A multi-layered cross-shrinking channel phase change cold plate and its control method

Abstract

This invention relates to the field of laser cooling technology, specifically to a multi-layered cross-shrinking channel phase change cold plate and its control method. The multi-layered cross-shrinking channel phase change cold plate includes a first thermally conductive layer, a second thermally conductive layer, a first flow channel, a second flow channel, and a thermally conductive separator. The first and second thermally conductive layers are spaced apart along a first arrangement direction. The first flow channel extends along the surface of the first thermally conductive layer, and the cross-sectional area of ​​the first flow channel gradually decreases along the first flow direction. The second flow channel extends along the surface of the second thermally conductive layer, and the cross-sectional area of ​​the second flow channel gradually decreases along a second flow direction. The first and second flow directions are opposite. This invention can solve the problems of efficient double-sided heat dissipation, flow stability, and temperature uniformity in the thermal management of high-power lasers.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of laser cooling, in particular to a multi-layer cross tapered channel phase change cold plate and a control method. BACKGROUND

[0002] In the field of laser technology, as the output power of the laser continues to increase, the heat dissipation density of the core device (such as the pump source and the gain medium) increases significantly, and efficient heat management becomes the key to ensuring the stability and service life of the laser. The core device of the laser includes the pump source surface and the fiber disc surface, which requires double-sided heat dissipation to quickly dissipate the large amount of heat generated on both sides and avoid local high temperature causing device performance degradation or damage.

[0003] The current mainstream laser cooling scheme mostly uses a traditional water-cooled cold plate. Such a cold plate generally has a single-layer flow channel, a fixed flow cross-sectional area design structure, and is designed only for single-sided cooling scenarios, which cannot simultaneously meet the efficient heat dissipation requirements of the double sides of the device. At the same time, for high-power lasers, the traditional water-cooled cold plate relies on the sensible heat exchange of single-phase fluid, and the heat exchange efficiency is limited, making it difficult to match the heat dissipation requirements of high-power devices. In addition, the core components of the laser pump source have strict requirements on temperature uniformity, and the temperature of the fluid in the flow channel of the traditional cold plate has a clear temperature gradient along the flow direction, which easily leads to uneven temperature distribution on the surface of the device, thereby affecting the output beam quality and stability of the laser.

[0004] To solve the problems of high-power heat dissipation and temperature uniformity, micro-channel phase change cold plates have become a promising solution due to their high latent heat exchange efficiency during the phase change process. However, existing micro-channel phase change cold plates still face technical bottlenecks in application: the phase change working fluid in the micro-channel is prone to flow instability due to uneven heat flux distribution and other factors, and the working fluid in the tail of the flow channel is prone to dry-out, resulting in a sharp drop in heat exchange performance. Therefore, the comprehensive requirements of double-sided efficient heat dissipation, flow stability, and temperature uniformity have become a technical problem that needs to be solved in the heat management of high-power lasers. SUMMARY

[0005] To solve the problems of double-sided efficient heat dissipation, flow stability, and temperature uniformity in the heat management of high-power lasers, the present application provides a multi-layer cross tapered channel phase change cold plate and a control method.

[0006] In a first aspect, the present application provides a multi-layer cross tapered channel phase change cold plate, comprising:

[0007] a first heat-conducting layer;

[0008] a second heat-conducting layer, the first heat-conducting layer and the second heat-conducting layer being arranged along a first arrangement direction;

[0009] a first flow channel extending along a surface of the first thermally conductive layer; the phase change working medium in the first flow channel flows in a first flow direction; a cross-sectional area of the first flow channel gradually decreases along the first flow direction;

[0010] a second flow channel extending along a surface of the second thermally conductive layer; the phase change working medium in the second flow channel flows in a second flow direction; a cross-sectional area of the second flow channel gradually decreases along the second flow direction; the first flow direction and the second flow direction are opposite; the first flow channel and the second flow channel are oppositely arranged along the first arrangement direction;

[0011] a thermally conductive partition layer; the thermally conductive partition layer is located between the first flow channel and the second flow channel.

[0012] In some embodiments, the multi-layer cross-tapered channel phase change cold plate further comprises:

[0013] a third flow channel extending along a surface of the first thermally conductive layer; the phase change working medium in the third flow channel flows in the second flow direction; a cross-sectional area of the third flow channel gradually decreases along the second flow direction;

[0014] a fourth flow channel extending along a surface of the second thermally conductive layer; the phase change working medium in the fourth flow channel flows in the first flow direction; a cross-sectional area of the fourth flow channel gradually decreases along the first flow direction; the third flow channel and the fourth flow channel are oppositely arranged along the first arrangement direction.

[0015] In some embodiments, the first flow channel, the second flow channel, the third flow channel and the fourth flow channel are arranged in multiple along a second arrangement direction; the second arrangement direction is perpendicular to the first arrangement direction; the first flow channel and the third flow channel are staggered arranged along the second arrangement direction; the second flow channel and the fourth flow channel are staggered arranged along the second arrangement direction.

[0016] In some embodiments, the multi-layer cross-tapered channel phase change cold plate further comprises:

[0017] a first return channel connecting an outlet of the first flow channel and an inlet of the second flow channel;

[0018] a second return channel connecting an outlet of the third flow channel and an inlet of the fourth flow channel.

[0019] In some embodiments, a cross-sectional area of the second flow channel is adjustable; a cross-sectional area of the fourth flow channel is adjustable.

[0020] In some embodiments, the thermally conductive partition layer comprises:

[0021] a first flow channel extending along a surface of the first partition layer; the first flow channel is located between the first thermally conductive layer and the first partition layer;

[0022] a second flow channel extending along a surface of the second partition layer; the second flow channel is located between the second thermally conductive layer and the second partition layer;

[0023] a compensation flow channel located between the first partition layer and the second partition layer; a phase change working medium in the compensation flow channel flows in the first flow direction or the second flow direction.

[0024] In some embodiments, the first flow channel is provided with a plurality of first prongs arranged at intervals on an inner wall of the first thermally conductive layer; the arrangement density of the first prongs gradually increases along the first flow direction;

[0025] the second flow channel is provided with a plurality of second prongs arranged at intervals on an inner wall of the second thermally conductive layer; the arrangement density of the first prongs gradually increases along the second flow direction.

[0026] In the second aspect, the present application provides a multi-layer cross tapered channel phase change cold plate control method, which is applied to the multi-layer cross tapered channel phase change cold plate in any one of the embodiments of the first aspect, and the multi-layer cross tapered channel phase change cold plate control method comprises the following steps:

[0027] real-time acquisition of a first target heat dissipation power of the first thermally conductive layer and a second target heat dissipation power of the second thermally conductive layer;

[0028] when the first target heat dissipation power and the second target heat dissipation power are both greater than a first threshold value, a first cooling strategy is executed; the first cooling strategy comprises introducing a first phase change working medium flowing in a first flow direction into the first flow channel and introducing a second phase change working medium flowing in a second flow direction into the second flow channel;

[0029] adjustment of a first fluid parameter of the first phase change working medium according to the first target heat dissipation power; the first fluid parameter comprises a first flow rate;

[0030] adjustment of a second fluid parameter of the second phase change working medium according to the second target heat dissipation power; the second fluid parameter comprises a second flow rate.

[0031] In some embodiments, the multi-layer cross tapered channel phase change cold plate further comprises a first return channel, which communicates an outlet of the first flow channel and an inlet of the second flow channel;

[0032] the first cooling strategy further comprises closing the first return channel;

[0033] The multi-layer cross-tapered channel phase change cold plate control method further includes:

[0034] When the second target heat dissipation power is less than the first threshold value, and the first target heat dissipation power is greater than the second target heat dissipation power, a second cooling strategy is executed; the second cooling strategy includes introducing third phase change working medium flowing in the first flow direction into the first flow channel and opening the first return channel;

[0035] A third flow parameter of the third phase change working medium is adjusted according to the first target heat dissipation power and the second target heat dissipation power; the third flow parameter includes a third flow rate.

[0036] In some embodiments, a channel cross-sectional area of the second flow channel is adjustable;

[0037] The second cooling strategy further includes:

[0038] A first difference value of the first target heat dissipation power and the second target heat dissipation power is obtained;

[0039] When the first difference value is greater than a second threshold value, a reduction ratio of the channel cross-sectional area of the second flow channel is regulated according to the second target heat dissipation power; the reduction ratio is less than 1.

[0040] In some embodiments, the heat-conductive partition layer includes:

[0041] A first partition layer, the first flow channel extending along a surface of the first partition layer; the first flow channel being located between the first heat-conductive layer and the first partition layer;

[0042] A second partition layer, the second flow channel extending along a surface of the second partition layer; the second flow channel being located between the second heat-conductive layer and the second partition layer;

[0043] A compensation flow channel, the compensation flow channel being located between the first partition layer and the second partition layer; phase change working medium in the compensation flow channel flowing in the first flow direction or the second flow direction;

[0044] The first cooling strategy further includes:

[0045] When the first target heat dissipation power is greater than the second target heat dissipation power, fourth phase change working medium flowing in the second flow direction is introduced into the compensation flow channel;

[0046] When the second target heat dissipation power is greater than the first target heat dissipation power, fifth phase change working medium flowing in the first flow direction is introduced into the compensation flow channel.

[0047] To solve the problems of double-sided high-efficiency heat dissipation, flow stability and temperature uniformity in high-power laser thermal management, the present application has the following advantages:

[0048] 1. The double-layer flow channel formed by the first flow channel and the second flow channel is used to dissipate heat from the first heat conduction layer and the second heat conduction layer, the first flow channel and the second flow channel are arranged in a structure in which the cross-sectional area gradually decreases, so as to accelerate the fluid velocity at the end of the fluid, break through the large bubbles at the tail of the flow channel, and relieve the instability of two-phase flow. Since the first flow direction is opposite to the second flow direction, the first flow channel and the second flow channel are arranged in a counter-flow manner, so as to suppress the local dryout phenomenon at the tail of the flow channel of each other, reduce the dryness of the cooling medium after boiling in the first flow channel and the second flow channel, and improve the flow stability. In addition, the shapes of the first flow channel and the second flow channel are complementary, so that the shape of the cold plate is relatively regular. Thus, the demand for double-sided high-efficiency heat dissipation of a high-power laser is met.

[0049] 2. The first return channel is arranged, when the heat dissipation demand of the second heat conduction layer is small, the first return channel is opened, so that the phase change working medium of the first flow channel flows into the second flow channel to realize the return. After the phase change working medium of the first flow channel cools the first heat conduction layer, it continues to flow into the second flow channel to cool the second heat conduction layer. During the flow process, the heat exchange effect is different due to the change of the phase fraction of the cooling medium, and the different heat dissipation demands of the first heat conduction layer and the second heat conduction layer are automatically matched. The first flow channel and the second flow channel transfer heat, and the cold energy of the first flow channel and the cold energy of the second flow channel are complementary at the same cross section along the flow direction, which can suppress the local dryout phenomenon of the second flow channel, guarantee the uniformity of the first flow channel and the second flow channel, and improve the energy utilization rate. BRIEF DESCRIPTION OF DRAWINGS

[0050] Figure 1 A cross-sectional view of the front view angle of the multi-layer cross tapered channel phase change cold plate of embodiment one is shown;

[0051] Figure 2 A cross-sectional view of the right view angle of the multi-layer cross tapered channel phase change cold plate in Figure 1 is shown;

[0052] Figure 3 A cross-sectional view of the front view angle of the multi-layer cross tapered channel phase change cold plate of embodiment two is shown;

[0053] Figure 4 A cross-sectional view of the right view angle of the multi-layer cross tapered channel phase change cold plate in Figure 3 is shown;

[0054] Figure 5 A cross-sectional view of the front view angle of the multi-layer cross tapered channel phase change cold plate of embodiment three is shown;

[0055] Figure 6 A cross-sectional view of another cutting position of the front view angle of the multi-layer cross tapered channel phase change cold plate of embodiment three is shown;

[0056] Figure 7 FIG. 4 shows a cross-sectional view of a front view perspective of a multi-layer cross tapered channel phase change cold plate of embodiment four;

[0057] Figure 8 FIG. 5 shows a cross-sectional view of a front view perspective of a multi-layer cross tapered channel phase change cold plate of embodiment five;

[0058] Figure 9 FIG. 6 shows a flowchart of a multi-layer cross tapered channel phase change cold plate control method of embodiment six.

[0059] REFERENCE NUMERALS:

[0060] 10, first thermally conductive layer; 20, second thermally conductive layer; 30, first flow channel; 31, first side plate; 32, first prong; 40, second flow channel; 41, second side plate; 42, second prong; 50, thermally conductive spacer; 51, first spacer; 52, second spacer; 53, compensation flow channel; 60, third flow channel; 70, fourth flow channel; 80, first return channel; 90, second return channel. DETAILED DESCRIPTION

[0061] The present disclosure will now be discussed with respect to several exemplary embodiments. It should be understood that the embodiments are discussed merely to provide a more precise description of the present disclosure and, as such, are not intended to pose any limitations on the scope of the present disclosure.

[0062] As used herein, the terms "includes," "including," "has," "having," "contains," "containing," "comprises," "comprising," "may" and "including," are open-ended terms that are intended to mean "includes but not limited to." The term "based on" is intended to mean "based, at least in part, on." The terms "one embodiment" and "an embodiment" are intended to mean "at least one embodiment." The term "another embodiment" is intended to mean "at least one other embodiment." The terms "upper," "lower," "left," "right," "front," "back," "top," "bottom," "inner," "outer," "vertical," "horizontal," "lateral," "longitudinal," and the like, shall mean the orientation or position as shown in the drawings. These terms are used primarily just to better describe the application and its embodiments, and are not used to limit the indicated device, element or component must have a particular orientation, or be constructed and operated in a particular orientation. Also, some of the above terms can be used to mean other meanings, for example, the term "upper" can also mean "top" in some instances. The specific meanings of these terms in the application can be understood by those skilled in the art based on the specific context in which the terms are used. In addition, the terms "mount," "provide," "have," "connect," "couple," and "engage" are to be construed broadly. For example, it can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection, or an electrical connection; it can be a direct connection, or an indirect connection through an intermediate medium; or it can be an internal connection between two devices, elements or components. The specific meanings of these terms in the application can be understood by those skilled in the art based on the specific context in which the terms are used. In addition, the terms "first," "second," and the like are primarily used to distinguish different devices, elements or components (the specific types and structures of which can be the same or different), and are not intended to indicate or imply the relative importance and quantity of the indicated devices, elements or components. Unless otherwise stated, the meaning of "multiple" is two or more.

[0063] To solve the problems of double-sided high-efficiency heat dissipation, flow stability and uniformity in high-power laser thermal management, the application provides a multi-layer cross tapered channel phase change cold plate and a control method.

[0064] Embodiment one:

[0065] As Figure 1As shown, the embodiment provides a multi-layer cross tapered channel phase change cold plate, including a first heat conduction layer 10, a second heat conduction layer 20, a first flow channel 30, a second flow channel 40 and a heat conduction partition layer 50. The first heat conduction layer 10 and the second heat conduction layer 20 are arranged along a first arrangement direction. The first heat conduction layer 10 and the second heat conduction layer 20 are both heat conduction plates, and the first heat conduction layer 10 and the second heat conduction layer 20 are parallel. In the application of high-power laser, the first heat conduction layer 10 cools the pump source surface, and the second heat conduction layer 20 cools the fiber disc surface. Generally, the heat dissipation requirement of the pump source surface is higher, and the heat dissipation requirement of the fiber disc surface is lower.

[0066] As shown, Figure 1 The first flow channel 30 extends along the surface of the first heat conduction layer 10, and the phase change working medium in the first flow channel 30 can be in contact with the first heat conduction layer 10 to cool the first heat conduction layer 10. The phase change working medium in the first flow channel 30 flows along a first flow direction, that is, the first flow direction is parallel to the surface of the first heat conduction layer 10. The cross-sectional area of the first flow channel 30 gradually decreases along the first flow direction, so that the bubbles at the end of the first flow channel 30 collide and break each other, the particle size of the broken bubbles is smaller, the specific surface area is larger, and the liquid cooling medium is more fully in contact with the flow channel wall, thereby relieving the gas film barrier formed by the bubble adhering to the wall, improving the contact heat exchange between the phase change working medium and the first heat conduction layer 10, and strengthening the latent heat exchange.

[0067] As shown, Figure 1 The second flow channel 40 extends along the surface of the second heat conduction layer 20, and the phase change working medium in the second flow channel 40 can be in contact with the second heat conduction layer 20 to cool the second heat conduction layer 20. The phase change working medium in the second flow channel 40 flows along a second flow direction, that is, the second flow direction is parallel to the surface of the second heat conduction layer 20. The cross-sectional area of the second flow channel 40 gradually decreases along the second flow direction, so that the bubbles at the end of the second flow channel 40 collide and break each other, the particle size of the broken bubbles is smaller, the specific surface area is larger, and the liquid cooling medium is more fully in contact with the flow channel wall, thereby relieving the gas film barrier formed by the bubble adhering to the wall, improving the contact heat exchange between the phase change working medium and the first heat conduction layer 10, and strengthening the latent heat exchange. The first flow direction and the second flow direction are opposite, and the first flow channel 30 and the second flow channel 40 are arranged opposite along the first arrangement direction. The first flow direction and the second flow direction are both perpendicular to the first arrangement direction.

[0068] As shown, Figure 1As shown, the heat-conducting partition 50 is located between the first flow channel 30 and the second flow channel 40, and heat can be transferred between the first flow channel 30 and the second flow channel 40 through the heat-conducting partition 50. The inlet of the first flow channel 30 can absorb part of the heat at the end of the second flow channel 40, and the inlet of the second flow channel 40 can exchange heat with the end of the first flow channel 30, so that the first flow channel 30 and the second flow channel 40 are designed to flow in opposite directions, which can effectively prevent the phenomenon of local dryout of the cooling medium at the end of the flow channel, reduce the dryness of the cooling medium after boiling, and improve the flow stability of the first flow channel 30 and the second flow channel 40.

[0069] The first flow channel 30 and the second flow channel 40 formed by the first flow channel 30 and the second flow channel 40 can effectively dissipate heat from the first heat-conducting layer 10 and the second heat-conducting layer 20. The first flow channel 30 and the second flow channel 40 are arranged in a structure in which the cross-sectional area gradually decreases, which accelerates the fluid velocity at the end of the fluid, breaks through the large bubbles at the end of the flow channel, and relieves the instability of two-phase flow. Since the first flow direction is opposite to the second flow direction, the first flow channel 30 and the second flow channel 40 are arranged in a counter-flow arrangement, so that the first flow channel 30 and the second flow channel 40 can effectively prevent the local dryout phenomenon at the end of the flow channel, reduce the dryness of the cooling medium after boiling, and improve the flow stability. In addition, the shapes of the first flow channel 30 and the second flow channel 40 are complementary, so that the shape of the cold plate is relatively regular. Thus, the problems of double-sided efficient heat dissipation, flow stability and uniformity in the thermal management of high-power lasers are solved.

[0070] As shown in FIG. 1, Figure 2 In some embodiments, the first flow channel 30 is arranged in multiple along the second arrangement direction, the second flow channel 40 is arranged in multiple along the second arrangement direction, and the first flow channel 30 and the second flow channel 40 correspond one-to-one. Each corresponding first flow channel 30 and second flow channel 40 are arranged along the first arrangement direction. The first arrangement direction is perpendicular to the second arrangement direction. The second arrangement direction is perpendicular to the first flow direction.

[0071] As shown in FIG. 1, Figure 2As shown, in some embodiments, the first flow channel 30 includes two first side plates 31, which are fixed between the first heat-conducting layer 10 and the heat-conducting insulating layer 50. The two first side plates 31 between adjacent first flow channels 30 are integrally formed. The first side plates 31 can also be integrally formed with the heat-conducting insulating layer 50 to improve structural strength. The surface of the heat-conducting insulating layer near the first flow channel 30 is inclined, thereby achieving a uniform change in the cross-sectional area of ​​the first flow channel 30. The second flow channel 40 includes two second side plates 41, which are fixed between the second heat-conducting layer 20 and the heat-conducting insulating layer 50. The two second side plates 41 between adjacent second flow channels 40 are integrally formed. The second side plates 41 can also be integrally formed with the heat-conducting insulating layer 50. The surface of the heat-conducting insulating layer near the second flow channel 40 is inclined, thereby achieving a uniform change in the cross-sectional area of ​​the first flow channel 30.

[0072] Example 2:

[0073] like Figure 3 As shown, the difference between Embodiment 2 and Embodiment 1 is that the multi-layer cross-shrinking channel phase change cold plate further includes a third flow channel 60. The third flow channel 60 extends along the surface of the first heat-conducting layer 10, meaning that the phase change working medium in the third flow channel 60 cools the first heat-conducting layer 10. The phase change working medium in the third flow channel 60 flows along the second flow direction, so the flow direction of the phase change working medium in the third flow channel 60 and the first flow channel 30 simultaneously cool the first heat-conducting layer 10, but their flow directions are opposite. The cross-sectional area of ​​the third flow channel 60 gradually decreases along the second flow direction. The first flow channel 30 and the third flow channel 60 mutually inhibit the local evaporation phenomenon at the tail of each other's flow channels, reducing the dryness of the cooling medium after boiling in the first flow channel 30 and the second flow channel 40, and improving flow stability.

[0074] like Figure 3 As shown, the fourth flow channel 70 extends along the surface of the second heat-conducting layer 20, meaning that the phase change working fluid in the fourth flow channel 70 cools the second heat-conducting layer 20. The phase change working fluid in the fourth flow channel 70 flows along the first flow direction, therefore the flow direction of the fourth flow channel 70 is opposite to that of the second flow channel 40. The cross-sectional area of ​​the fourth flow channel 70 gradually decreases along the first flow direction, and the third flow channel 60 and the fourth flow channel 70 are arranged opposite each other along the first arrangement direction. The third flow channel 60 and the fourth flow channel 70 mutually inhibit the local evaporation phenomenon at the tail of each other's flow channels, and the second flow channel 40 and the fourth flow channel 70 mutually inhibit the local evaporation phenomenon at the tail of each other's flow channels, thereby improving the flow stability of multiple flow channels.

[0075] like Figure 4As shown, multiple first flow channels 30, second flow channels 40, third flow channels 60, and fourth flow channels 70 are arranged along a second arrangement direction, which is perpendicular to the first arrangement direction. First flow channels 30 and third flow channels 60 are arranged alternately along the second arrangement direction, as are second flow channels 40 and fourth flow channels 70. This alternating forward and reverse flow arrangement of the first flow channels 30, second flow channels 40, third flow channels 60, and fourth flow channels 70 further improves the temperature uniformity of the cooling surface.

[0076] Example 3:

[0077] like Figure 5 As shown, the difference between Embodiment 3 and Embodiment 1 is that the multi-layer cross-convex channel phase change cold plate also includes a first reversal channel 80, which connects the outlet of the first flow channel 30 and the inlet of the second flow channel 40. When the heat dissipation demand of the second heat-conducting layer 20 is small, the first reversal channel 80 is opened, allowing the phase change working medium of the first flow channel 30 to flow into the second flow channel 40, thereby achieving reversal. After the phase change working medium of the first flow channel 30 cools the first heat-conducting layer 10, it continues to flow into the second flow channel 40 to cool the second heat-conducting layer 20. During the flow, the phase fraction change of the cooling medium leads to differences in heat transfer effect, automatically matching the different heat dissipation demands of the first heat-conducting layer 10 and the second heat-conducting layer 20. The first flow channel 30 and the second flow channel 40 transfer heat, and at the same cross section along the flow direction, the cooling capacity of the first flow channel 30 and the second flow channel 40 are complementary, which can suppress the local evaporation phenomenon of the second flow channel 40, ensure the temperature uniformity of the first flow channel 30 and the second flow channel 40, and improve energy utilization.

[0078] By utilizing the natural change in phase fraction of the cooling medium during the folding flow process, a difference in heat transfer intensity is formed between the first heat-conducting layer 10 and the second heat-conducting layer 20. This difference can automatically adapt to the different heat dissipation requirements of the two sides, and can achieve uniform temperature control to a certain extent without additional control.

[0079] like Figure 6 As shown, it should be understood that in some embodiments, the difference from Embodiment 2 is that the multilayer cross-convex channel phase change cold plate further includes a second reversal channel 90. The second reversal channel 90 connects the outlet of the third flow channel 60 and the inlet of the fourth flow channel 70. When the heat dissipation demand of the second heat-conducting layer 20 is small, the second reversal channel 90 is opened, allowing the cooling medium of the third flow channel 60 to flow from the outlet of the third flow channel 60 to the inlet of the fourth flow channel 70, forming a reversal to improve energy utilization.

[0080] Furthermore, the cross-sectional area of ​​the second flow channel 40 and the fourth flow channel 70 are adjustable. The second side plate 41 can be configured as a telescopic plate to control the distance between the second heat-conducting layer 20 and the heat-conducting partition 50, thereby controlling the cross-sectional area of ​​the second flow channel 40 and the fourth flow channel 70. When the outlet of the first flow channel 30 connects with the inlet of the second flow channel 40 to form a cooling medium reversal flow channel, the amount of cooling medium bubbles in the second flow channel 40 is at its maximum. By controlling the reduction of the cross-sectional area of ​​the second flow channel 40, the velocity of the fluid in the second flow channel 40 can be accelerated, breaking through large bubbles at the tail of the flow channel and mitigating the instability of the two-phase flow. Similarly, when the third flow channel 60 connects with the fourth flow channel 70 to form a reversal flow channel, the cross-sectional area of ​​the fourth flow channel 70 can also be reduced to accelerate the fluid velocity, thereby mitigating the instability of the two-phase flow.

[0081] Example 4:

[0082] like Figure 7 As shown, the difference between Embodiment 4 and Embodiment 1 is that the thermally conductive insulating layer 50 includes a first insulating layer 51, a second insulating layer 52, and a compensating flow channel 53. The first flow channel 30 and the third flow channel 60 both extend along the surface of the first insulating layer 51, and the second flow channel 40 and the fourth flow channel 70 both extend along the surface of the second insulating layer 52. The compensating flow channel 53 is located between the first insulating layer 51 and the second insulating layer 52, and the phase change working fluid within the compensating flow channel 53 flows along either a first flow direction or a second flow direction.

[0083] Based on the changes in cooling efficiency of the first heat-conducting layer 10 and the second heat-conducting layer 20, the flow direction or flow rate of the cooling medium in the compensation channel 53 is adjusted to compensate for the cooling capacity of the first channel 30 or the second channel 40.

[0084] Example 5:

[0085] like Figure 8 As shown, the difference between Embodiment 5 and Embodiment 1 is that the first flow channel 30 further includes a plurality of first spikes 32, which are spaced apart along the inner wall of the first heat-conducting layer 10 and the density of the spikes gradually increases along the first flow direction. The second flow channel 40 further includes a plurality of second spikes 42, which are spaced apart along the inner wall of the second heat-conducting layer 20 and the density of the spikes gradually increases along the second flow direction. The first spikes 32 and the second spikes 42 can accelerate the probability of bubble breakage in the first heat-conducting layer 10 and the second heat-conducting layer 20, thereby accelerating the flow rate of the phase change working fluid and improving the heat exchange efficiency.

[0086] In some embodiments, the third flow channel 60 is provided with a plurality of third prongs arranged at intervals on the inner wall of the first heat-conductive layer 10, the arrangement density of the third prongs gradually increases along the second flow direction, and the fourth flow channel 70 is provided with a plurality of fourth prongs arranged at intervals on the inner wall of the second heat-conductive layer 20, the arrangement density of the fourth prongs gradually increases along the first flow direction.

[0087] In the combined scheme of Embodiment Three and Embodiment Five, the first prongs 32 break large bubbles into small bubbles, and the small bubbles have stronger flowability and can be more evenly distributed in the flow channel, adapting to the flow demand of a complex flow channel (such as a turn-back structure) and avoiding, to some extent, the stagnation or too fast flow of the working medium in a local area.

[0088] In other embodiments, the sawtooth shape formed by the first prongs 32 and the second prongs 42 can be replaced by a wave shape or a porous shape to increase the roughness of the surface, accelerate the destruction of bubble adhesion, and thus improve the flow stability of the cooling working medium.

[0089] Embodiment Six:

[0090] As shown in Figure 9 The present embodiment provides a multi-layer cross-tapered channel phase change cold plate control method, applied to the multi-layer cross-tapered channel phase change cold plate of any one of Embodiments One to Five. The multi-layer cross-tapered channel phase change cold plate control method includes steps S10 to S50.

[0091] Step S10, real-time acquisition of a first target heat dissipation power of the first heat-conductive layer 10 and a second target heat dissipation power of the second heat-conductive layer 20.

[0092] Step S20, when the first target heat dissipation power and the second target heat dissipation power are both greater than a first threshold value, a first cooling strategy is executed, and the first cooling strategy includes introducing the first phase change working medium flowing along the first flow direction into the first flow channel 30 and introducing the second phase change working medium flowing along the second flow direction into the second flow channel 40.

[0093] Step S30, adjustment of a first fluid parameter of the first phase change working medium according to the first target heat dissipation power, the first fluid parameter including a first flow rate. In some embodiments, the first fluid parameter further includes a first pressure.

[0094] Step S40, adjustment of a second fluid parameter of the second phase change working medium according to the second target heat dissipation power, the second fluid parameter including a second flow rate. In some embodiments, the second fluid parameter further includes a second pressure.

[0095] The embodiment is used in the case that the heat conduction requirements of the first heat conduction layer 10 and the second heat conduction layer 20 are both high, and the first flow channel 30 and the second flow channel 40 are respectively filled with separate phase change working medium for cooling. The first fluid parameter is adjusted according to the actual first target heat dissipation power, and the second fluid parameter is adjusted according to the actual second target heat dissipation power, so as to improve the efficiency of double-sided heat dissipation of the high-power laser.

[0096] In some embodiments, the multi-layer cross tapered channel phase change cold plate further comprises a first return channel 80, which is connected to the outlet of the first flow channel 30 and the inlet of the second flow channel 40.

[0097] The first cooling strategy further comprises closing the first return channel 80.

[0098] The multi-layer cross tapered channel phase change cold plate control method further comprises steps S50 and S60.

[0099] Step S50, when the first target heat dissipation power or the second target heat dissipation power is less than the first threshold value, and the first target heat dissipation power is greater than the second target heat dissipation power, the second cooling strategy is executed. The second cooling strategy comprises filling the first flow channel 30 with the third phase change working medium flowing in the first flow direction and opening the first return channel 80. Thus, the phase change working medium of the first flow channel 30 flows into the second flow channel 40 to realize the return. After the phase change working medium of the first flow channel 30 cools the first heat conduction layer 10, it continues to flow into the second flow channel 40 to cool the second heat conduction layer 20. The change of the phase fraction of the cooling medium during the flow process causes the difference in heat exchange effect, which automatically matches the different heat dissipation requirements of the first heat conduction layer 10 and the second heat conduction layer 20. The first flow channel 30 and the second flow channel 40 transfer heat, and the cooling capacity of the first flow channel 30 and the cooling capacity of the second flow channel 40 are complementary at the same cross section along the flow direction, which can suppress the local dry-out phenomenon of the second flow channel 40, guarantee the uniformity of the first flow channel 30 and the second flow channel 40, and improve the energy utilization rate.

[0100] Step S60, adjusting the third fluid parameter of the third phase change working medium according to the first target heat dissipation power and the second target heat dissipation power, the third fluid parameter comprising the third flow rate.

[0101] In some embodiments, the channel cross-sectional area of the second flow channel 40 is adjustable.

[0102] The second cooling strategy further comprises steps S51 and S52.

[0103] Step S51, obtaining a first difference value of the first target heat dissipation power and the second target heat dissipation power. The first difference value is the basis for judging the difference between the heat dissipation requirements of the first heat conduction layer 10 and the second heat conduction layer 20.

[0104] Step S52, when the first difference is greater than the second threshold, according to the second target heat dissipation power, the reduction ratio of the channel cross-sectional area of the second flow channel 40 is adjusted, and the reduction ratio is less than 1.

[0105] When the first difference is large, the remaining cold quantity of the phase change working medium in the first flow channel 30 can be used to cool the second heat conduction layer 20. At the same time, since the heat dissipation demand of the second heat conduction layer 20 is small enough, the flow sensitivity of the cooling medium in the second flow channel 40 is low, and reducing the channel cross-sectional area of the second flow channel 40 can increase the flow rate of the phase change working medium in the second flow channel 40, thereby breaking the large bubbles in the second flow channel 40 as a whole, relieving the instability of the two-phase flow, and thereby improving the cooling effect on the second heat conduction layer 20.

[0106] In some embodiments, the heat conduction partition layer 50 includes a first partition layer 51, a second partition layer 52, and a compensation flow channel 53. The first flow channel 30 and the third flow channel 60 extend along the surface of the first partition layer 51. The second flow channel 40 and the fourth flow channel 70 extend along the surface of the second partition layer 52. The first flow channel 30 and the third flow channel 60 are located between the first heat conduction layer 10 and the first partition layer 51, and the second flow channel 40 and the fourth flow channel 70 are located between the second heat conduction layer 20 and the second partition layer 52. The compensation flow channel 53 is located between the first partition layer 51 and the second partition layer 52, and the phase change working medium in the compensation flow channel 53 flows in the first flow direction or the second flow direction.

[0107] The first cooling strategy further includes steps S21 and S22.

[0108] Step S21, when the first target heat dissipation power is greater than the second target heat dissipation power, the fourth phase change working medium flowing in the second flow direction is introduced into the compensation flow channel 53.

[0109] Step S22, when the second target heat dissipation power is greater than the first target heat dissipation power, the fifth phase change working medium flowing in the first flow direction is introduced into the compensation flow channel 53.

[0110] Steps S21 and S22 adjust the flow direction of the phase change working medium in the compensation flow channel 53 according to the actual heat dissipation demand of the first heat conduction layer 10 and the second heat conduction layer 20, so as to better adapt to the double-layer flow channel cooling plate, and improve the effect of double-sided cooling of the high-power laser.

[0111] Those skilled in the art can understand that the above embodiments are specific cases for implementing the present disclosure, and in actual application, various changes can be made in form and details without departing from the scope of the present disclosure.

Claims

1. A multi-layer cross-tapered channel phase change cold plate, characterized by, The multi-layer cross tapered channel phase change cold plate comprises: a first heat-conductive layer; a second heat-conductive layer, the first heat-conductive layer and the second heat-conductive layer being arranged at intervals along a first arrangement direction; a first flow channel extending along a surface of the first heat-conductive layer; a phase change working medium in the first flow channel flows along a first flow direction; a cross-sectional area of the first flow channel gradually decreases along the first flow direction; a second flow channel extending along a surface of the second heat-conductive layer; a phase change working medium in the second flow channel flows along a second flow direction; a cross-sectional area of the second flow channel gradually decreases along the second flow direction; the first flow direction and the second flow direction are opposite; the first flow channel and the second flow channel are arranged opposite to each other along the first arrangement direction; a heat-conductive partition layer; the heat-conductive partition layer is located between the first flow channel and the second flow channel; the heat-conductive partition layer comprises a first partition layer, a second partition layer and a compensation flow channel; the first flow channel extends along a surface of the first partition layer; the first flow channel is located between the first heat-conductive layer and the first partition layer; the second flow channel extends along a surface of the second partition layer; the second flow channel is located between the second heat-conductive layer and the second partition layer; the compensation flow channel is located between the first partition layer and the second partition layer; a phase change working medium in the compensation flow channel flows along the first flow direction or the second flow direction.

2. The multi-layer cross tapered channel phase change cold plate of claim 1, wherein, The multi-layer cross tapered channel phase change cold plate further comprises: a third flow channel extending along a surface of the first heat-conductive layer; a phase change working medium in the third flow channel flows along the second flow direction; a cross-sectional area of the third flow channel gradually decreases along the second flow direction; a fourth flow channel extending along a surface of the second heat-conductive layer; a phase change working medium in the fourth flow channel flows along the first flow direction; a cross-sectional area of the fourth flow channel gradually decreases along the first flow direction; the third flow channel and the fourth flow channel are arranged opposite to each other along the first arrangement direction.

3. The multi-layer cross tapered channel phase change cold plate of claim 2, wherein, The first flow channel, the second flow channel, the third flow channel and the fourth flow channel are arranged in multiple along a second arrangement direction; the second arrangement direction is perpendicular to the first arrangement direction; the first flow channel and the third flow channel are staggered arranged along the second arrangement direction; the second flow channel and the fourth flow channel are staggered arranged along the second arrangement direction.

4. The multi-layer cross tapered channel phase change cold plate of claim 2, wherein, The multi-layer cross tapered channel phase change cold plate further comprises: a first return channel connecting an outlet of the first flow channel and an inlet of the second flow channel; a second return channel connecting an outlet of the third flow channel and an inlet of the fourth flow channel.

5. The multi-layer cross tapered channel phase change cold plate of claim 4, wherein, A cross-sectional area of the second flow channel is adjustable; a cross-sectional area of the fourth flow channel is adjustable.

6. The multi-layer cross tapered channel phase change cold plate of claim 1, wherein, A plurality of first prongs are arranged at intervals on an inner wall of the first heat-conductive layer; an arrangement density of the first prongs gradually increases along the first flow direction; A plurality of second prongs are arranged at intervals on an inner wall of the second heat-conductive layer; an arrangement density of the first prongs gradually increases along the second flow direction.

7. A method for controlling a multi-layer cross-tapered channel phase change cold plate, applied to the multi-layer cross-tapered channel phase change cold plate of any one of claims 1-6, characterized in that, The multi-layer cross tapered channel phase change cold plate control method comprises: Real-time acquisition of a first target heat dissipation power of a first heat conduction layer and a second target heat dissipation power of a second heat conduction layer; When the first target heat dissipation power and the second target heat dissipation power are both greater than a first threshold value, a first cooling strategy is executed; the first cooling strategy comprises introducing a first phase change working medium flowing in a first flow direction into the first flow channel and introducing a second phase change working medium flowing in a second flow direction into the second flow channel; Adjusting a first fluid parameter of the first phase change working medium according to the first target heat dissipation power; the first fluid parameter comprises a first flow rate; Adjusting a second fluid parameter of the second phase change working medium according to the second target heat dissipation power; the second fluid parameter comprises a second flow rate; The first cooling strategy further comprises: When the first target heat dissipation power is greater than the second target heat dissipation power, introducing a fourth phase change working medium flowing in the second flow direction into a compensation flow channel; When the second target heat dissipation power is greater than the first target heat dissipation power, introducing a fifth phase change working medium flowing in the first flow direction into the compensation flow channel.

8. The method of claim 7, wherein, The multi-layer cross tapered channel phase change cold plate further comprises a first return channel, which communicates an outlet of the first flow channel and an inlet of the second flow channel; The first cooling strategy further comprises closing the first return channel; The multi-layer cross tapered channel phase change cold plate control method further comprises: When the second target heat dissipation power is less than the first threshold value and the first target heat dissipation power is greater than the second target heat dissipation power, a second cooling strategy is executed; The second cooling strategy comprises introducing a third phase change working medium flowing in the first flow direction into the first flow channel and opening the first return channel; Adjusting a third fluid parameter of the third phase change working medium according to the first target heat dissipation power and the second target heat dissipation power; the third fluid parameter comprises a third flow rate.

9. The method of claim 8, wherein, The channel cross-sectional area of the second flow channel is adjustable; The second cooling strategy further comprises: Acquisition of a first difference value of the first target heat dissipation power and the second target heat dissipation power; When the first difference value is greater than a second threshold value, adjusting a reduction ratio of the channel cross-sectional area of the second flow channel according to the second target heat dissipation power; the reduction ratio is less than 1.

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