CN119803133B - Modular integrated multi-layer independent parallel driven capillary wick microchannel heat exchanger - Google Patents

Abstract

The invention provides a modularized integrated multi-layer independent parallel driving type capillary core micro-channel heat exchanger, which comprises an upper end cover, a lower end cover, a capillary core and a porous supporting frame. The lower surface of upper end cover is provided with compensation chamber baffle and air collecting chamber baffle, and the compensation chamber baffle slot position that sets up with the lower end cover inner wall corresponds the installation with lower end cover air collecting chamber baffle slot position, divide into compensation chamber, phase transition district and air collecting chamber with the working cavity. The capillary wick and porous support are disposed within the phase change region. The capillary core is tightly connected with the porous supporting frame, and the porous supporting frame plays a supporting role on the capillary core. The capillary core microchannel heat exchanger provided by the invention can adjust the number of layers of the working cavity and the types of the conversion channels according to the thermal control requirements of different heat flow densities, so that the heat dissipation capacity of the heat exchanger is greatly improved, the layered independent liquid supply and gas transmission in space are realized, and the system operation capacity is improved.

Description

Modular integrated multi-layer independent parallel driven capillary wick microchannel heat exchanger

Technical Field

The invention relates to the field of thermal control management of microelectronic devices, and in particular to a modular integrated multi-layer independent parallel driven capillary core microchannel heat exchanger.

Background Art

The microelectronics industry is developing rapidly. The current trend of microelectronics technology is that the feature size of micro-integrated electronic systems and micro-semiconductor systems is constantly decreasing and the integration is continuously increasing. Although the power of each component is very small, the high integration makes the heat flux density increase sharply, which poses a challenge to the reasonable design of thermal control management technology.

Conventional single-layer capillary wick microchannel heat exchangers usually have a compensation chamber and a steam channel, with a capillary wick layer between them. The driving effect of capillary force is used to provide transportation power for the steam generated by the vaporization of the liquid working medium. However, when the high heat flux density interface of the high-power thermal control object is temperature-controlled and heat-dissipated, it is often easy to cause insufficient liquid storage in the compensation chamber and dry burning due to the intense evaporation degree and the limited volume space provided by the single-layer structure for the gas-liquid two-phase working medium. At the same time, the heat exchange area provided for the evaporation of the working medium is very limited, and several common steam channel structures cannot smoothly realize the active transportation and collection of steam. On the contrary, the randomness of the steam transportation path is relatively large, so that the steam cannot be discharged in time, and even steam blockage occurs, which causes a sharp increase in local temperature. Therefore, for the microchannel heat exchanger with a single-layer capillary wick structure, although the mechanical pump drive mode greatly shortens the startup time and greatly improves the operating stability compared to the capillary force self-starting mode, the overall effective utilization rate of the space inside the heat exchanger is low, and the uniformity and stability of the gas-liquid two-phase transport need to be further improved. In addition, when dealing with high heat flux density heat dissipation conditions, the effectiveness of the heat exchanger is seriously problematic.

Conventional multi-layer capillary wick microchannel heat exchangers usually have a capillary wick and a steam channel symmetrically arranged on the upper and lower sides of the interior (two capillary wicks on the inner side and two steam channels on the outer side), and a compensation cavity is set between the two capillary wicks to supply liquid to the capillary wicks adjacent to the upper and lower interfaces. Although this structure helps to enhance the steam working medium's transmission power and improve the effective utilization of space to a certain extent, it is easy for the heat dissipation function of the lower half of the heat exchanger to fail, that is, when the compensation cavity supplies liquid to the capillary wick adjacent to the lower side, the liquid working medium is easy to immerse the entire capillary wick channel on the lower side under the action of gravity, thereby blocking the steam generating hole. At the same time, the liquid working medium will pass through the capillary wick and continue to immerse the steam channel at the bottom, thereby increasing the steam flow resistance, and ultimately resulting in poor heat exchange effect in the lower space of the microchannel heat exchanger.

Therefore, for multi-capillary microchannel heat exchangers, special attention should be paid to the problem of independent liquid supply and gas transmission in the internal structure of the space. At the same time, when multiple layers of compensation cavities are set up, how to achieve active liquid supply in each layer and further solve the problem of uneven liquid distribution are still problems to be solved.

Summary of the invention

In response to the defects of the prior art or the need for improvement, the present invention proposes a modular integrated multi-layer independent parallel-driven capillary wick microchannel heat exchanger, which not only helps to improve the defects of the prior art such as uneven liquid distribution, easy immersion of the capillary wick and steam channels and even steam blockage, and excessive flow resistance generated by the channels, but also is expected to greatly improve the heat dissipation capacity of the heat exchanger.

In order to achieve the above object, the technical solution adopted by the present invention is as follows:

The invention provides a modular integrated multi-layer independent parallel driven capillary core microchannel heat exchanger, comprising an upper end cover, a lower end cover, a capillary core and a porous support frame.

The lower surface of the upper end cover is provided with a compensation cavity baffle and a gas collecting chamber baffle, which are installed correspondingly to the compensation cavity baffle slot and the gas collecting chamber baffle slot of the lower end cover provided on the inner wall of the lower end cover, and the working cavity is divided into a compensation cavity, a phase change zone and a gas collecting chamber. The capillary wick and the porous support frame are arranged in the phase change zone. The capillary wick is tightly connected with the porous support frame, and the porous support frame supports the capillary wick.

Furthermore, the heat exchanger also includes an annular wall surface and a middle partition layer.

The upper surface of the middle partition layer is provided with a middle partition layer gas collecting chamber baffle slot, and the lower surface is provided with a compensation cavity baffle and a gas collecting chamber baffle, which are installed correspondingly to the lower end cover gas collecting chamber baffle slot correspondingly arranged on the upper surface of the lower end cover, dividing the working cavity into a compensation cavity, a phase change zone and a gas collecting chamber.

The inner wall of the annular wall is provided with a compensation cavity baffle slot and a gas collecting chamber baffle slot correspondingly, and is fixed to the middle partition by a connecting piece. The position of the gas collecting chamber baffle slot of the middle partition is consistent with the annular wall gas collecting chamber baffle slot, and is perpendicular to it in direction. When the annular wall and the middle partition are clamped up and down, the annular wall gas collecting chamber baffle slot is combined with the middle partition gas collecting chamber baffle slot to form a complete gas collecting chamber baffle slot.

Furthermore, a plurality of tiny grooves are provided on the lower surface between the compensation cavity baffle and the air collecting chamber baffle of the upper end cover and the middle partition layer, serving as steam grooves, and the capillary core is tightly connected to the steam grooves.

Furthermore, the cross-section of the steam channel is rectangular, triangular, Ω-shaped, semicircular, upper trapezoidal and lower trapezoidal, and the channel size range is within 1mm×1mm.

Preferably, a steam outlet is provided on the surface of the baffle plate of the plenum chamber at a position corresponding to the steam channel, and the cross-sectional shape of the steam outlet is consistent with the cross-sectional shape of the steam channel.

Furthermore, there are gaps between the compensation cavity baffle and the top surface of the bottom cover bottom plate, and between the compensation cavity baffle and the top surface of the middle partition layer, forming a compensation cavity liquid delivery port.

Furthermore, a liquid inlet and a steam outlet are respectively provided on both sides of the lower end cover and the annular wall, and a micro precision flow control valve is fixed at the positions of the liquid inlet and the steam outlet to control the inflow flow of the liquid working medium and adjust the steam output size of the steam outlet according to the evaporation intensity.

Particularly, the upper and lower end covers are made of metal material with high thermal conductivity, and the top of the upper end cover is the heating surface.

Furthermore, the porous support frame is made of metal with low thermal conductivity. The surface of the porous support frame is evenly provided with through holes, and four ends are provided with support legs, and the height of the support legs is used to limit the liquid level of the liquid working medium in the capillary core.

Furthermore, the upper end cover and the lower end cover cooperate with the annular wall to clamp the middle partition layer from top to bottom, that is, to fix the middle partition layer in the vertical direction; by changing the number of annular walls and middle partition layers, a single or multiple parallel working cavities are formed in the internal space of the heat exchanger.

The modular integrated multi-layer independent parallel driven capillary wick microchannel heat exchanger provided by the present invention has the following significant features when applied to a thermal control management system for microelectronic devices with high heat flux density:

1) The layered structure realizes independent liquid supply and gas transmission, which is precisely controllable:

The internal space of the microchannel heat exchanger provided by the present invention is divided into multiple layers of parallel working cavities by the middle partition layer, and a compensation cavity, a phase change zone and a gas collecting chamber are independently arranged in each cavity. Compared with the conventional single-layer capillary core microchannel heat exchanger, the overall space utilization rate is effectively improved, and the multi-layer space utilization inside the microchannel heat exchanger is realized. At the same time, the existing double-layer capillary core heat exchanger is avoided, such as uneven liquid distribution, strong randomness of liquid working medium flow, and easy immersion and even steam blockage of the capillary core and steam channel. Micro precision flow control valves are arranged at each liquid inlet and steam outlet to realize precise control of flow, active independent liquid supply and independent gas transmission.

2) Layered structure improves the heat dissipation capacity of the heat exchanger:

The upper and lower end covers of the microchannel heat exchanger provided by the present invention are both made of metal materials with high thermal conductivity, and the top of the upper end cover is the heating surface. Since the multi-layer working cavity inside the heat exchanger is independently provided with phase change zones, heat is transferred from top to bottom through the metal conductor to each phase change zone, and then transferred to each capillary core by the steam channel of the phase change zone, so that the liquid working medium in each capillary core is heated and phase-changed. Therefore, under the same spatial size, the heat exchange area is greatly increased compared with the conventional single-layer capillary core microchannel heat exchanger, and the heat of the heat source is shared, the evaporation intensity is improved, the steam volume is increased, and the heat dissipation capacity of the heat exchanger is enhanced. At the same time, the gas-liquid transportation is more autonomous, and there is no problem of large randomness of the steam transportation path of the existing double-layer capillary core microchannel heat exchanger, which eliminates the situation where the local temperature rises sharply due to the inability to discharge steam in time and steam blockage. The layered structure further improves the heat dissipation capacity of the heat exchanger.

3) Layered structure improves heat exchanger startup speed:

Since the liquid working fluid in the capillary wicks in each layer of the working cavity undergoes phase change to produce steam, the pressure on the steam side of each gas collecting chamber increases more rapidly than that of a conventional single-layer capillary wick microchannel heat exchanger, and the gas path transportation method is smoother than that of the existing double-layer capillary wick microchannel heat exchanger. Therefore, the conditions for successful system startup are achieved more quickly: the pressure difference on both sides of the evaporation interface is sufficient to overcome the flow resistance of the working fluid in the system.

4) Flexible transformation of layered structure and convenient replacement of efficient and active gas transmission methods:

Microchannel heat exchangers supported by mature experimental data will continue to expand their application effectiveness, and even realize multiple different uses of the same microchannel heat exchanger. By reducing or increasing the number of annular walls and intermediate partitions, the multi-layer parallel working cavity in the microchannel heat exchanger can be flexibly changed from one layer to three layers, easily meeting the interface temperature control and heat dissipation requirements of different levels of heat flux density; by installing upper end covers and intermediate partitions with grooves of different shapes, the efficient active gas transmission method can be conveniently replaced, further improving the operation capacity of the heat exchanger.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG1 is an assembly diagram of a microchannel heat exchanger with three layers of working cavities provided by the present invention;

FIG2 is a three-dimensional view of a microchannel heat exchanger with three layers of working cavities provided by the present invention;

FIG3 is a working principle diagram of a microchannel heat exchanger with three layers of working cavities provided by the present invention;

FIG4 is a three-dimensional view of a microchannel heat exchanger with two layers of working cavities provided by the present invention;

FIG5 is a three-dimensional view of a microchannel heat exchanger having a layer of working cavity provided by the present invention;

FIG6 is a half-section view of a plan view of a working cavity example of a microchannel heat exchanger provided by the present invention;

FIG7 is a three-dimensional right view of the upper end cover of the microchannel heat exchanger provided by the present invention;

FIG8 is a three-dimensional half-section view of the lower end cover of the microchannel heat exchanger provided by the present invention;

FIG9 is a three-dimensional half-section view of the annular wall of the microchannel heat exchanger provided by the present invention;

FIG10 is a three-dimensional half-section view of a partition layer in a microchannel heat exchanger provided by the present invention;

FIG. 11 is a three-dimensional view of a porous support frame of a microchannel heat exchanger provided by the present invention.

Description of reference numerals:

100—upper end cover, 200—lower end cover, 300—annular wall, 400—middle partition, 500—capillary wick, 600—porous support frame, 700—micro precision flow control valve;

001—compensation chamber, 002—phase change zone, 003—gas collecting chamber, 004—liquid inlet, 005—steam outlet, 006—compensation chamber baffle, 007—gas collecting chamber baffle, 008—compensation chamber baffle slot, 009—annular wall gas collecting chamber baffle slot, 010—middle partition gas collecting chamber baffle slot, 011—lower end cover gas collecting chamber baffle slot, 012—steam channel, 013—compensation chamber liquid delivery port, 014—steam outlet, 015—through hole, 016—support foot.

DETAILED DESCRIPTION

In order to make the purpose, technical scheme and advantages of the present invention clearer, the present invention is further described below in conjunction with the accompanying drawings and embodiments. The specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention. In addition, the technical features involved in each embodiment of the present invention described below can be combined with each other as long as they do not conflict with each other.

The present application provides a modular integrated multi-layer independent parallel-driven capillary core microchannel heat exchanger, including an upper end cover, a lower end cover, an annular wall, a middle partition, a capillary core, a porous support frame and a micro-precision flow control valve. The present application is a microchannel heat exchanger with a segmented two-phase cooling loop for high heat flux density interface temperature control and heat dissipation.

Wherein, a liquid inlet and a steam outlet are respectively arranged on both sides of the lower end cover and the annular wall.

The upper end cover and the lower surface of the middle partition are provided with a compensation cavity baffle and a gas collecting chamber baffle, and the top surface of the middle partition is provided with a middle partition gas collecting chamber baffle slot.

The inner wall of the annular wall is provided with a compensation cavity baffle slot and an annular wall gas collecting chamber baffle slot, and the inner wall of the lower end cover is provided with a compensation cavity baffle slot and a lower end cover gas collecting chamber baffle slot.

When the annular wall and the middle partition are clamped up and down, the annular wall gas collecting chamber baffle slot is combined with the middle partition gas collecting chamber baffle slot to form a complete gas collecting chamber baffle slot.

The compensation cavity baffles and air collecting chamber baffles of the upper end cover and the middle partition are placed along the annular wall, the compensation cavity baffle slots and the air collecting chamber baffle slots of the lower end cover respectively, so that the upper end cover and the middle partition are placed on the annular wall or the lower end cover, and the upper end cover and the middle partition are fixed in the horizontal direction. The upper end cover and the lower end cover cooperate with the annular wall to clamp the middle partition, that is, the middle partition is fixed in the vertical direction, and multiple parallel working cavities are formed in the internal space of the heat exchanger.

Each working cavity is divided into a compensation cavity, a phase change zone and a gas collecting chamber by means of an upper end cover, a compensation cavity baffle and a gas collecting chamber baffle arranged in a middle partition.

A plurality of tiny grooves are provided on the lower surface between the upper end cover, the compensation cavity baffle of the middle partition layer and the air collecting chamber baffle, serving as steam channels.

A capillary wick and a porous support frame are placed in each phase change zone, and the capillary wick is tightly connected to the porous support frame. The porous support frame supports the capillary wick and controls the liquid level of the liquid working medium so that it soaks but does not immerse the capillary wick. The capillary wick transfers heat to the internal liquid working medium, causing it to change phase and vaporize, and provides transport motive force for the steam through capillary suction force.

The steam channel is closely connected to the capillary core, and the steam generated by the phase change of the liquid working medium in the capillary core is transported into the gas collecting chamber. The steam working medium in the gas collecting chamber is output to the heat exchanger through the steam outlet and is collected and enters the external cooling device.

Example 1

As shown in Figures 1 and 2, this embodiment provides a microchannel heat exchanger with a three-layer working cavity, including an upper end cover 100, a lower end cover 200, an annular wall 300, a middle partition layer 400, a capillary core 500, a porous support frame 600 and a micro precision flow control valve 700.

Since the structures of the working cavities of each layer of the microchannel heat exchanger with three layers of working cavities provided in this embodiment are similar, only one layer of working cavity is taken as an example for detailed description.

As shown in FIG. 7 to FIG. 10 , fixing bolt holes of equal diameter are provided at corresponding positions on the surfaces of the upper end cover 100 , the annular wall surface 300 and the middle partition layer 400 .

As shown in FIG. 6 , the lower surfaces of the upper end cover 100 and the middle partition layer 400 are both provided with a compensation cavity baffle 006 and a gas collecting chamber baffle 007 .

As shown in Fig. 9, the inner wall of the annular wall 300 is provided with corresponding compensation cavity baffle slots 008 and annular wall gas collecting chamber baffle slots 009. As shown in Fig. 10, the top surface of the middle partition 400 is provided with a middle partition gas collecting chamber baffle slot 010, which is consistent with the annular wall gas collecting chamber baffle slot 009 and perpendicular to it in direction.

As shown in Fig. 6, the bolt holes of the annular wall 300 and the middle partition 400 are aligned up and down, and the annular wall gas chamber baffle slot 009 and the middle partition gas chamber baffle slot 010 are combined into a complete gas chamber baffle slot. The upper end cover 100 compensation cavity baffle 006 and the gas chamber baffle 007 are respectively placed along the compensation cavity baffle slot 008 of the annular wall and the annular wall gas chamber baffle slot 009, until the gas chamber baffle 007 reaches the middle partition to form the gas chamber baffle slot 010, thereby fixing the upper end cover on the annular wall to form a working cavity, and fixing the middle partition in the horizontal direction.

As shown in FIG3 , similarly, the upper annular wall, the middle partition layer and the lower end cover are combined, and the fixing bolts are installed to form a microchannel heat exchanger with three layers of working cavities. The compensation cavity baffle 006 and the gas collecting chamber baffle 007 of the upper end cover 100 and the middle partition layer 400 divide the working cavities of each layer into a compensation cavity 001, a phase change zone 002 and a gas collecting chamber 003.

As shown in Figures 7 and 10, a plurality of tiny grooves are provided on the lower surface between the compensation cavity baffle 006 and the gas collecting chamber baffle 007 of the upper end cover 100 and the middle partition 400, as steam channels 012. Capillary wicks 500 and porous support frames 600 are placed in each phase change zone 002 of the microchannel heat exchanger, and the capillary wicks are tightly connected to the steam channels and the porous support frames. The porous support frame supports the capillary wicks and controls the liquid level of the liquid working medium so that it wets but does not immerse the capillary wicks. The capillary wick transfers heat to the internal liquid working medium, causing it to change phase and vaporize, and provides transport motive force for the steam through capillary suction force.

Furthermore, the steam channel 012 is composed of a plurality of parallel micro channels, with cross sections of rectangular, triangular, Ω-shaped, semicircular, upper trapezoidal and lower trapezoidal shapes, and the basic size of the channel is within 1 mm×1 mm, and is used to transport the steam generated by the phase change of the liquid working medium in the capillary wick into the gas collecting chamber 003. The steam working medium in the gas collecting chamber is output from the heat exchanger through the steam outlet 005 and is collected and enters the external cooling device.

Furthermore, a steam vent 014 is provided on the surface of the air collecting chamber baffle 007 at a position corresponding to the steam channel 012, and the steam in the steam channel enters the air collecting chamber 003 through the steam vent 014, and the cross-sectional shape of the steam vent is consistent with the cross-sectional shape of the steam channel.

Furthermore, there are gaps between the compensation cavity baffle 006 and the top surface of the middle partition layer 400 and the top surface of the bottom plate of the lower end cover 200, forming a compensation cavity liquid delivery port 013 for the liquid working medium in each compensation cavity 001 to enter the respective phase change zone 002.

Furthermore, the capillary core 500 is formed by sintering metal powder.

As shown in FIG11 , the porous support frame 600 is made of metal with low thermal conductivity, and has through holes 015 with slightly larger apertures evenly arranged on the surface, and the shape of the through holes is rectangular or circular. The four ends of the porous support frame are provided with legs 016, and the height of the legs is used to limit the liquid level of the liquid working medium in the capillary core, so that the liquid infiltrates but does not immerse the capillary core. The porous support frame is used to support the capillary core and evenly divert the liquid working medium through the through holes 015 into the capillary core.

Furthermore, the micro precision flow control valve 700 is fixed at the position of the liquid inlet 004 and the steam outlet 005, so as to independently control the inflow flow of the liquid working medium and adjust the gas output size of the steam outlet according to the evaporation intensity. The micro precision flow control valve is connected to external equipment such as a cooling device and a pump through a hose to reduce vibration and facilitate spatial three-dimensional layout.

Example 2

The structure of the microchannel heat exchanger with two layers of working cavities provided in this embodiment is substantially the same as that described in Embodiment 1, except that:

As shown in Figure 4, compared with the microchannel heat exchanger with three layers of working cavities provided in Example 1, this embodiment reduces an annular wall, an intermediate partition layer, a capillary core and a porous support frame. That is, after forming a layer of working cavity as shown in Figure 6, it is directly matched with the lower end cover to form only two layers of working cavities. The liquid working medium is divided into two paths before entering the microchannel heat exchanger, entering the upper and lower working cavities respectively, absorbing heat and changing phases to produce steam, which is output from the gas collecting chamber and then collected. By reducing the number of annular walls and intermediate partition layers, the transformation of parallel working cavities from three layers to two layers in the microchannel heat exchanger can be achieved to meet the interface temperature control and heat dissipation requirements with relatively small heat flux density.

Example 3

The structure of the microchannel heat exchanger with a layer of working cavity provided in this embodiment is substantially the same as that described in Embodiment 1, except that:

As shown in Figure 5, compared with the microchannel heat exchanger with three layers of working cavities provided in Example 1, this embodiment does not have an annular wall and an intermediate partition, and the number of internal capillary wicks and porous support frames is correspondingly reduced, so that only one layer of working cavity is formed. Before entering the microchannel heat exchanger, the liquid working fluid is no longer divided into multiple paths but directly enters the working cavity, absorbs heat and changes phase to produce steam, and outputs from the gas collecting chamber. Without the provision of annular walls and intermediate partitions, the transformation of multiple layers of parallel working cavities in the microchannel heat exchanger from three layers to one layer can be achieved to meet the interface temperature control and heat dissipation requirements with relatively smaller heat flux density.

As shown in FIG1 , the assembly process of a modular integrated multi-layer independent parallel-driven capillary wick microchannel heat exchanger provided in the present application is as follows:

First, a porous support frame 600 is placed in the phase change region 002 of the lower end cover 200, and then the capillary core 500 is laid on the porous support frame.

Next, the compensation cavity baffle 006 and the gas collecting chamber baffle 007 of the middle partition 400 are aligned with the compensation cavity baffle slot 008 of the lower end cover and the gas collecting chamber baffle slot 011 of the lower end cover respectively. At this time, the compensation cavity baffle 006 and the gas collecting chamber baffle 007 fix the porous support frame 600 and the capillary wick 500 in the horizontal direction, while the steam channel 012 of the middle partition 400 acts on the capillary wick 500 and is tightly connected thereto, fixing the porous support frame 600 and the capillary wick 500 in the vertical direction.

Afterwards, an annular wall surface 300 is placed through the bolt holes to align with the assembled middle partition layer 400 and the lower end cover 200 .

Then, similar to the previous assembly process, another porous support frame 600 and a capillary core 500 are placed in the phase change region 002 of the second working cavity, and another intermediate spacer 400 and annular wall 300 are installed to form a third working cavity. Then, a porous support frame 600 and a capillary core 500 are placed in the phase change region 002 of the third working cavity, and then the upper end cover 100 is matched.

Finally, the microchannel heat exchanger is fixed and clamped by bolts, and the micro precision flow control valve 700 is installed at each liquid inlet 004 and steam outlet 005 to complete the assembly.

If a microchannel heat exchanger with two layers of working cavities is to be realized, the upper end cover 100 can be directly matched after the second layer of working cavities is completed and the porous support frame 600 and the capillary core 500 are placed. Similarly, if a microchannel heat exchanger with one layer of working cavities is to be realized, the upper end cover 100 can be directly matched after the porous support frame and the capillary core are placed in the phase change zone 002 of the lower end cover.

The following is a detailed description of the working process of a modular integrated multi-layer independent parallel driven capillary wick microchannel heat exchanger provided by the present application:

As shown in FIG. 3 , the micro precision flow control valve 700 is adjusted to a suitable flow position so that the liquid medium flows from each liquid inlet 004 into the compensation cavity 001 of each layer of the working cavity and is evenly settled in the compensation cavity.

Then the liquid working medium enters each phase change zone 002 through each compensation cavity liquid delivery port 013, accumulates in the phase change zone, causes the liquid level to rise, covers the porous support frame 600 placed in the phase change zone 002, and infiltrates the capillary core 500 placed on the porous support frame 600.

The top of the upper cover 100 of the microchannel heat exchanger is a heating surface, which is in direct contact with the heat load surface during operation and absorbs heat through heat conduction. The heat is quickly transferred to the capillary wick 500 in the working cavity of this layer through the fins of the steam channel 012 of the upper cover 100, causing the liquid working medium in the capillary wick to be heated and vaporized.

Due to the heat conduction phenomenon of the side wall of the heat exchanger, the heat is transferred from top to bottom through the steam channels 012 of each intermediate partition layer 400 to the capillary cores 500 in the working cavities of each layer below, causing the liquid working medium in the capillary core to be heated and vaporized.

The steam formed in each layer of the phase change zone 002 is transported through the steam channel 012 and enters the respective gas collecting chamber 003 through the steam port 014. The steam working medium in each gas collecting chamber 003 is output from the heat exchanger through the respective steam outlet 005, and is collected and enters the external cooling device, where it releases sensible heat and latent heat and condenses into a supercooled liquid working medium, which then flows back into the microchannel heat exchanger to complete the cycle.

It can be seen from the above that the modular integrated multi-layer independent parallel-driven capillary wick microchannel heat exchanger provided by the present application overcomes the shortcomings of the existing double-layer capillary wick heat exchanger and improves the working performance.

It will be easily understood by those skilled in the art that the above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims (8)

1. A modular integrated multi-layer independent parallel driven capillary core microchannel heat exchanger, characterized in that it includes an upper end cover, a lower end cover, a capillary core and a porous support frame; The lower surface of the upper end cover is provided with a compensation cavity baffle and a gas collecting chamber baffle, which are installed corresponding to the compensation cavity baffle slots and the gas collecting chamber baffle slots provided on the inner wall of the lower end cover, and the working cavity is divided into a compensation cavity, a phase change zone and a gas collecting chamber; The capillary core and the porous support frame are arranged in the phase change region; The capillary wick is tightly connected to the porous support frame, and the porous support frame supports the capillary wick; It also includes an annular wall and a middle partition; The upper surface of the middle partition is provided with a middle partition gas collecting chamber baffle slot, and the lower surface is provided with a compensation cavity baffle and a gas collecting chamber baffle, which are installed correspondingly to the lower end cover gas collecting chamber baffle slot correspondingly provided on the upper surface of the lower end cover, dividing the working cavity into a compensation cavity, a phase change zone and a gas collecting chamber; The inner wall of the annular wall surface is correspondingly provided with a compensation cavity baffle slot and a gas collecting chamber baffle slot, which are fixed to the middle partition layer by a connecting piece; The position of the middle interlayer gas collecting chamber baffle slot is consistent with the annular wall gas collecting chamber baffle slot and is perpendicular to it in direction; When the annular wall and the middle partition are clamped up and down, the annular wall gas collecting chamber baffle slot is combined with the middle partition gas collecting chamber baffle slot to form a complete gas collecting chamber baffle slot; The upper end cover and the lower end cover cooperate with the annular wall surface to clamp the middle partition layer in the vertical direction; by changing the number of the annular wall surface and the middle partition layer, a single or multiple parallel working cavities are formed in the internal space of the heat exchanger; The lower end cover and the two sides of the annular wall are respectively provided with a liquid inlet and a steam outlet. 2. According to the modular integrated multi-layer independent parallel driven capillary wick microchannel heat exchanger described in claim 1, it is characterized in that the lower surface between the upper end cover and the compensation cavity baffle and the air collecting chamber baffle of the middle partition layer is provided with a plurality of tiny grooves as steam channels, and the capillary wick is tightly connected to the steam channel. 3. The modular integrated multi-layer independent parallel-driven capillary wick microchannel heat exchanger according to claim 2 is characterized in that the cross-section of the steam channel is rectangular, triangular, Ω-shaped, semicircular, upper trapezoidal and lower trapezoidal, and the channel size range is within 1mm×1mm. 4. The modular integrated multi-layer independent parallel-driven capillary wick microchannel heat exchanger according to claim 2 or 3 is characterized in that a steam outlet is opened on the surface of the baffle plate of the gas collecting chamber at a position corresponding to the steam channel, and the cross-sectional shape of the steam outlet is consistent with the cross-sectional shape of the steam channel. 5. The modular integrated multi-layer independent parallel-driven capillary core microchannel heat exchanger according to claim 1 is characterized in that there are gaps between the compensation chamber baffle and the top surface of the lower end cover bottom plate, and between the compensation chamber baffle and the top surface of the middle partition layer, forming a compensation chamber liquid delivery port. 6. According to the modular integrated multi-layer independent parallel driven capillary core microchannel heat exchanger according to claim 1, it is characterized in that a micro precision flow control valve is fixed at the liquid inlet and steam outlet positions to control the inflow flow of the liquid working medium and adjust the gas output size of the steam outlet according to the evaporation intensity. 7. The modular integrated multi-layer independent parallel driven capillary wick microchannel heat exchanger according to claim 1 is characterized in that the upper end cover and the lower end cover are both made of high thermal conductivity metal material, and the top of the upper end cover is the heating surface. 8. The modular integrated multi-layer independent parallel-driven capillary wick microchannel heat exchanger according to claim 1 is characterized in that the porous support frame is made of metal with low thermal conductivity; the surface of the porous support frame is evenly provided with through holes, and four ends are provided with supporting feet, and the liquid level of the liquid working medium in the capillary wick is limited by the height of the supporting feet.