CN217546568U - Microchannel liquid cooling cold plate with herringbone turbulent flow channel - Google Patents
Microchannel liquid cooling cold plate with herringbone turbulent flow channel Download PDFInfo
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Abstract
The invention provides a micro-channel liquid cooling cold plate with a herringbone turbulent flow channel, which comprises a metal substrate and a metal cover plate, wherein a groove is formed on the metal substrate through machining, and the groove and the metal cover plate are welded to form the cold plate, so that the sealing property of the whole structure is ensured; the closed space formed by the groove in the metal substrate and the inner surface of the metal cover plate is the microchannel; the microchannel is divided into two parts, and the microchannel is respectively provided with a cooling liquid inlet and a cooling liquid outlet which are independent. The invention overcomes the limitation of the surface temperature rise of the liquid cooling plate of the existing straight micro-channel to the heat exchange efficiency of the cold plate, improves the heat exchange efficiency of the cold plate, reduces the total heat resistance of the cold plate, has a gentle change curve of the total pressure drop along with the flow, has better variable working condition performance of the cold plate, and has the advantages of small volume, compact structure, good heat exchange effect, safe and reliable operation and the like, and the processing technology of the flow channel of the cold plate is easy to realize and can be produced in batches.
Description
Technical Field
The invention relates to the technical field of thermal management of military electronic equipment, in particular to a micro-channel liquid cooling plate.
Background
High power and high integration are important development trends of radio frequency electronic systems such as radars, electronic warfare, communication and the like, and a three-dimensional integrated radio frequency micro-system technology represented by system-in-package (SIP) and system-on-chip (SOC) is a main supporting technology for realizing high power and high integration, is expected to become an effective means for realizing a low-profile phased array antenna, and can realize higher integration and microminiaturization of the phased array antenna. With the gradual application of the three generations of semiconductor materials represented by GaN, the heat dissipation density and difficulty of heat dissipation of the system are increased dramatically, which is embodied in the following three aspects: the heat dissipation problem of high surface heat flow density, high bulk heat flow density and thermal stack has become one of the bottlenecks restricting the development of the radio frequency micro system.
The development of the radio frequency microsystem is mainly in the SIP stage at present, the T/R component of the SIP radio frequency microsystem generally adopts a tile type structure, and a chip of the SIP radio frequency microsystem is in a three-dimensional layout: generally, a high-power chip is arranged at the bottom layer, a low-power chip is arranged at the upper layer, the thermal coupling effect is obvious after a plurality of layers of heat sources are stacked, the bulk heat flow density is larger due to the reduction of the packaging volume, the surface heat flow density of the chip is greatly increased due to the application of the GaN technology, and the heat dissipation of a T/R assembly is more difficult due to the three-dimensional integration. How to realize the heat dissipation of the three-dimensional stack chip with extremely high heat flux density in an extremely small space becomes a main problem faced by the radio frequency micro-system cooling technology, and the cold plate is used as a terminal heat sink of the radio frequency micro-system and plays an important role in the heat management of the chip.
The micro-channel liquid cooling cold plate has the characteristics of compact structure, high heat exchange efficiency, light weight, safe and reliable operation and the like, has more obvious advantages in small areas and under the condition of high heat flow density, and is widely used in microelectronics, aerospace equipment, high-temperature superconductors and other occasions with special requirements on the size and weight of heat exchange equipment. However, the existing flat micro-channel liquid cooling cold plate has the following defects:
1. along with the proceeding of the heat exchange process, the temperature of the cooling liquid inlet is lower, while the temperature of the cooling liquid outlet is higher, so that the rising of the surface temperature of the cold plate can limit the efficiency of the existing straight micro-channel liquid cooling cold plate;
2. most of the existing flat microchannel liquid cooling cold plates adopt a single-inlet and single-outlet structural form, the total length of a flow channel is long, the on-way resistance of cooling liquid is large, the total pressure drop of the cold plates is large, and the required power of a liquid supply pump is large;
in order to strengthen heat transfer, a turbulent flow channel can be added between adjacent main channels to generate 'secondary flow', the flow blockage in the turbulent flow channel and the 'secondary flow' can strengthen the thermal characteristic of the micro channel on the premise of not generating pressure loss, and the heat exchange method is an effective strengthening heat exchange means.
Disclosure of Invention
In order to overcome the defects in the prior art, the invention provides a micro-channel liquid cooling plate with a herringbone turbulent flow channel. The invention aims to meet the specific application requirements of high-integration-level radio frequency micro-system thermal control, and simultaneously provides a micro-channel liquid cooling cold plate with a herringbone turbulent flow channel, which has the advantages of small total pressure drop, good heat exchange performance, compact structure, safe and reliable operation and the like.
The technical scheme adopted by the invention for solving the technical problems is as follows:
a micro-channel liquid cooling cold plate with a herringbone turbulent flow channel comprises a metal base plate and a metal cover plate, wherein a groove is formed in the metal base plate through machining, and the groove and the metal cover plate are welded to form the cold plate, so that the sealing performance of the whole structure is guaranteed; a closed space formed by the groove in the metal substrate and the inner surface of the metal cover plate is a micro-channel; the microchannel is divided into two parts, and the microchannel is respectively provided with a cooling liquid inlet and a cooling liquid outlet which are independent.
The metal cover plate is provided with two cooling liquid inlets and two cooling liquid outlets, and the cooling liquid inlets and the cooling liquid outlets are arranged in a crossed arrangement mode, so that the temperature consistency of the cold plate is improved.
The cross section of the flow channel of the micro-channel is rectangular, and the width W of the flow channel ch And adjacent flow passagesWidth W of the flow channel wall therebetween w All of which are 0.5-1.5 mm, and a series of herringbone turbulent flow channels are formed by 'breaking' the channel walls of the adjacent channels, as shown in figures 3 and 5, and the interval p of the turbulent flow channels f The effective length of the flow passage wall is 10mm divided by the number of the flow passage surrounding each row N, i.e. p f =10/N; the inclination angle theta of the bypass flow channel is 20-45 degrees; width W of turbulent flow channel sc Is W sc ＝W w 2; length l of turbulent flow channel sc Is 1 sc ＝W sc /sinθ。
The invention has the beneficial effects that:
(1) According to the microchannel liquid cooling cold plate with the herringbone turbulent flow channels, the herringbone turbulent flow channels are additionally arranged between the adjacent main channels to form 'secondary flow' flow, so that the limitation of the surface temperature rise of the conventional straight microchannel liquid cooling cold plate on the heat exchange efficiency of the cold plate is overcome, and the heat exchange efficiency of the cold plate is improved;
(2) According to the microchannel liquid cooling cold plate with the herringbone turbulent flow channel, the total heat resistance of the cold plate is reduced due to the reinitialization of the flow boundary layer and the heat boundary layer at the front edge of the inclined herringbone turbulent flow channel and the increase of the effective heat exchange area;
(3) Compared with the traditional straight micro-channel liquid cooling cold plate with a single inlet and a single outlet, the micro-channel liquid cooling cold plate with the herringbone turbulent flow channel provided by the invention has the advantages that the length of the channel is obviously reduced, the on-way resistance loss of the cooling liquid flowing in the micro-channel is reduced, the total pressure drop of the cold plate is greatly reduced, and the power of a liquid supply pump required by the cold plate is obviously reduced. In addition, the change curve of the total pressure drop along with the flow is smooth, and the variable working condition performance of the cold plate is better;
(4) According to the microchannel liquid cooling plate with the herringbone turbulent flow channels, the number, the spacing and the inclination angle of the herringbone turbulent flow channels can be correspondingly optimized and adjusted according to different applied thermal loads, and the microchannel liquid cooling plate has the advantages of small volume, compact structure, good heat exchange effect, safe and reliable operation and the like. In addition, the processing technology of the cold plate runner is easy to realize, can be produced in batches, and has wide application prospect.
Drawings
FIG. 1 is a schematic diagram of a metal substrate in a micro-channel liquid cold plate with a chevron-shaped turbulent flow channel according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of a metal cover plate in a micro-channel liquid cooling plate with chevron-shaped turbulating flow channels according to an embodiment of the present invention;
FIG. 3 is a schematic parameter naming diagram of a micro-channel liquid cooling plate with chevron-shaped turbulating flow channels according to an embodiment of the present invention;
FIG. 4 is a schematic diagram of parameter naming of a conventional flat microchannel liquid cooling plate;
FIG. 5 is a schematic parameter naming diagram of a herringbone turbulent flow channel according to an embodiment of the present invention;
FIG. 6 is a numerical simulation model of a micro-channel liquid cooling plate with chevron-shaped turbulating flow channels according to an embodiment of the present invention;
FIG. 7 is a comparison of total pressure drop of a conventional flat microchannel liquid cold plate and a microchannel liquid cold plate having a chevron-shaped turbulator flow channel according to the present invention;
FIG. 8 is a comparison of the total thermal resistance of a conventional flat micro-channel liquid cold plate and a micro-channel liquid cold plate with chevron-shaped turbulator flow channels according to the present invention;
FIG. 9 is a velocity vector diagram of an intermediate cross-section of a microchannel liquid cold plate with chevron shaped turbulator channels according to an embodiment of the present invention at a coolant flow rate of 159 mL/min.
Wherein, 1-a metal substrate; 2 a-a first microchannel, 2 b-a second microchannel, 3-a metal cover plate, 4 a-a first cooling liquid inlet, 4 b-a second cooling liquid inlet, 5 a-a first cooling liquid outlet and 5 b-a second cooling liquid outlet; 6-solid domain in numerical simulation model; 7a, 7 b-fluid domains in the numerical simulation model.
Detailed Description
The invention is further illustrated with reference to the following figures and examples.
A micro-channel liquid cooling cold plate with a herringbone turbulent flow channel comprises a metal base plate 1 and a metal cover plate 3, wherein a micro groove is formed in the metal base plate 3 through machining, and the groove and the metal cover plate 3 are welded to form a cold plate, so that the sealing performance of the whole structure is guaranteed; a closed space formed by the groove in the metal substrate 3 and the inner surface of the metal cover plate 3 is a micro-channel; the microchannel is divided into two parts, namely a first microchannel 2a and a second microchannel 2b in the figure 1, and the two parts are respectively provided with a cooling liquid inlet and a cooling liquid outlet which are independent from each other.
The metal cover plate 3 is provided with two cooling liquid inlets and two cooling liquid outlets, namely a cooling liquid inlet 4a, a cooling liquid inlet two 4b, a cooling liquid outlet 5a and a cooling liquid outlet two 5b, wherein the cooling liquid inlets 4a and 4b and the cooling liquid outlets 5a and 5b are arranged in a cross arrangement mode, and the temperature consistency of the cold plate is improved.
The cross section of the flow channel of the micro-channel is rectangular, and the width W of the flow channel ch And a width W of a flow channel wall between adjacent flow channels w All of which are 0.5-1.5 mm, a series of herringbone turbulent flow channels are formed by 'breaking' the channel walls of the adjacent channels, as shown in figures 3 and 5, and the distance p between the turbulent flow channels f The effective length of the flow passage wall is 10mm divided by the number of the flow passage surrounding each row N, i.e. p f =10/N; the inclination angle theta of the bypass flow channel is 20-45 degrees; width W of turbulent flow channel sc Is W sc ＝W w 2; length l of turbulent flow channel sc Is 1 sc ＝W sc /sinθ。
As shown in fig. 1 to fig. 2, the embodiment provides a microchannel liquid cooling cold plate with a herringbone turbulent flow channel, which includes a metal substrate 1 and a metal cover plate 3, where the metal substrate 1 is provided with a groove, and the metal substrate 1 with the groove and the metal cover plate 3 are welded to form the liquid cooling cold plate, so as to ensure the sealing performance of the overall structure; a closed space formed by the groove in the metal substrate 1 and the inner surface of the metal cover plate 3 is a microchannel, and the section of the microchannel is rectangular; and a cooling liquid inlet 4a, a cooling liquid inlet 4b, a cooling liquid outlet 5a and a cooling liquid outlet 5b of the liquid cooling plate are arranged on the metal cover plate 3.
The beneficial effects of the invention are verified by comparing the flow and heat exchange processes in the microchannel liquid cooling plate (MCCF) with the herringbone turbulent flow channel with the conventional straight microchannel liquid cooling plate (MCPF) through simulation experiments.
Example (b):
in this embodiment, names of two types of micro-channel liquid cooling plates and herringbone turbulent flow channels are shown in fig. 3, fig. 4 and fig. 5, and specific structural dimensions are shown in table 1 below:
TABLE 1 structural dimensions of microchannel liquid cooling plate and herringbone flow-around channel
The material properties of the microchannel liquid cold plate and the cooling liquid are shown in table 2:
TABLE 2 micro-channel liquid Cold plate and Material Properties of the Cooling liquid
As shown in FIG. 6, in the numerical simulation, the rest surfaces of the cold plate except the bottom surface of the cold plate are set to be heat insulation, and the constant heat flow density is given to the bottom surface of the cold plate and is 40W/cm 2 (ii) a Applying non-slip velocity boundary condition u to solid wall surface s =0, wall temperature is defined as: t is a unit of s ＝T f at wall (ii) a At the interface of the fluid domain 7a in the numerical simulation model, the fluid domain 7b in the numerical simulation model and the solid domain 6 in the numerical simulation model, the heat conduction and convection heat transfer to the fluid are coupled by applying a heat flow continuity condition between the two; inlet given coolant flow rate V of the calculation field in (m/s) and temperature T f，in =20 ℃, given outlet pressure p = p 0 ，p 0 Is the cold plate outlet pressure.
Fig. 7 is a comparison graph of total pressure drop of cooling liquid of the microchannel liquid cooling plate with the herringbone turbulent flow channel and the conventional straight microchannel liquid cooling plate in this embodiment, and for the two forms of microchannel liquid cooling plates, the pressure drop of the inlet and the outlet of the cooling liquid rises along with the increase of the flow rate of the cooling liquid. Because the length of the flow channel of the liquid cooling cold plate of the micro-channel with the herringbone turbulent flow channel is obviously reduced, the on-way resistance loss of the cooling liquid flowing in the micro-channel is reduced, the total pressure drop of the liquid cooling cold plate is greatly reduced, the change curve of the total pressure drop is more gentle, and the variable working condition performance of the cold plate is better.
Fig. 8 is a comparison diagram of the total thermal resistance of the microchannel liquid cooling plate with the herringbone turbulent flow channel and the conventional straight microchannel liquid cooling plate in this embodiment, and for the two types of microchannel liquid cooling plates, as the flow rate of the cooling liquid increases, the total thermal resistance of the cooling plate decreases due to the decrease of the surface temperature of the cooling plate. Due to the reinitialization of the flow boundary layer and the thermal boundary layer at the front edge of the inclined herringbone turbulence flow channel and the increase of the effective heat exchange area of the cold plate, the total thermal resistance of the cold plate can be reduced due to the herringbone turbulence flow channel, and the reduction amplitude is increased along with the increase of the flow of the cooling liquid.
Fig. 9 is a vector diagram of the intermediate section velocity of a liquid cooling cold plate of a micro-channel with a herringbone turbulent flow channel in this embodiment, where the mixture of the main flow and the "secondary flow" existing in the flow channel can be clearly seen, which is beneficial to improving the heat exchange efficiency of the cold plate.
The above description is only an example of the present invention, but the protection scope of the present invention is not limited thereto, and any person skilled in the art can substitute or change the technical solution of the present invention and the inventive concept thereof within the scope of the present invention.
Claims (3)
1. The utility model provides a microchannel liquid cooling cold plate with chevron shape vortex runner, includes metal substrate and metal decking, its characterized in that:
the microchannel liquid cooling cold plate with the herringbone turbulent flow channels is characterized in that grooves are formed on a metal substrate through machining, the grooves and a metal cover plate are welded to form the cold plate, and a closed space formed by the grooves in the metal substrate and the inner surface of the metal cover plate is a microchannel; the microchannel is divided into two parts, and the microchannel is respectively provided with a cooling liquid inlet and a cooling liquid outlet which are independent.
2. The micro-channel liquid cooling plate with chevron shaped turbulator flow channel of claim 1, wherein:
the metal cover plate is provided with two cooling liquid inlets and two cooling liquid outlets, and the cooling liquid inlets and the cooling liquid outlets are arranged in a cross arrangement mode.
3. The micro-channel liquid cooling plate with chevron shaped turbulator flow channel of claim 1, wherein:
the cross section of the flow channel of the micro-channel is rectangular, and the width W of the flow channel ch And a width W of a flow channel wall between adjacent flow channels w All of which are 0.5-1.5 mm, a series of herringbone disturbed flow channels are formed by breaking the channel walls of the adjacent channels, and the distance p between every two disturbed flow channels f The effective length of the flow passage wall is 10mm divided by the number of the flow passage surrounding each row N, i.e. p f =10/N; the inclination angle theta of the bypass flow channel is 20-45 degrees; width W of turbulent flow channel sc Is W sc ＝W w 2; length l of turbulent flow channel sc Is 1 of sc ＝W sc /sinθ。
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