled in the art can make various modifications and alterations without departing from the spirit and scope of the invention; therefore, the scope of protection of the present invention should be determined by the scope defined in the claims.

Claims

1. A double-sided manifold microchannel heat exchanger, comprising, from top to bottom, an upper shell cover plate, an upper fluid distribution plate, a middle manifold core, a lower fluid distribution plate, and a lower shell cover plate. The inner sides of both the upper and lower shell cover plates are provided with microchannel structures. The upper and lower fluid distribution plates are respectively attached to their corresponding microchannel structures. A central linear inlet channel extending along its length and left and right linear return channels arranged on both sides of the inlet channel are provided. The middle manifold core has a central wedge-shaped inlet cavity communicating with an external inlet port, and a distribution... The left and right wedge-shaped return chambers are located at the left and right ends of the inlet chamber and are connected to the external outlet. The inlet chamber and the return chamber are not directly connected. The inlet chamber is connected to the middle linear inlet groove on the upper and lower fluid distribution plates, so that the coolant entering from the inlet is distributed to the middle inlet groove on the upper and lower sides in the middle manifold layer. The left and right wedge-shaped return chambers are connected to the left and right linear return grooves on the upper and lower fluid distribution plates, respectively. They are used to collect the coolant that flows from the middle to the sides through the upper and lower microchannels and then merges into the return groove. After merging inside the middle manifold core, the coolant is discharged from the outlet.

2. The heat exchanger as described in claim 1, characterized in that, The inlet and outlet are located on the front and rear sides of the intermediate manifold core, respectively.

3. The heat exchanger as described in claim 2, characterized in that, The wedge-shaped wide portion of the wedge-shaped inlet chamber connects to the inlet, while the wedge-shaped apex is located away from the inlet.

4. The heat exchanger as described in claim 3, characterized in that, A connecting channel is provided between the left and right wedge-shaped return cavities. The connecting channel is connected to the liquid outlet. The wedge-shaped wide part of the wedge-shaped return cavity is connected to the connecting channel, and the wedge-shaped tip of the wedge-shaped return cavity is away from the connecting channel.

5. The heat exchanger as described in claim 4, characterized in that, The outlet is further back than the wedge-shaped wide portion of the wedge-shaped return cavity, thus forming a bend in the channel towards the return cavity.

6. The heat exchanger as described in claim 1, characterized in that, From top to bottom, the flow area of ​​the wedge-shaped inlet cavity and / or wedge-shaped return cavity gradually decreases.

7. The heat exchanger as described in claim 6, characterized in that, From top to bottom, the rate at which the flow area of ​​the wedge-shaped inlet cavity and / or wedge-shaped return cavity gradually decreases gradually increases.

8. The heat exchanger as described in claim 6, characterized in that, The capillary suction force of the microchannel structure on the inner side of the upper shell cover is greater than that of the microchannel structure on the inner side of the lower shell cover.

9. The heat exchanger as described in claim 8, characterized in that, The microchannel structure is formed directly on the upper and lower shell cover plates.

10. The heat exchanger as claimed in claim 9, characterized in that, The microchannel structure is separate from the upper and lower housing cover plates. The inner sides of both the upper and lower housing cover plates are machined with grooves for placing the microchannel cooling structure.

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