Single-phase two-phase hybrid cold plate

Abstract

The utility model discloses a single -phase two -phase mixed cold plate for cooling the object to be cooled, include: casing, first radiating mechanism and second radiating mechanism, the casing is two layers hollow structure of mutual isolation, wherein the lower layer is first cooling flow channel, and the upper layer is second cooling flow channel, and the first cooling flow channel and second cooling flow channel all have the cooling liquid that passes in, the cooling liquid in the first cooling flow channel is used to carry out phase change cooling to the object to be cooled, and the cooling liquid in the second cooling flow channel carries out indirect cooling to the object to be cooled through the non phase change cooling of first cooling flow channel, and the first radiating mechanism is located in the inside of first cooling flow channel and sets up, and the second radiating mechanism is located in the inside of second cooling flow channel and sets up corresponding first cooling flow channel. The utility model can realize greater sensible heat exchange, improve the heat flow density of first cooling flow channel, prevent first cooling flow channel dry burning.

Description

Technical Field

[0001] This utility model relates to the field of cooling equipment technology, and in particular to a single-phase and two-phase hybrid cold plate. Background Technology

[0002] Two-phase cooling equipment is a type of heat exchange device that typically uses water or air as a coolant to remove heat. It is a widely used heat exchange device in industries such as metallurgy, chemical engineering, energy, transportation, light industry, and food processing. In existing technologies, with a fixed inlet pressure, the cooling equipment contains a two-phase flow of gas and liquid, resulting in significant flow resistance and limiting the flow rate of the liquid coolant. This restricts the amount of sensible heat that can be transferred. Furthermore, the temperature of the fluid in the cooling equipment is its evaporation temperature; when the temperature difference between the evaporation temperature and the ambient temperature is large, there is a potential thermal impact on the environment. Summary of the Invention

[0003] According to an embodiment of the present invention, a single-phase and two-phase hybrid cold plate is provided for cooling an object to be cooled, comprising: a shell, a first heat dissipation mechanism, and a second heat dissipation mechanism;

[0004] The object to be cooled is located below the shell, which is a two-layer hollow structure isolated from each other. The lower layer is a first cooling channel, and the upper layer is a second cooling channel. Coolant flows through both the first and second cooling channels. The coolant in the first cooling channel is used for phase change cooling of the object to be cooled, while the coolant in the second cooling channel indirectly cools the object to be cooled by non-phase change cooling of the first cooling channel. Both the first and second cooling channels are provided with inlet and outlet ports to allow the flow of coolant within them. The first heat dissipation mechanism is located inside the first cooling channel and is positioned corresponding to the object to be cooled, while the second heat dissipation mechanism is located inside the second cooling channel and is positioned corresponding to the first cooling channel.

[0005] Furthermore, both the first and second heat dissipation mechanisms are heat dissipation layers, which are laid at the bottom of the first or second cooling channel and have a porous metal structure.

[0006] Furthermore, the porous metal structure is formed by sintering.

[0007] Furthermore, both the first and second heat dissipation mechanisms are heat dissipation fins, which are evenly arranged at the bottom of the first or second cooling channel.

[0008] Furthermore, the first heat dissipation mechanism is a heat dissipation layer, which is laid at the bottom of the first cooling channel and has a porous metal structure; the second heat dissipation mechanism is heat dissipation fins, which are evenly arranged at the bottom of the second cooling channel.

[0009] Furthermore, the second cooling channel partially surrounds the outside of the first cooling channel, and the contact surfaces of the first cooling channel and the second cooling channel are each provided with a second heat dissipation mechanism.

[0010] Furthermore, the second cooling channel partially surrounds the top and sides of the first cooling channel, and the contact surfaces of the first cooling channel and the second cooling channel are provided with a second heat dissipation mechanism.

[0011] Furthermore, the coolant is deionized water, ethylene glycol solution, propylene glycol solution, or fluorinated liquid.

[0012] Furthermore, the liquid outlet of the first cooling channel is connected to the liquid outlet of the second cooling channel via a T-joint.

[0013] According to an embodiment of this utility model, a single-phase and two-phase hybrid cold plate is provided. The inlet pressure of the second cooling channel is the saturation pressure of the coolant. The inlet temperature of the coolant in the second cooling channel is lower than the evaporation temperature of the first cooling channel, thus the second cooling channel cools the first cooling channel. The temperature of the outer wall of the first cooling channel is the evaporation temperature of the coolant at the inlet pressure of the second cooling channel. Because there is no heat exchange at the evaporation temperature, the coolant in the second cooling channel will always remain liquid. In the liquid state, the flow resistance of the coolant in the second cooling channel will be lower than that of the first cooling channel, thus allowing more liquid coolant to pass through, achieving greater sensible heat transfer, increasing the heat flux density of the first cooling channel, and preventing the first cooling channel from dry-burning. When the subcooling temperature of the coolant in the second cooling channel is high, it can reduce the surface temperature of the heat exchanger, reducing the environmental impact of the first cooling channel. When the heat load of the first cooling channel significantly exceeds the design load, causing dry-burning of the first cooling channel, the second cooling channel will undergo a phase change, maintaining the temperature of the first cooling channel for a short time, thus protecting against heat load overload.

[0014] It should be understood that both the foregoing general description and the following detailed description are exemplary and intended to provide further illustration of the claimed technology. Attached Figure Description

[0015] Figure 1 This is a structural diagram of a single-phase and two-phase hybrid cold plate according to an embodiment of the present invention;

[0016] Figure 2 This is a structural diagram of another single-phase and two-phase hybrid cold plate according to an embodiment of the present utility model.

[0017] In the figure, the following labels are used: 1 represents the casing, 2 represents the first cooling channel, 3 represents the second cooling channel, 4 represents the first heat dissipation mechanism, and 5 represents the second heat dissipation mechanism. Detailed Implementation

[0018] The preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings, further illustrating the present invention.

[0019] like Figures 1-2 As shown, a single-phase and two-phase hybrid cold plate according to an embodiment of the present invention is used to cool the object to be cooled, including: a shell 1, a first heat dissipation mechanism 4, and a second heat dissipation mechanism 5;

[0020] The object to be cooled is located below the housing 1, which is a two-layer hollow structure isolated from each other. The lower layer is a first cooling channel 2, and the upper layer is a second cooling channel 3. Coolant flows through both the first and second cooling channels 2 and 3. The coolant in the first cooling channel 2 is used for phase change cooling of the object to be cooled, while the coolant in the second cooling channel 3 indirectly cools the object by non-phase change cooling of the first cooling channel 2. Both the first and second cooling channels 2 and 3 are provided with inlet and outlet ports to allow the flow of coolant. The first heat dissipation mechanism 4 is located inside the first cooling channel 2 and is positioned corresponding to the object to be cooled. The second heat dissipation mechanism 5 is located inside the second cooling channel 3 and is positioned corresponding to the first cooling channel 2. The thickness of the heat dissipation mechanism is not less than one-fifth of the height of the first cooling channel 2. The coolant is deionized water, ethylene glycol solution, propylene glycol solution, or fluorinated liquid.

[0021] The inlet pressure of the second cooling channel 3 in this application is the saturation pressure of the coolant. The inlet temperature of the coolant in the second cooling channel 3 is lower than the evaporation temperature of the first cooling channel 2, therefore the second cooling channel 3 cools the first cooling channel 2. The temperature of the outer wall of the first cooling channel 2 is the evaporation temperature of the coolant at the inlet pressure of the second cooling channel 3. Because there is no heat exchange at the evaporation temperature, the coolant in the second cooling channel 3 will always remain liquid. In the liquid state, the flow resistance of the coolant in the second cooling channel 3 will be lower than that of the first cooling channel 2, thus allowing more liquid coolant to pass through, achieving greater sensible heat transfer, increasing the heat flux density of the first cooling channel 2, and preventing the first cooling channel 2 from dry burning. When the subcooling temperature of the coolant in the second cooling channel 3 is large, it can reduce the surface temperature of the heat exchanger and reduce the environmental impact of the first cooling channel 2. When the heat load of the first cooling channel 2 seriously exceeds the design load and dry burning occurs, the second cooling channel 3 will also undergo a phase change, maintaining the temperature of the first cooling channel 2 for a short time, thus protecting against heat load overload.

[0022] like Figure 1As shown, the first heat dissipation mechanism 4 is a heat dissipation layer, which is laid at the bottom of the first cooling channel 2. The heat dissipation layer is a porous metal structure. The second heat dissipation mechanism 5 is a heat dissipation fin, which is evenly arranged at the bottom of the second cooling channel 3.

[0023] In this embodiment, the first heat dissipation mechanism 4 and the second heat dissipation mechanism 5 are different heat dissipation structures. The first heat dissipation mechanism 4 is a heat dissipation layer with a porous metal structure, while the second heat dissipation mechanism 5 in the second cooling channel 3 is a heat dissipation fin. Since the first heat dissipation mechanism 4 is a heat dissipation fin, the second heat dissipation mechanism 5 is a heat dissipation layer.

[0024] like Figures 1-2 As shown, both the first heat dissipation mechanism 4 and the second heat dissipation mechanism 5 are heat dissipation layers. The heat dissipation layer is laid at the bottom of the first cooling channel 2 or the second cooling channel 3, and the heat dissipation layer is a porous metal structure. The porous metal structure is formed by sintering.

[0025] The heat dissipation layer is a porous metal structure formed by sintering, or a metal powder block formed by sintering. It has a certain degree of air permeability, which allows the coolant to diffuse into the heat dissipation layer through capillary action, thereby improving the heat exchange effect.

[0026] In this embodiment, the heat dissipation layer in the first cooling channel 2 is a porous structure, and the heat dissipation layer in the second cooling channel 3 is a microchannel structure.

[0027] like Figures 1-2 As shown, both the first heat dissipation mechanism 4 and the second heat dissipation mechanism 5 are heat dissipation fins, which are evenly arranged at the bottom of the first cooling channel 2 or the second cooling channel 3.

[0028] Heat dissipation fins can increase the contact area with the coolant, thereby improving the cooling effect.

[0029] like Figure 2 As shown, the second cooling channel 3 partially surrounds the outside of the first cooling channel 2, and the contact surfaces of the first cooling channel 2 and the second cooling channel 3 are provided with a second heat dissipation mechanism 5.

[0030] The second cooling channel 3 partially surrounds the top and sides of the first cooling channel 2, and the contact surfaces of the first cooling channel 2 and the second cooling channel 3 are provided with a second heat dissipation mechanism 5.

[0031] The second heat dissipation mechanism 5 is set outside the first heat dissipation mechanism 4 with a semi-enclosed structure, which can protect the first heat dissipation mechanism 4 and improve the cooling effect of the second heat dissipation mechanism 5 on the first heat dissipation mechanism 4.

[0032] like Figures 1-2 As shown, the liquid outlet of the first cooling channel 2 and the liquid outlet of the second cooling channel 3 are connected by a T-joint.

[0033] The coolant flowing from the outlet in the first cooling channel 2 and the second cooling channel 3 has a different temperature. The coolant is collected together through the T-joint to make the temperature of the coolant more uniform, which facilitates the subsequent circulation of the coolant for heat exchange.

[0034] In this embodiment, the first cooling channel 2 and the second cooling channel 3 may be interconnected or not interconnected, and different coolants may be introduced into the first cooling channel 2 and the second cooling channel 3 respectively.

[0035] Above, refer to Figures 1-2 This invention describes a single-phase and two-phase hybrid cold plate according to an embodiment of the present invention. The inlet pressure of the second cooling channel 3 is the saturation pressure of the coolant. The inlet temperature of the coolant in the second cooling channel 3 is lower than the evaporation temperature of the first cooling channel 2, thus the second cooling channel 3 cools the first cooling channel 2. The temperature of the outer wall of the first cooling channel 2 is the evaporation temperature of the coolant at the inlet pressure of the second cooling channel 3. Because there is no heat exchange at the evaporation temperature, the coolant in the second cooling channel 3 will always remain liquid. In the liquid state, the flow resistance of the coolant in the second cooling channel 3 will be lower than that of the first cooling channel 2, thus allowing more liquid coolant to pass through, achieving greater sensible heat transfer, increasing the heat flux density of the first cooling channel 2, and preventing the first cooling channel 2 from dry burning. When the subcooling temperature of the coolant in the second cooling channel 3 is high, the surface temperature of the heat exchanger can be reduced, minimizing the environmental impact of the first cooling channel 2. When the heat load of the first cooling channel 2 seriously exceeds the design load and the first cooling channel 2 is dry-burned, the second cooling channel 3 will also undergo a phase change to maintain the temperature of the first cooling channel 2 for a short time, thus protecting against heat load overload.

[0036] The first cooling channel 2 and the second cooling channel 3 of this application use different coolants. The inlet pressure of the first cooling channel 2 is the saturation pressure of the coolant. After absorbing heat from the object to be cooled through the first heat dissipation mechanism 4, the coolant partially evaporates, achieving phase change cooling of the object. The evaporation temperature of the coolant in the second cooling channel 3 is higher than that of the coolant in the first cooling channel 2, while the inlet temperature of the coolant in the second cooling channel 3 is lower than that of the first cooling channel 2. The coolant in the second cooling channel 3 absorbs heat from the first cooling channel 2 through the second heat dissipation mechanism 5, achieving single-phase cooling of the first cooling channel 2. The inlet pressure of the second cooling channel 3 can be appropriately increased. In the liquid state, the flow resistance of the coolant in the second cooling channel 3 will be lower than that in the two-phase state, thus allowing more liquid coolant to pass through, achieving greater sensible heat transfer, increasing the heat flux density of the first cooling channel 2, and preventing the first cooling channel 2 from dry burning. When the subcooling temperature of the coolant in the second cooling channel 3 is large, the surface temperature of the heat exchanger can be reduced, minimizing the heat exchanger's environmental impact.

[0037] It should be noted that, in this specification, the terms "comprising," "including," or any other variations thereof are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Unless otherwise specified, an element defined by the phrase "comprising..." does not exclude the presence of additional identical elements in the process, method, article, or apparatus that includes said element.

[0038] Although the present invention has been described in detail through the above preferred embodiments, it should be understood that the above description should not be considered as a limitation of the present invention. Various modifications and substitutions to the present invention will be apparent to those skilled in the art after reading the above content. Therefore, the scope of protection of the present invention should be defined by the appended claims.

Claims

1. A single-phase and two-phase hybrid cold plate for cooling an object, characterized in that, include: Housing, first heat dissipation mechanism, and second heat dissipation mechanism; The object to be cooled is located below the shell, which is a two-layer hollow structure isolated from each other. The lower layer is a first cooling channel, and the upper layer is a second cooling channel. Coolant flows through both the first and second cooling channels. The coolant in the first cooling channel is used for phase change cooling of the object to be cooled, while the coolant in the second cooling channel indirectly cools the object to be cooled by non-phase change cooling of the first cooling channel. Both the first and second cooling channels are provided with inlet and outlet ports to allow the flow of coolant within them. The first heat dissipation mechanism is located inside the first cooling channel and is positioned corresponding to the object to be cooled, while the second heat dissipation mechanism is located inside the second cooling channel and is positioned corresponding to the first cooling channel.

2. The single-phase two-phase hybrid cold plate as described in claim 1, characterized in that, The first heat dissipation mechanism is a heat dissipation layer, which is laid at the bottom of the first cooling channel and has a porous metal structure. The second heat dissipation mechanism is heat dissipation fins, which are evenly arranged at the bottom of the second cooling channel.

3. The single-phase two-phase hybrid cold plate as described in claim 1, characterized in that, Both the first and second heat dissipation mechanisms are heat dissipation layers, which are laid at the bottom of the first or second cooling channel and have a porous metal structure.

4. A single-phase or two-phase hybrid cold plate as described in claim 2 or 3, characterized in that, The porous metal structure is formed by sintering.

5. The single-phase two-phase hybrid cold plate as described in claim 1, characterized in that, Both the first and second heat dissipation mechanisms are heat dissipation fins, which are evenly arranged at the bottom of the first or second cooling channel.

6. The single-phase two-phase hybrid cold plate as described in claim 1, characterized in that, The second cooling channel partially surrounds the outside of the first cooling channel, and the contact surfaces of the first cooling channel and the second cooling channel are each provided with a second heat dissipation mechanism.

7. The single-phase two-phase hybrid cold plate as described in claim 1, characterized in that, The second cooling channel partially surrounds the top and sides of the first cooling channel, and the contact surfaces of the first cooling channel and the second cooling channel are provided with a second heat dissipation mechanism.

8. The single-phase two-phase hybrid cold plate as described in claim 1, characterized in that, The coolant is deionized water, ethylene glycol solution, propylene glycol solution, or fluorinated liquid.

9. The single-phase two-phase hybrid cold plate as described in claim 1, characterized in that, The liquid outlet of the first cooling channel is connected to the liquid outlet of the second cooling channel via a T-joint.

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