CN109671688B - Refrigerant phase change cold plate - Google Patents

Refrigerant phase change cold plate Download PDF

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Publication number
CN109671688B
CN109671688B CN201710961842.7A CN201710961842A CN109671688B CN 109671688 B CN109671688 B CN 109671688B CN 201710961842 A CN201710961842 A CN 201710961842A CN 109671688 B CN109671688 B CN 109671688B
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flow channel
refrigerant
cold plate
mixing cavity
scale
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CN109671688A (en
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冯钊赞
姚磊
胡家喜
邓文川
王春燕
李诗怀
郭宗坤
何凯
曾云峰
王雄
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CRRC Zhuzhou Institute Co Ltd
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CRRC Zhuzhou Institute Co Ltd
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    • HELECTRICITY
    • H01ELECTRIC ELEMENTS
    • H01LSEMICONDUCTOR DEVICES NOT COVERED BY CLASS H10
    • H01L23/00Details of semiconductor or other solid state devices
    • H01L23/34Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements
    • H01L23/42Fillings or auxiliary members in containers or encapsulations selected or arranged to facilitate heating or cooling
    • H01L23/427Cooling by change of state, e.g. use of heat pipes

Abstract

The invention discloses a refrigerant phase change cold plate, comprising: the cold plate substrate is provided with an inlet mixing cavity, an outlet mixing cavity and a flow channel for communicating the inlet mixing cavity with the outlet mixing cavity; the cover plate is arranged on the cold plate base plate and used for sealing the flow channel, and the heating element is arranged on the cover plate and/or the cold plate base plate. The flow channel comprises a forward flow channel and a reverse flow channel which are communicated with each other, the forward flow channel and the reverse flow channel are communicated through a bend, a refrigerant enters from the inlet mixing cavity, passes through the forward flow channel with more than one level and the reverse flow channel with more than one level and then flows out from the outlet mixing cavity. The forward flow channel and the reverse flow channel respectively comprise a sudden shrinkage flow channel and an expansion flow channel which are communicated with each other, and the coolant generates a hydrodynamic cavitation process in the flow channels at intervals once passing through the sudden shrinkage flow channel and the expansion flow channel. The invention can solve the technical problems of unstable flow pattern distribution and flow in different directions of the two-phase flow in the channel of the existing cold plate and low heat exchange performance.

Description

Refrigerant phase change cold plate
Technical Field
The invention relates to the technical field of heat dissipation of power electronic devices, in particular to a refrigerant phase change cold plate based on a hydrodynamic cavitation effect or a gas-liquid separation effect.
Background
In the heat dissipation technology of the high-power electronic device, the flow boiling is one of the forms with the highest heat exchange coefficient, and in the existing heat radiator of the high-power electronic device, the refrigerant phase change cold plate adopting the flow boiling technology has higher efficiency. Flow boiling heat exchange performance is closely related to the distribution and flow characteristics of the gas phase and the liquid phase, for example, when the dryness is high, the heat exchange surface is covered by the gas phase, which causes the heat exchange to be deteriorated. Refrigerant phase change cold plates based on the technology often adopt a single serpentine flow channel arrangement scheme, flow characteristics of gas-liquid two-phase flow are not considered, and improvement of heat exchange performance of the cold plates is greatly limited. This solution also often has the following technical drawbacks:
(1) the pipe diameter of the flow channel is single, and the resistance of gas-liquid two-phase mixed flow is large;
(2) when the cold plate is vertically placed, an upward flow and a downward flow exist, the flowing boiling heat exchange performance is sensitive to the flowing direction (the upward flow and the downward flow), and the instability of gas-liquid flow during the downward flow greatly reduces the heat exchange performance of the cold plate;
(3) when the gas phase content in the flow channel is high, large-area drying may occur on the heat exchange surface in the flow channel, resulting in a flying rise in surface temperature.
In the prior art, the technical scheme which is similar to the application of the invention mainly comprises the following steps:
scheme 1 is applied by the changjiang three gorges group corporation of china on year 2014, month 02, and published on year 2014, month 06, day 04, publication No. CN203633055U, which is a heat sink heat dissipation device with a novel heat exchange structure and self-adaptive characteristics. The utility model discloses a patent discloses a heat sink heat abstractor with novel heat transfer structure and self-adaptation characteristic, heat sink heat abstractor comprises microchannel heat sink system, micropump device, power supply system and power supply unit. The microchannel heat sink system is formed by packaging a top cover plate, a drainage plate and a heat sink plate from top to bottom, and microchannels are processed on the heat sink plate. The micro-channel is formed by combining a plurality of micro-channels with different hydraulic diameters in a multi-stage mode. The utility model discloses a can realize heat abstractor of high heat transfer intensity, it has the self-adaptation characteristic, is applicable to the small-size, high heat flux density heating part, like electron device, laser device etc.. But this scheme is applicable to single-phase heat transfer, does not involve the phase transition heat transfer of refrigerant.
Scheme 2 is applied by the institute of engineering thermal physics of the academy of sciences of china at 16/05 in 2014 and at 30/07 in 2014, and the publication number is CN 103954162A. The invention discloses a low-resistance hydrodynamic cavitation structure for strengthening microchannel heat exchange, which mainly comprises: a base plate, on which several cooling micro-channels are uniformly arranged in parallel. One end of the cooling micro-channel is an inlet, the other end of the cooling micro-channel is an outlet, the inlet is provided with a flow distribution cavity, and the outlet is provided with a liquid collection cavity. And a reducing-gradually expanding hydraulic structure for inducing cavitation is arranged in each cooling micro-channel between the flow distribution cavity and the liquid collection cavity. The ratio of the throat section length of the convergent-divergent hydraulic structure to the width of the cooling micro-channel is 0.1-1, the inlet cone angle of the convergent section of the convergent-divergent hydraulic structure is 15-45 degrees, and the outlet cone angle of the divergent section of the convergent-divergent hydraulic structure is 15-90 degrees. The invention can reduce the flow resistance loss of liquid and reduce the extra pump work input for inducing cavitation while strengthening the heat exchange of the micro-channel. The invention is suitable for single-phase flow heat exchange, and has the effect that gas dissolved in liquid escapes when the pressure is lower than saturated vapor pressure, but the condition of boiling heat exchange is not considered, a large amount of bubbles are generated during boiling heat exchange, and a coupling effect is generated with cavitation.
Scheme 3 is applied by the institute of physical and chemical technology of the academy of sciences of china on 10 th 2009, and is published on 09 th 01 th 2010, with publication number CN 201570775U. The utility model discloses a single-chip laser diode microchannel phase change is heat sink, including the fin, have the inlet channel of cavitation structural style on the fin. The utility model discloses a can effectively restrain the emergence of the in-process instability phenomenon of boiling, guarantee the reliable normal heat dissipation of laser diode. The cooling device has the advantages of high heat dissipation heat flow density, good cooling effect, stable work and the like. However, the channel characteristic hydraulic diameter of the technical scheme of the utility model completely belongs to the microscale, lacks the combination of multi-scale channels from the microscale to the macroscale, and is not suitable for the heat dissipation of the large-sized cold plate.
Therefore, a more efficient flow channel structure needs to be developed to solve the technical problems of two-phase flow pattern distribution and flow instability in different directions in the existing cold plate channel.
Disclosure of Invention
In view of the above, the present invention provides a cold plate for phase change of refrigerant, so as to solve the technical problems of unstable flow pattern distribution of two-phase flow in the channel of the existing cold plate and flow in different directions, and low heat exchange performance.
In order to achieve the above object, the present invention specifically provides a technical implementation scheme of a refrigerant phase change cold plate, which dissipates heat for a heating element disposed thereon, and includes:
the cold plate base plate is provided with an inlet mixing cavity, an outlet mixing cavity and a flow passage for communicating the inlet mixing cavity and the outlet mixing cavity;
the cover plate is arranged on the cold plate substrate and used for sealing the flow channel, and the heating element is arranged on the cover plate and/or the cold plate substrate;
the flow channel comprises a forward flow channel and a reverse flow channel which are communicated with each other, the forward flow channel and the reverse flow channel are communicated through a bend, a refrigerant enters from the inlet mixing cavity, passes through more than one stage of forward flow channel and more than one stage of reverse flow channel and then flows out from the outlet mixing cavity;
the forward flow passage includes a first contracted flow passage and a first expanded flow passage which are communicated with each other, and the reverse flow passage includes a second contracted flow passage and a second expanded flow passage which are communicated with each other. And a refrigerant enters from the inlet mixing cavity, sequentially passes through the first sudden shrinkage flow channel and the first expansion flow channel, and sequentially passes through the second sudden shrinkage flow channel and the second expansion flow channel through the bent channel, so that the refrigerant generates a hydrodynamic cavitation process at intervals in the flow channel.
Preferably, when the refrigerant enters the first sudden shrinkage flow channel from the inlet mixing chamber, the cross section of the refrigerant is rapidly reduced, the flow velocity of the refrigerant is rapidly increased, and when the static pressure of the refrigerant is smaller than the vapor pressure at the current temperature, cavitation bubbles are generated. When the refrigerant enters the first expansion flow channel, the pressure is recovered, and the high-speed micro jet formed by the collapse of the cavitation bubbles strengthens the boiling heat exchange in the first expansion flow channel and inhibits the polymerization of small bubbles during boiling.
Preferably, when the refrigerant enters the curved passage, a streaming vortex generated by a curvature structure of the curved passage induces a cavitation effect, and meanwhile, the refrigerant in a gas-liquid two-phase state passes through the second sudden shrinkage flow passage, and then passes through the second expansion flow passage after static pressure reduction, cavitation bubbles, bubble fracture and disturbance, boiling enhancement, and then the refrigerant rapidly decreases in the main flow direction, so that the resistance of the bubbles generated during boiling in the countercurrent direction to the top is increased, and meanwhile, large bubbles generated during boiling of the refrigerant are not easily gathered under the influence of the cavitation bubble fracture, so that the flow pattern of the refrigerant passing through the countercurrent flow passage is optimized, and the boiling heat exchange is enhanced.
Preferably, the forward flow passage includes a first expansion flow passage having more than two expansion stages and sequentially communicating with each other, and a width of the first expansion flow passage is gradually increased in a direction from the first sudden-shrinkage flow passage to the curved passage. The reverse flow passage comprises a second expansion flow passage with more than two expansion stages which are communicated in sequence, and the width of the second expansion flow passage is gradually increased along the direction from the second sudden shrinkage flow passage to the next bend.
Preferably, the number of expansion stages of the first expanded flow passage in the forward flow passage is the same as the number of expansion stages of the second expanded flow passage in the reverse flow passage.
The invention also provides another technical implementation scheme of the refrigerant phase change cold plate, the refrigerant phase change cold plate is used for radiating heat of a heating element arranged on the refrigerant phase change cold plate, and the refrigerant phase change cold plate comprises the following components:
the cold plate base plate is provided with an inlet mixing cavity, an outlet mixing cavity and a flow passage for communicating the inlet mixing cavity and the outlet mixing cavity;
the cover plate is arranged on the cold plate substrate and used for sealing the flow channel, and the heating element is arranged on the cover plate and/or the cold plate substrate;
the flow channel comprises a forward flow channel and a reverse flow channel which are communicated with each other, the forward flow channel and the reverse flow channel are communicated through a bend, a refrigerant enters from the inlet mixing cavity, passes through more than one stage of forward flow channel and more than one stage of reverse flow channel and then flows out from the outlet mixing cavity;
the forward flow channel comprises a first expansion flow channel, a first large-scale flow channel and a plurality of first micro-scale flow channels with smaller width sizes relative to the first large-scale flow channel. The reverse flow channel comprises a second expansion flow channel, a second large-scale flow channel and a plurality of second micro-scale flow channels with smaller width relative to the second large-scale flow channel. And one part of the refrigerant enters the first micro-scale flow channel from the inlet mixing cavity and flows into the first expansion flow channel through the first micro-scale flow channel, and the other part of the refrigerant enters the first large-scale flow channel from the inlet mixing cavity and then enters the first expansion flow channel through the injection hole arranged on the first large-scale flow channel. And one part of the refrigerant enters the second micro-scale flow channel through the bend and flows into the second expansion flow channel through the second micro-scale flow channel, and the other part of the refrigerant enters the second large-scale flow channel from the bend and then enters the second expansion flow channel through the jet holes arranged on the second large-scale flow channel, so that the refrigerant is subjected to a gas-liquid separation process at intervals in the flow channel.
Preferably, when the refrigerant enters the first micro-scale flow channel from the inlet mixing chamber, the flow velocity rapidly rises, and when the static pressure of the refrigerant is smaller than the vapor pressure at the current temperature, cavitation bubbles are generated, and the hydrodynamic cavitation effect induced by the refrigerant passing through the first micro-scale flow channel can strengthen the boiling heat exchange. When the gas phase in the refrigerant is close to the first micro-scale flow channel, the gas phase is easy to flow into the first large-scale flow channel due to the fact that the surface energy of cavitation bubbles is increased when the cavitation bubbles enter the first micro-scale flow channel. And the gas phase in the refrigerant enters the first large-scale flow channel and then reenters the first expansion flow channel positioned at the rear part of the first micro-scale flow channel through the injection hole. Due to the throttling effect of the first micro-scale flow channel, the pressure in the first expansion flow channel is low, and the pressure in the first large-scale flow channel is high, so that high-low pressure difference is formed on two sides of the jet hole, the gas phase speed passing through the jet hole is accelerated, and the boiling bubbles in the first expansion flow channel are impacted, and therefore the boiling bubbles are prevented from agglomerating into large bubbles blocking the flow channel. When the refrigerant enters the first expansion flow channel, the pressure is recovered, and the high-speed micro jet formed by the collapse of the cavitation bubbles strengthens the boiling heat exchange in the first expansion flow channel and inhibits the polymerization of small bubbles during boiling.
Preferably, when the refrigerant enters the curved channel, under the action of gravity and centrifugal force, gas-liquid two phases are separated, a streaming vortex generated by a curvature structure of the curved channel induces cavitation effect, meanwhile, after the refrigerant in a gas-liquid two-phase state enters the second expansion channel through the second micro-scale channel and the second large-scale channel, the static pressure of the refrigerant is sharply reduced along the main flow direction, the resistance of bubbles generated during boiling to the upstream is increased, and meanwhile, large bubbles generated during boiling of the refrigerant are not easily gathered under the influence of cavitation bubble breakage, so that the flow pattern of the refrigerant passing through the reverse channel is optimized, and boiling heat exchange is enhanced.
Preferably, the first micro-scale flow channel is communicated with the inlet mixing cavity and is positioned on one side, close to the reverse flow channel, in the forward flow channel, and the first large-scale flow channel is positioned on the other side in the forward flow channel and is adjacent to and arranged side by side with the first micro-scale flow channel. One end of the first expansion flow channel is communicated with the first microscale flow channel, and the other end of the first expansion flow channel is communicated with the bend. The second large-scale flow channel is communicated with the bend and is positioned on one side, close to the first expansion flow channel, in the reverse flow channel, and the second micro-scale flow channel is arranged on the other side in the reverse flow channel and is adjacent to and arranged side by side with the second large-scale flow channel. One end of the second microscale channel is communicated with the bend, and the other end of the second microscale channel is communicated with the second expansion channel. When the refrigerant passes through the bend, the liquid phase part of the refrigerant is distributed on the outer side in the bend under the action of centrifugal force.
Preferably, the refrigerant enters the refrigerant phase change cold plate in a slightly supercooled state or a saturated state, and the heat of the heating element is taken away in a supercooled boiling or saturated boiling manner.
Preferably, the cold plate substrate is provided with an inlet, and the inlet is communicated with the inlet mixing chamber. An outlet is further formed in the cold plate substrate and communicated with the outlet mixing cavity. The cavity cross-sectional dimension of the outlet mixing chamber is larger than the cavity cross-sectional dimension of the inlet mixing chamber, and the cross-sectional dimension of the outlet is larger than the cross-sectional dimension of the inlet.
Preferably, pressure and temperature sensors are respectively arranged in the inlet mixing cavity and the outlet mixing cavity to monitor instantaneous temperature, pressure and pressure difference fluctuation data of the refrigerant, and the inflow flow and temperature of the refrigerant can be adjusted according to the data.
By implementing the technical scheme of the refrigerant phase change cold plate provided by the invention, the refrigerant phase change cold plate has the following beneficial effects:
(1) according to the invention, the multi-scale flow channel is designed in the cold plate, and the hydrodynamic cavitation effect or the gas-liquid separation effect of the multi-scale flow channel is utilized, so that the difference of two-phase flow patterns between the forward flow channel and the reverse flow channel can be reduced, the flow resistance of gas-liquid two phases is reduced, the distribution of the gas phase and the liquid phase on the heat exchange surface is improved, and the uniformity and the stability of the temperature distribution of the heat exchange surface are improved;
(2) the invention can effectively solve the problem of flow boiling instability through the hydrodynamic cavitation effect, and can advance the boiling initiation by utilizing the hydrodynamic cavitation effect, reduce the superheat degree, break large bubbles through cavitation bubble bursting and reduce the problem of boiling instability;
(3) the invention can effectively solve the problem of flow pattern distribution of two-phase flow based on the gas-liquid separation effect, and can realize the separation of gas-liquid two phases by arranging the multi-scale flow channel by utilizing the effect; the separated steam becomes high-speed steam flow through the jet holes, large bubbles generated by boiling in the liquid channel can be further broken, the flow resistance is favorably reduced, and the wetting of a heat exchange surface with higher heat flow density is also favorably realized.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below. It is obvious that the drawings in the following description are only some embodiments of the invention, and that for a person skilled in the art, other embodiments can be obtained from these drawings without inventive effort.
FIG. 1 is a schematic diagram of a cold plate substrate according to an embodiment of a refrigerant phase change cold plate of the present invention;
FIG. 2 is a schematic diagram of a cold plate substrate according to another embodiment of the refrigerant phase change cold plate of the present invention;
FIG. 3 is a schematic view of an installation structure of a refrigerant phase change cold plate according to an embodiment of the present invention;
in the figure: 1-cold plate substrate, 2-inlet mixing cavity, 3-outlet mixing cavity, 4-inlet, 5-outlet, 6-cover plate, 7-heating element, 10-flow channel, 11-first sudden shrinkage flow channel, 12-first expansion flow channel, 13-bend, 14-second sudden shrinkage flow channel, 15-second expansion flow channel, 16-first large-scale flow channel, 17-first micro-scale flow channel, 18-jet hole, 19-second large-scale flow channel, 100-refrigerant phase change cold plate, and 110-second micro-scale flow channel.
Detailed Description
For reference and clarity, the terms, abbreviations or abbreviations used hereinafter are as follows:
hydrodynamic cavitation effect: the method is characterized in that a low-pressure and high-flow-rate state is manufactured at a certain position of a pipeline through which liquid passes, when the pressure of the liquid is smaller than saturated vapor pressure, bubbles in the liquid are expanded continuously, the volume of the bubbles is increased, and the bubbles collapse and burst after reaching a high-pressure and low-flow-rate area along with the movement of the fluid;
gas-liquid separation effect: when the bubbles enter the smaller flow passage from the larger flow passage, the increase of the surface energy requires that the two ends of the bubbles have larger pressure difference, and when the pressure difference does not meet the requirement, the bubbles cannot enter the smaller flow passage.
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention. It is to be understood that the described embodiments are merely a few embodiments of the invention, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Referring to fig. 1 to fig. 3, embodiments of a refrigerant phase change cold plate according to the present invention are shown, and the present invention will be further described with reference to the drawings and the embodiments.
Example 1
As shown in fig. 1 and 3, an embodiment of a refrigerant phase change cold plate for dissipating heat of a heating element 7 disposed thereon includes:
the device comprises a cold plate substrate 1, wherein an inlet mixing cavity 2, an outlet mixing cavity 3 and a flow channel 10 for communicating the inlet mixing cavity 2 and the outlet mixing cavity 3 are arranged on the cold plate substrate 1; a cover plate 6 arranged on the cold plate substrate 1 for sealing the flow passage 10, and a heating element 7 arranged on the cover plate 6, or arranged at the bottom of the cold plate substrate 1, or arranged on the cover plate 6 and the bottom of the cold plate substrate 1 on both sides. The manufacturing process comprises the following steps: a flow passage 10 (not shown in fig. 3) and an inlet mixing chamber 2 and an outlet mixing chamber 3 are milled on a cold plate base plate 1 made of aluminum, and an inlet 4 and an outlet 5 are opened. And the cover plate 6 made of aluminum is arranged on the flow channel 10, and the cover plate 6 and the flow channel 10 are sealed by vacuum brazing. A heating element (the heating element is a power device, such as an IGBT or an IGCT, and the heat of the heating element is transferred to the refrigerant in the flow channel 10 through the cover plate 6), and is mounted on the cover plate 6 by means of screw fastening (the screw hole is not shown in the figure). Arrows shown in fig. 3 indicate the inflow and outflow directions of the refrigerant.
The flow passage 10 includes a forward flow passage a and a reverse flow passage B communicating with each other, and the reverse flow passage B is opposite to the refrigerant flow direction in the forward flow passage a. The forward flow passage A and the reverse flow passage B are communicated through a bend 13, and a refrigerant enters from the inlet mixing chamber 2, passes through the more than one stage of forward flow passage A and the more than one stage of reverse flow passage B and then flows out from the outlet mixing chamber 3. As shown in fig. 1, in the present embodiment, the flow channel 10 includes three forward flow channels a and two reverse flow channels B, and the forward flow channels a and the reverse flow channels B are alternately arranged.
The forward flow passage A comprises a first sudden shrinkage flow passage 11 and a first expansion flow passage 12 which are communicated with each other, the reverse flow passage B comprises a second sudden shrinkage flow passage 14 and a second expansion flow passage 15 which are communicated with each other, and the refrigerant enters from the inlet mixing chamber 2, sequentially passes through the first sudden shrinkage flow passage 11 and the first expansion flow passage 12, sequentially flows through the second sudden shrinkage flow passage 14 and the second expansion flow passage 15 through the bend 13, so that the refrigerant generates a hydraulic cavitation process in the flow passage 10 at intervals.
The refrigerant enters the refrigerant phase change cold plate 100 in a slightly supercooled state or a saturated state, and takes away heat of the heating element 7 in a supercooled boiling or saturated boiling manner. The flow velocity of the refrigerant in the inlet mixing cavity 1 is small, the cross section of the refrigerant is rapidly reduced after the refrigerant enters the first sudden shrinkage flow channel 11 from the inlet mixing cavity 2, the flow velocity of the refrigerant is rapidly increased, and cavitation bubbles are generated when the static pressure of the refrigerant is smaller than the steam pressure at the current temperature. When the refrigerant enters the first expanding flow channel 12, the pressure is recovered, and the high-speed micro-jet formed by the collapse of the cavitation bubbles strengthens the boiling heat exchange in the first expanding flow channel 12 and inhibits the polymerization of the small bubbles during boiling. When the refrigerant enters the curved passage 13, a streaming vortex generated by the curvature structure of the curved passage 13 induces a cavitation effect, and meanwhile, the refrigerant in a gas-liquid two-phase state passes through the second sudden contraction flow passage 14, and then passes through the second expansion flow passage 15 after static pressure reduction, cavitation bubbles, bubble fracture and disturbance and boiling enhancement, the static pressure of the refrigerant is sharply reduced along the main flow direction, and the resistance of bubbles generated during boiling in a counter-flow upward direction is increased. Meanwhile, large bubbles generated during boiling of the refrigerant are not easy to gather under the influence of cavitation bubble breakage, so that the flow pattern of the refrigerant passing through the reverse flow channel B is optimized, and boiling heat exchange is enhanced. In the reverse flow channel B, the bubbles are easy to gather in the conventional serpentine channel to form the blockage of the bubbles, thereby deteriorating the heat exchange and increasing the flow resistance.
The forward flow path a includes a first expanding flow path 12 having two or more expanding stages and communicating with each other in this order, and the width L of the first expanding flow path 12 is gradually increased in the direction from the first contracting flow path 11 to the curved path 13. The reverse flow path B includes second expanding flow paths 15 sequentially connected in an expanding order of two or more stages, and the width dimension L of the second expanding flow path 15 is gradually increased in a direction from the second contracting flow path 14 to the next curve 13. The expansion stages of the first expanded flow passage 12 in the forward flow passage a are the same as the expansion stages of the second expanded flow passage 15 in the reverse flow passage B. As shown in fig. 1, in the present embodiment, the forward flow path a includes a first expansion flow path 12 having two stages of expansion and communicating in sequence, and the reverse flow path B includes a second expansion flow path 15 having two stages of expansion and communicating in sequence.
An inlet (adopting a threaded hole) 4 is formed in the cold plate substrate 1, and the inlet 4 is communicated with the inlet mixing chamber 2. An outlet (adopting a threaded hole) 5 is also formed in the cold plate substrate 1, and the outlet 5 is communicated with the outlet mixing chamber 3. The size of the cavity cross section S1 of the outlet mixing cavity 3 is larger than that of the cavity cross section S2 of the inlet mixing cavity 2, and the size of the section of the outlet 5 is larger than that of the section of the inlet 4 (when the inlet 4 and the outlet 5 are both round holes, namely the aperture size a of the outlet 5 is larger than the aperture size b of the inlet 4), so as to ensure that the fluid carrying part of steam at the outlet 5 can rapidly pass through. Pressure and temperature sensors are respectively arranged in the inlet mixing cavity 2 and the outlet mixing cavity 3 to monitor instantaneous temperature, pressure and pressure difference fluctuation data of the refrigerant and adjust the inflow flow and temperature of the refrigerant according to the data.
The refrigerant phase change cold plate 100 described in embodiment 1 mills a flow channel 10 as shown in fig. 1 in the cold plate substrate 1, and the flow channel 10 adopts a mode of vertical ascending expansion flow, vertical descending expansion flow and 180-degree curve sudden contraction, so that the refrigerant generates a hydrodynamic cavitation process in the flow channel 10 at intervals.
Example 2
As shown in fig. 2 and 3, another embodiment of a refrigerant phase change cold plate for dissipating heat of a heating element 7 disposed thereon includes:
the device comprises a cold plate substrate 1, wherein an inlet mixing cavity 2, an outlet mixing cavity 3 and a flow channel 10 for communicating the inlet mixing cavity 2 and the outlet mixing cavity 3 are arranged on the cold plate substrate 1; a cover plate 6 arranged on the cold plate substrate 1 for sealing the flow passage 10, and a heating element 7 arranged on the cover plate 6, or arranged at the bottom of the cold plate substrate 1, or arranged on the cover plate 6 and the bottom of the cold plate substrate 1 on both sides.
The flow channel 10 comprises a forward flow channel a and a reverse flow channel B which are communicated with each other, the forward flow channel a and the reverse flow channel B are communicated through a bend 13, and a refrigerant enters from the inlet mixing chamber 2, passes through the forward flow channel a of more than one level and the reverse flow channel B of more than one level, and then flows out from the outlet mixing chamber 3. As shown in fig. 2, in the present embodiment, the flow channel 10 includes two forward flow channels a and one reverse flow channel B, and the forward flow channels a and the reverse flow channels B are alternately arranged.
The forward flow channel a includes the first expanding flow channel 12, the first large-scale flow channel 16, and a plurality of first micro-scale flow channels 17 (width dimension d) that are smaller than the width dimension c of the first large-scale flow channel 16. The converse flow channel B includes a second expanded flow channel 15, a second large-scale flow channel 19, and a plurality of second micro-scale flow channels 110 having a smaller size relative to the width of the second large-scale flow channel 19 (the sizes of the second large-scale flow channel 19 and the second micro-scale flow channels 110 can refer to the corresponding sizes of the first large-scale flow channel 16 and the first micro-scale flow channel 17 in fig. 2). One part of the refrigerant enters the first micro-scale flow channel 17 from the inlet mixing cavity 2 and flows into the first expansion flow channel 12 through the first micro-scale flow channel 17, and the other part of the refrigerant enters the first large-scale flow channel 16 from the inlet mixing cavity 2 and then enters the first expansion flow channel 12 through the injection hole 18 arranged on the first large-scale flow channel 16. One part of the refrigerant enters the second micro-scale flow channel 110 through the bend 13 and flows into the second expansion flow channel 15 through the second micro-scale flow channel 110, and the other part of the refrigerant enters the second large-scale flow channel 19 from the bend 13 and then enters the second expansion flow channel 15 through the injection hole 18 arranged on the second large-scale flow channel 19, so that the refrigerant is subjected to a gas-liquid separation process at intervals in the flow channel 10. Wherein the dimensions of the narrower first and second microscale flow channels 17 and 110, and the wider first and second macroscale flow channels 16 and 19, are defined based on the minimum pressure differential required for a bubble to enter the flow channels. Assuming that the width of a higher-level runner before flowing into a next-level runner is W and the width of the next-level runner is W, assuming that the depth of the runner is unchanged, the minimum pressure difference required by the bubbles entering the next-level runner is as follows:
ΔP=2γlg(1/w-1/W)
wherein Δ P is the minimum pressure difference, γlgTo working fluids employedGas-liquid surface energy per unit area. From the above formula, the smaller the size of the next stage flow channel is, the larger the required minimum pressure difference is, and when the pressure difference between the two ends of the bubble is smaller than the minimum value, the bubble cannot enter the flow channel, and the flow channel is called as a micro-scale flow channel. Also according to the above formula, the larger the size of the next-stage flow channel, the smaller the corresponding minimum pressure difference, and at this time, the easier the air bubbles enter the next-stage flow channel, which is called a large-scale flow channel.
The refrigerant enters the refrigerant phase change cold plate 100 in a slightly supercooled state or a saturated state, and takes away heat of the heating element 7 in a supercooled boiling or saturated boiling manner. When the coolant enters the first micro-scale flow channel 17 from the inlet mixing cavity 2, the flow rate rapidly rises, and when the static pressure of the coolant is smaller than the vapor pressure at the current temperature, cavitation bubbles are generated, and the hydrodynamic cavitation effect induced by the coolant passing through the first micro-scale flow channel 17 can strengthen the boiling heat exchange. On the other hand, when the gas phase in the refrigerant fluid approaches the narrow flow channel (i.e., the first microscale flow channel 17) on the right side of the forward flow channel a, since the surface energy of the bubbles increases when entering the narrow flow channel, it is necessary to apply work with a large pressure difference between the front and rear of the bubbles, and therefore the bubbles are difficult to enter the narrow flow channel and easily flow into the wide flow channel (i.e., the first microscale flow channel 16, i.e., the gas channel C in fig. 2) on the left side of the forward flow channel a. When the gas phase in the refrigerant approaches the first micro-scale flow channel 17, the gas phase is likely to flow into the first large-scale flow channel 16 because the surface energy of the cavitation bubbles increases when the cavitation bubbles enter the first micro-scale flow channel 17. The gas phase in the refrigerant enters the first macro-scale flow channel 16 and then reenters the first expanding flow channel 12 (i.e., the liquid channel D in fig. 2) located at the rear of the first micro-scale flow channel 17 through the injection hole 18. Due to the throttling effect of the first micro-scale flow passage 17, the pressure in the first expansion flow passage 12 is low, and the pressure in the first large-scale flow passage 16 is high, so that high-low pressure difference is formed at two sides of the injection hole 18, the gas phase speed passing through the injection hole 18 is accelerated, and the boiling bubbles in the first expansion flow passage 12 are impacted, thereby preventing the boiling bubbles from agglomerating into large bubbles blocking the flow passage. When the refrigerant enters the first expanding flow channel 12, the pressure is recovered, and the high-speed micro-jet formed by the collapse of the cavitation bubbles strengthens the boiling heat exchange in the first expanding flow channel 12 and inhibits the polymerization of the small bubbles during boiling. When the cold plate substrate 1 is vertically placed (at this time, the inlet 4 is located below, and the outlet 5 is located above), when a refrigerant enters the curved channel 13, gas-liquid phases are separated under the action of gravity and centrifugal force, a streaming vortex generated by a curvature structure of the curved channel 13 induces a cavitation effect, and meanwhile, after the refrigerant in a gas-liquid two-phase state enters the second expansion channel 15 through the second microscale channel 110 and the second macroscale channel 19, the static pressure of the refrigerant sharply decreases along the mainstream direction, the resistance of bubbles generated during boiling to the upstream becomes large, and meanwhile, large bubbles generated during boiling of the refrigerant are not easily gathered under the influence of cavitation bubble cracking, so that the flow pattern when the refrigerant passes through the reverse channel B is optimized, and boiling heat exchange is enhanced.
The first micro-scale flow channel 17 is communicated with the inlet mixing chamber 2 and is positioned on one side (shown as F in fig. 2) of the forward flow channel a close to the reverse flow channel B, and the first large-scale flow channel 16 is positioned on the other side (shown as E in fig. 2) of the forward flow channel a and is arranged adjacent to and side by side with the first micro-scale flow channel 17. One end of the first expanding flow channel 12 communicates with the first micro-scale flow channel 17, and the other end communicates with the curved channel 13. The second large-scale flow channel 19 communicates with the curved channel 13 and is located on one side (shown as F in fig. 2) of the reverse flow channel B close to the first expansion flow channel 12, and the second micro-scale flow channel 110 is provided on the other side (shown as E in fig. 2) of the reverse flow channel B and is arranged adjacent to and side by side with the second large-scale flow channel 19. One end of the second micro-scaled flow channel 110 communicates with the curved channel 13, and the other end communicates with the second expanding flow channel 15. When passing through the curved path 13, the liquid phase portion of the refrigerant is distributed to the outer side of the curved path 13 by the centrifugal force. The outer side in the first bend 13 (i.e., the bend 13 between the first expanding flow channel 12 and the second large-scale flow channel 19, the second micro-scale flow channel 110) is shown as E in fig. 2, and the inner side in the bend 13 is shown as F.
An inlet 4 is formed in the cold plate substrate 1, and the inlet 4 is communicated with the inlet mixing cavity 2. An outlet 5 is also formed in the cold plate substrate 1, and the outlet 5 is communicated with the outlet mixing cavity 3. The cavity cross section S1 of the outlet mixing chamber 3 is larger than the cavity cross section S2 of the inlet mixing chamber 2, and the cross-sectional dimension of the outlet 5 is larger than the cross-sectional dimension of the inlet 4 (when the inlet 4 and the outlet 5 are both circular holes, i.e., the aperture dimension a of the outlet 5 is larger than the aperture dimension b of the inlet 4). Pressure and temperature sensors are uniformly arranged in the inlet mixing cavity 2 and the outlet mixing cavity 3 to monitor instantaneous temperature, pressure and pressure difference fluctuation data of the refrigerant, and the inflow flow and temperature of the refrigerant can be adjusted according to the data.
In embodiment 2, the flow channels 10 shown in fig. 2 are milled in the cold plate substrate 1, and at the inlets of each of the vertical forward flow channel and the vertical downward flow channel, the gas-liquid two-phase is separated by the flow channels with larger and smaller dimensions under the action of surface energy, and the gas-liquid two-phase can also be naturally separated under the action of centrifugal force when passing through the curved channel 13.
In the embodiments 1 and 2 of the present invention, the cold plate substrate 1 may be placed vertically (in this case, the inlet 4 is located below, and the outlet 5 is located above), or may be placed horizontally. However, when the cold plate base plate 1 is vertically arranged, the action effect of hydrodynamic cavitation or gas-liquid separation effect is better due to the factor of gravity.
The refrigerant phase change cold plate described in embodiments 1 and 2 reduces the difference in two-phase flow pattern between the forward flow channel a and the reverse flow channel B by designing the multi-scale flow channel 10 in the cold plate and utilizing the hydrodynamic cavitation effect or the gas-liquid separation effect thereof, reduces the gas-liquid two-phase flow resistance, improves the distribution of the gas phase and the liquid phase on the heat exchange surface, and improves the uniformity and stability of the temperature distribution on the heat exchange surface. Based on the regulation and control of the two-phase flow pattern: under the conditions of low dryness and low heat flow, a stable vaporization core is formed by virtue of cavitation bubbles induced by the cavitation structure, so that the boiling evaporation process is kept stable; when the high-dryness and high-heat flow exist, the bubbles are prevented from flowing reversely upstream by virtue of the characteristic that the cavitation structure has a narrow inlet and a wide outlet, and the bubbles are prevented from gathering by virtue of high-pressure microjet impact formed by annihilation of the bubbles, so that the flow instability can be greatly reduced, and the limit of heat dissipation power density can be improved. The embodiment 2 also carries out deformation on the basis of a hydrodynamic cavitation structure, realizes gas-liquid two-phase separation by utilizing the surface energy and the centrifugal force action of a curve, and further improves the flow characteristic of two-phase flow. The specific embodiment of the invention leads the boiling starting point in the refrigerant phase change cold plate to be advanced, and stabilizes the boiling heat exchange process; the bubble counter flow in the descending flow in the refrigerant phase change cold plate can be prevented, and the flowing stability is improved; the bubble aggregation is prevented by utilizing the cavitation annihilation effect induced by the sudden expansion structure, and the critical heat flux density of boiling heat exchange is improved; the gas-liquid separation effect is utilized, so that the heat exchange surface is more easily wetted by a liquid phase, and the heat exchange capacity of the refrigerant phase change cold plate is improved.
By implementing the technical scheme of the refrigerant phase change cold plate described in the specific embodiment of the invention, the following technical effects can be achieved:
(1) the refrigerant phase change cold plate described in the specific embodiment of the invention can reduce the difference of two-phase flow patterns between the forward flow channel and the reverse flow channel by designing a multi-scale flow channel in the cold plate and utilizing the hydrodynamic cavitation effect or the gas-liquid separation effect of the cold plate, reduce the flow resistance of gas-liquid two phases, improve the distribution of gas-liquid phases on the heat exchange surface and improve the uniformity and the stability of the temperature distribution of the heat exchange surface;
(2) the refrigerant phase change cold plate described in the specific embodiment of the invention can effectively solve the problem of instability of flowing boiling by virtue of the hydrodynamic cavitation effect, the starting of boiling can be advanced by virtue of the hydrodynamic cavitation effect, the superheat degree is reduced, large bubbles can be broken by virtue of cavitation bubble bursting, and the problem of instability of boiling can be reduced;
(3) the refrigerant phase change cold plate described in the specific embodiment of the invention can effectively solve the problem of two-phase flow pattern distribution based on the gas-liquid separation effect, and by utilizing the effect, the gas-liquid two-phase separation can be realized by arranging the multi-scale flow channel; the separated steam becomes high-speed steam flow through the jet holes, large bubbles generated by boiling in the liquid channel can be further broken, the flow resistance is favorably reduced, and the wetting of a heat exchange surface with higher heat flow density is also favorably realized.
The embodiments in the present description are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other.
The foregoing is merely a preferred embodiment of the invention and is not intended to limit the invention in any manner. Although the present invention has been described with reference to the preferred embodiments, it is not intended to be limited thereto. Those skilled in the art can make many possible variations and modifications to the disclosed embodiments, or equivalent modifications, without departing from the spirit and scope of the invention, using the methods and techniques disclosed above. Therefore, any simple modification, equivalent replacement, equivalent change and modification made to the above embodiments according to the technical essence of the present invention are still within the protection scope of the technical solution of the present invention.

Claims (14)

1. The utility model provides a refrigerant phase transition cold plate, dispels the heat for heating element (7) that set up on it, its characterized in that includes:
the device comprises a cold plate substrate (1), wherein an inlet mixing cavity (2), an outlet mixing cavity (3) and a flow channel (10) for communicating the inlet mixing cavity (2) and the outlet mixing cavity (3) are arranged on the cold plate substrate (1);
the cover plate (6) is arranged on the cold plate substrate (1) and used for sealing the flow channel (10), and the heating element (7) is arranged on the cover plate (6) and/or the cold plate substrate (1);
the flow channel (10) comprises a forward flow channel (A) and a reverse flow channel (B) which are communicated with each other, the forward flow channel (A) and the reverse flow channel (B) are communicated through a bend (13), a refrigerant enters from the inlet mixing cavity (2), passes through the forward flow channel (A) with more than one stage and the reverse flow channel (B) with more than one stage, and then flows out from the outlet mixing cavity (3);
the forward flow passage (A) comprises a first projecting flow passage (11) and a first expanding flow passage (12) which are communicated with each other, and the reverse flow passage (B) comprises a second projecting flow passage (14) and a second expanding flow passage (15) which are communicated with each other; a refrigerant enters from the inlet mixing cavity (2), sequentially passes through the first sudden shrinkage flow channel (11) and the first expansion flow channel (12), sequentially passes through the second sudden shrinkage flow channel (14) and the second expansion flow channel (15) through the bend (13), and is subjected to a hydrodynamic cavitation process at intervals in the flow channel (10);
when the refrigerant enters the bend (13), a streaming vortex generated by a curvature structure of the bend (13) induces a cavitation effect, meanwhile, the refrigerant in a gas-liquid two-phase state passes through the second sudden shrinkage flow channel (14), and passes through a second expansion flow channel (15) after static pressure reduction, cavitation bubbles, bubble fracture and disturbance and boiling enhancement, the static pressure of the refrigerant is sharply reduced along the main flow direction, the resistance of bubbles generated during boiling in a countercurrent upward mode is increased, and meanwhile, large bubbles generated during boiling of the refrigerant are not easy to gather under the influence of the cavitation bubble fracture, so that the flow pattern of the refrigerant passing through the countercurrent flow channel (B) is optimized, and boiling heat exchange is enhanced.
2. The refrigerant phase change cold plate as claimed in claim 1, wherein: when the refrigerant enters the first sudden shrinkage flow channel (11) from the inlet mixing cavity (2), the cross section is rapidly reduced, the flow velocity of the refrigerant is rapidly increased, and cavitation bubbles are generated when the static pressure of the refrigerant is smaller than the steam pressure at the current temperature; when the refrigerant enters the first expanding flow channel (12), the pressure is recovered, and the high-speed micro jet formed by the collapse of the cavitation bubbles strengthens the boiling heat exchange in the first expanding flow channel (12) and inhibits the polymerization of small bubbles during boiling.
3. The refrigerant phase change cold plate as claimed in claim 1 or 2, wherein: the forward flow channel (A) comprises a first expansion flow channel (12) with more than two expansion stages which are sequentially communicated, and the width dimension (L) of the first expansion flow channel (12) is gradually increased along the direction from the first sudden shrinkage flow channel (11) to the bend (13); the reverse flow channel (B) comprises a second expansion flow channel (15) with more than two expansion stages which are communicated in sequence, and the width dimension (L) of the second expansion flow channel (15) is gradually increased along the direction from the second sudden shrinkage flow channel (14) to the next bend (13).
4. The refrigerant phase change cold plate as claimed in claim 3, wherein: the expansion stage number of the first expansion flow channel (12) in the forward flow channel (A) is the same as that of the second expansion flow channel (15) in the reverse flow channel (B).
5. The refrigerant phase change cold plate as claimed in claim 1, 2 or 4, wherein: the refrigerant enters the refrigerant phase change cold plate (100) in a micro-supercooling state or a saturation state, and the heat of the heating element (7) is taken away in a supercooling boiling or saturation boiling mode.
6. The refrigerant phase change cold plate as claimed in claim 5, wherein: an inlet (4) is formed in the cold plate substrate (1), and the inlet (4) is communicated with the inlet mixing cavity (2); an outlet (5) is further formed in the cold plate substrate (1), and the outlet (5) is communicated with the outlet mixing cavity (3); the cavity cross-sectional dimension of the outlet mixing cavity (3) is larger than that of the inlet mixing cavity (2), and the section dimension of the outlet (5) is larger than that of the inlet (4).
7. The refrigerant phase change cold plate as claimed in claim 1, 2, 4 or 6, wherein: pressure and temperature sensors are arranged in the inlet mixing cavity (2) and the outlet mixing cavity (3) respectively to monitor instantaneous temperature, pressure and pressure difference fluctuation data of the refrigerant, and the inflow flow and temperature of the refrigerant can be adjusted according to the data.
8. The utility model provides a refrigerant phase transition cold plate, dispels the heat for heating element (7) that set up on it, its characterized in that includes:
the device comprises a cold plate substrate (1), wherein an inlet mixing cavity (2), an outlet mixing cavity (3) and a flow channel (10) for communicating the inlet mixing cavity (2) and the outlet mixing cavity (3) are arranged on the cold plate substrate (1);
the cover plate (6) is arranged on the cold plate substrate (1) and used for sealing the flow channel (10), and the heating element (7) is arranged on the cover plate (6) and/or the cold plate substrate (1);
the flow channel (10) comprises a forward flow channel (A) and a reverse flow channel (B) which are communicated with each other, the forward flow channel (A) and the reverse flow channel (B) are communicated through a bend (13), a refrigerant enters from the inlet mixing cavity (2), passes through the forward flow channel (A) with more than one stage and the reverse flow channel (B) with more than one stage, and then flows out from the outlet mixing cavity (3);
the forward flow channel (A) comprises a first expansion flow channel (12), a first large-scale flow channel (16) and a plurality of first micro-scale flow channels (17) with smaller width sizes relative to the first large-scale flow channel (16); the reverse flow channel (B) comprises a second expansion flow channel (15), a second large-scale flow channel (19) and a plurality of second micro-scale flow channels (110) with smaller width dimension relative to the second large-scale flow channel (19); one part of the refrigerant enters the first micro-scale flow channel (17) from the inlet mixing cavity (2), and flows into the first expansion flow channel (12) through the first micro-scale flow channel (17), and the other part of the refrigerant enters the first large-scale flow channel (16) from the inlet mixing cavity (2), and then enters the first expansion flow channel (12) through a jet hole (18) arranged on the first large-scale flow channel (16); one part of the refrigerant enters the second micro-scale flow channel (110) through the bend (13) and flows into the second expansion flow channel (15) through the second micro-scale flow channel (110), the other part of the refrigerant enters the second large-scale flow channel (19) from the bend (13) and then enters the second expansion flow channel (15) through the injection hole (18) arranged on the second large-scale flow channel (19), so that the refrigerant is subjected to a gas-liquid separation process in the flow channel (10) at intervals.
9. The refrigerant phase change cold plate as claimed in claim 8, wherein: when the refrigerant enters the first micro-scale flow channel (17) from the inlet mixing cavity (2), the flow rate rapidly rises, when the static pressure of the refrigerant is smaller than the vapor pressure at the current temperature, cavitation bubbles are generated, and the hydrodynamic cavitation effect induced by the refrigerant passing through the first micro-scale flow channel (17) can strengthen boiling heat exchange; when the gas phase in the refrigerant is close to the first micro-scale flow channel (17), the gas phase is easy to flow into the first large-scale flow channel (16) due to the fact that the surface energy of cavitation bubbles is increased when the cavitation bubbles enter the first micro-scale flow channel (17); the gas phase in the refrigerant enters the first large-scale flow channel (16) and then reenters the first expansion flow channel (12) positioned at the rear part of the first micro-scale flow channel (17) through the injection hole (18); due to the throttling effect of the first micro-scale flow channel (17), the pressure in the first expansion flow channel (12) is low, the pressure in the first large-scale flow channel (16) is high, so that high-low pressure difference is formed on two sides of the jet hole (18), the speed of a gas phase passing through the jet hole (18) is increased, boiling bubbles in the first expansion flow channel (12) are impacted, and the boiling bubbles are prevented from being agglomerated into large bubbles blocking the flow channel; when the refrigerant enters the first expanding flow channel (12), the pressure is recovered, and the high-speed micro jet formed by the collapse of the cavitation bubbles strengthens the boiling heat exchange in the first expanding flow channel (12) and inhibits the polymerization of small bubbles during boiling.
10. The refrigerant phase change cold plate as claimed in claim 9, wherein: when the refrigerant enters the bend (13), gas-liquid phases are separated under the action of gravity and centrifugal force, a streaming vortex generated by a curvature structure of the bend (13) induces cavitation effect, meanwhile, after the refrigerant in the gas-liquid two-phase state enters the second expansion flow channel (15) through the second micro-scale flow channel (110) and the second large-scale flow channel (19) respectively, the static pressure of the refrigerant is sharply reduced along the main flow direction, the resistance of bubbles generated during boiling in a counter-flow and upward direction is increased, and meanwhile, large bubbles generated during boiling of the refrigerant are not easy to gather under the influence of cavitation bubble breakage, so that the flow pattern of the refrigerant passing through the counter-flow channel (B) is optimized, and boiling heat exchange is enhanced.
11. The refrigerant phase change cold plate as claimed in claim 8, 9 or 10, wherein: the first micro-scale flow channel (17) is communicated with the inlet mixing cavity (2) and is positioned on one side, close to the reverse flow channel (B), in the forward flow channel (A), and the first large-scale flow channel (16) is positioned on the other side in the forward flow channel (A) and is adjacent to and arranged side by side with the first micro-scale flow channel (17); one end of the first expansion flow channel (12) is communicated with the first microscale flow channel (17), and the other end of the first expansion flow channel is communicated with the bend (13); the second large-scale flow channel (19) is communicated with the bend (13) and is positioned at one side, close to the first expansion flow channel (12), in the reverse flow channel (B), and the second micro-scale flow channel (110) is arranged at the other side in the reverse flow channel (B) and is adjacent to and arranged side by side with the second large-scale flow channel (19); one end of the second micro-scale flow channel (110) is communicated with the bend (13), and the other end of the second micro-scale flow channel is communicated with the second expansion flow channel (15); when the refrigerant passes through the bend (13), the liquid phase part of the refrigerant is distributed on the outer side in the bend (13) under the action of centrifugal force.
12. The refrigerant phase change cold plate as claimed in claim 11, wherein: the refrigerant enters the refrigerant phase change cold plate (100) in a micro-supercooling state or a saturation state, and the heat of the heating element (7) is taken away in a supercooling boiling or saturation boiling mode.
13. A refrigerant phase change cold plate as claimed in claim 8, 9, 10 or 12, wherein: an inlet (4) is formed in the cold plate substrate (1), and the inlet (4) is communicated with the inlet mixing cavity (2); an outlet (5) is further formed in the cold plate substrate (1), and the outlet (5) is communicated with the outlet mixing cavity (3); the cavity cross-sectional dimension of the outlet mixing cavity (3) is larger than that of the inlet mixing cavity (2), and the section dimension of the outlet (5) is larger than that of the inlet (4).
14. The refrigerant phase change cold plate as claimed in claim 13, wherein: pressure and temperature sensors are arranged in the inlet mixing cavity (2) and the outlet mixing cavity (3) respectively to monitor instantaneous temperature, pressure and pressure difference fluctuation data of the refrigerant, and the inflow flow and temperature of the refrigerant can be adjusted according to the data.
CN201710961842.7A 2017-10-16 2017-10-16 Refrigerant phase change cold plate Active CN109671688B (en)

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