WO2018137503A1

WO2018137503A1 - Heat transfer method and heat transfer system based on heat-pressure conversion effect

Info

Publication number: WO2018137503A1
Application number: PCT/CN2018/072434
Authority: WO
Inventors: 姜玉雁; 李铁; 李玉华; 袁达忠; 李志刚; 王涛
Original assignee: 中国科学院工程热物理研究所
Priority date: 2017-01-25
Filing date: 2018-01-12
Publication date: 2018-08-02
Also published as: CN106839840B; CN106839840A

Abstract

A heat transfer method and heat transfer system based on a heat-pressure conversion effect. The method comprises: selecting a heat conducting working medium that meets a requirement of 1.0 kPa/°C according to a determined working temperature interval; then, filling a certain quantity of heat conducting working medium into a closed circulation loop with sufficient rigidity, so that the liquid volume of the heat conducting working medium accounts for 60% to 99% of the total volume of the entire closed circulation loop under the working temperature, ensuring that the interior of the closed circulation loop is basically in a full liquid state; and a liquid heat conducting working medium of a heating end (12) producing thermal expansion due to heating, and forming a pressure wave, wherein the pressure wave produces a compression action on the liquid working medium, and drives the liquid working medium to recirculate, so as to continuously maintain the heat-pressure conversion effect. Stronger and faster heat transfer over ordinary heat pipes can be realized, and an equivalent thermal conductivity coefficient can be up to 50 to 150 kW/ m. K, and the structure design is free and less affected by the gravity overload.

Description

Heat transfer method and heat transfer system based on hot pressing conversion effect

Technical field

The present disclosure relates to the field of high efficiency heat transfer technology, and in particular to a heat transfer method and a heat transfer system based on a hot press conversion effect.

Background technique

With the development of modern high-tech, the rapid development of new energy technologies, energy-saving emission reduction, advanced manufacturing technology and emerging science and technology make heat and mass transfer technology face new challenges and difficulties, solving high heat flux heat dissipation and efficient heat transfer. The problem has highlighted its importance. The thermal load per unit area of many devices is increasing, such as: large computers, power electronics, power equipment, heat dissipation of optoelectronic components, reactor heat transfer, thermal protection of spacecraft, aero-engines and gas turbines, high-power micro-powered machinery , MW-class magnetrons, heat transfer of micro-sized gas turbines, etc., and in these places with high heat load, it is often required to install compact devices and strict cooling temperature requirements, which puts high demands on heat-dissipation technology and equipment. The problem of heat dissipation has also become a bottleneck restricting the development of such industries.

In the prior art, there are some advanced active heat transfer technologies, including spray cooling, impinging jet cooling, microchannel mobile phase change cooling technology, and the like. Since active cooling technology requires the configuration of an external drive, there are disadvantages in terms of system complexity, reliability, operating cost, and convenience. The microchannel liquid forced convection cooling method has strong cooling capacity, small thermal resistance, and is not affected by gravity and direction. However, due to the small size of the flow channel, the system has large pressure drop, large temperature gradient, easy scaling, and blockage. In addition, the technology is extremely demanding on the performance of various micro-pumps.

Heat pipe is a commonly used passive (self-driven) efficient heat transfer technology. Due to the inherent mechanism of phase change and reflow, the traditional heat pipe is limited by the azimuth and length. It is greatly affected by gravity and acceleration. In application, the structural design The degree of freedom is low, making it difficult to make a more complex system. However, the working range of the pulsating heat pipe is narrow, and it is difficult to start, and it is difficult to adapt to changes in the heat load, and the application range is limited.

The existing heat pipe is known to attempt to bring the working medium to a supercritical state, and heat transfer is performed by a pressure wave. Although the heat transfer performance is good, the pressure resistance of the casing is high, and latent heat cannot be utilized.

Public content

The purpose of the present disclosure is to overcome various drawbacks of the existing heat pipe, and provide a heat transfer method and a heat transfer system based on the hot press conversion effect, which can realize stronger heat transfer than the ordinary heat pipe, and the structure design is free. It is less affected by gravity overload.

According to an aspect of the present disclosure, there is provided a heat transfer method based on a hot press conversion effect, comprising the steps of: step S101: providing a heat transfer system, the heat transfer system being a closed loop having a heating end and a cooling end Step S201: determining a working temperature interval and selecting a heat conductive working medium, so that a change of the corresponding working fluid pressure of the heat conductive working medium in the working temperature interval is greater than or equal to a preset value; and step S301: a closed cycle to the heat transfer system Filling the heat transfer medium in the circuit, the ratio of the volume of the liquid heat transfer medium to the total volume of the closed circulation circuit is in a preset range; step S401: the heating end of the heat transfer system is in close contact with the heat source, and the heat transfer system is The cooling end is in contact with a cold source or dissipates heat to the environment.

In some embodiments of the present disclosure, the preset value is 1.0 kPa/° C., so that the heat conductive medium is in a gas-liquid two-phase coexistence state within the working temperature range.

In some embodiments of the present disclosure, the predetermined range is from 60% to 99%.

In some embodiments of the present disclosure, in the step S301,

The filling quality of the heat transfer medium is determined by the following formula:

m=ρ ₁ V ₁ +ρ _g (VV ₁ )

Where m is the thermal mass of the working fluid, the unit is kg;

V is the total volume of the closed loop, in units of m ³ ;

V ₁ is the working liquid temperature T ₁ , the liquid volume of the heat transfer medium in the closed circulation loop, V ₁ = (60% ~ 99%) V, the unit is m ³ , T ₁ is the working temperature, and the charging is performed. When the mass is calculated, the value is taken as the average value of the highest temperature and the lowest temperature in the working temperature range, and the unit is °C;

ρ ₁ is the density of the saturated liquid heat transfer working medium at the working temperature T ₁ , and the unit is kg/m ³ ,

ρ _g is the density of the saturated gaseous heat transfer medium at the working temperature T ₁ in units of kg/m ³ .

In some embodiments of the present disclosure, in the step S401, the liquid heat transfer medium of the heating end is thermally expanded by heat to form a pressure wave, and the pressure wave presses the liquid heat conductive medium to drive the liquid heat transfer medium circulation. The flow flows to the cooling end to dissipate heat and then flows to the heating end, so that the cycle is performed to maintain the hot-pressure conversion effect.

In some embodiments of the present disclosure, the preset value is 2.7 kPa/° C.

In some embodiments of the present disclosure, the predetermined range is from 75% to 90%.

In some embodiments of the present disclosure, the thermally conductive working medium is selected from the group consisting of water, acetone, methanol, ethanol, refrigerant, carbon dioxide, ammonia, thermal conductivity, NaK alloy, potassium, sodium, and lithium according to the operating temperature interval. One or more of them.

According to another aspect of the present disclosure, there is provided a heat transfer system using the above heat transfer method to effect a hot press conversion effect, comprising a heating end in contact with a heat source, a cooling end in contact with a heat source or a heat sinking to the environment; The heating end and the cooling end are connected by at least two connecting passages, and the heating end, the cooling end and the connecting passage are all rigid components, and together form a closed loop.

In some embodiments of the present disclosure, the material of the rigid member is selected from any one of copper, copper alloy, aluminum, aluminum alloy, titanium alloy, nickel-based superalloy, and steel.

In some embodiments of the present disclosure, the heating end or the cooling end are each formed in the form of a serpentine tube, a tube row, or a plate channel.

In some embodiments of the present disclosure, the connecting channel is selected from any of an elliptical channel, a curved channel, and an inflation channel.

In some embodiments of the present disclosure, the closed loop is a single channel loop.

In some embodiments of the present disclosure, the closed loop is a multi-channel parallel loop.

In some embodiments of the present disclosure, a liquid storage device is disposed on the connecting passage, and the liquid filling amount in the closed circulation circuit is adjusted by an opening and closing valve.

In some embodiments of the present disclosure, an auxiliary pumping device is provided on the connecting passage.

The beneficial effects of the present disclosure include:

(1) The heat transfer method and system of the present disclosure is a novel passive heat transfer system developed on the basis of a heat pipe, which converts thermal energy into pressure wave by using a sharp expansion effect of a liquid working medium under a specific thermodynamic state. It is called the hot press conversion effect. Due to the large velocity of the pressure wave and the rapid heating effect, the hot-pressure conversion heat transfer system transfers heat faster and responds more quickly than the ordinary heat pipe.

(2) The hot-pressure conversion effect is also combined with other heat transfer effects. There is usually a triple heat transfer effect superposition in the hot-pressure conversion heat transfer system, namely hot-pressure conversion, local phase change, convective heat transfer, and therefore the ability to transfer heat load. Or the equivalent thermal conductivity is superior to the ordinary heat pipe. The equivalent thermal conductivity of the ordinary heat pipe generally does not exceed 20 kW/m·K, and the equivalent thermal conductivity of the heat transfer system of the present disclosure reaches 50-150 kW/m·K.

(3) Due to the expansion of the heating end, a pressure gradient can be formed in the closed circulation loop to drive the fluid to generate convection. The heat-pressure conversion heat transfer system is more capable of adapting to gravity changes than the heat pipe solely relying on gravity, so even Large angles or horizontal placement still work well.

(4) Since the pressure wave has a strong driving convection effect, the hot-pressure conversion heat transfer circuit has a greater degree of freedom, and may be a complicated multi-circuit, parallel circuit or long circuit.

DRAWINGS

The drawings are intended to provide a further understanding of the disclosure, and are in the In the drawing:

1 is a waveform diagram of pressure waves in a fluid measured in an embodiment of the present disclosure;

2 is a graph showing the effect of hot-pressure conversion of a superheated liquid obtained by a compressible fluid computer simulation in the embodiment of the present disclosure; wherein (a) is a transient pressure wave distribution in the loop, and (b) is a pressure at a point in the loop. Fluctuation (local time change);

3 is a schematic structural view of a heat transfer system of a hot press conversion effect according to an embodiment of the present disclosure;

4 is a flow chart of a heat transfer method of a hot press conversion effect of an embodiment of the present disclosure;

Figure 5 is a saturation graph of R134a;

Figure 6 is a graph of equivalent thermal conductivity measured by the present disclosure;

7 is a schematic structural view of a heating end and a cooling end of an embodiment of the present disclosure;

8 is a schematic structural view of a connection channel according to an embodiment of the present disclosure;

9 is a schematic structural view of a heat-pressure conversion heat transfer system having a liquid storage device according to an embodiment of the present disclosure;

Figure 10 is a schematic view showing the structure of a heat-pressure conversion heat transfer system having an auxiliary pumping device according to an embodiment of the present disclosure.

【Symbol Description】

11-connection channel; 12-heating end; 13-cooling end; 14-valve; 15--liquid storage device; 16-assisted pumping device; 21-coil tube form heating end/cooling end; 22-tube row heating End/cooling end; 23-plate-like channel form heating end/cooling end; 310-elliptical member body; 31-elliptical channel; 320-cuboid-shaped member body; 32-bend channel; 330-sheet metal member body; 33- Inflatable channel.

detailed description

The present disclosure provides a heat transfer method and a heat transfer system based on a hot press conversion effect. The heat transfer method and system use a heat transfer conversion principle to transfer heat, and the hot press conversion principle is as follows:

The energy transfer equation for compressible fluids is:

(1) where E is internal energy,

For the velocity vector, p is the pressure, λ is the thermal conductivity, T is the temperature, and Φ is the net heat flowing into the system.

For the differentiation of internal energy versus time, grad is the gradient vector and div is the scatter operator.

The formula (1) is converted into the following form according to the thermodynamic relationship:

(2) where α _v is the coefficient of thermal expansion, ρ is the density, and C _p is the specific heat capacity.

For the divergence operator, the remaining symbols are the same as (1).

When α _{v is} large, a large pressure change occurs in the heat transfer medium due to the temperature change, and the pressure change can be utilized for energy transfer, that is, heat energy transfer. When the heat transfer working liquid accounts for 60 to 99% of the entire closed loop, that is, the full liquid state, high-efficiency conversion of heat energy and pressure waves can be realized, thereby realizing high-density heat energy transfer.

In the closed loop circuit, the heat transfer working fluid in the boundary layer of the heating part expands due to heat, and has a squeezing effect on the surrounding heat transfer working fluid, forming a pressure wave, and the pressure wave is again in the heat transfer working fluid in the circuit at the speed of sound. Rapidly spread, absorbed by the heat transfer working fluid along the way into heat energy, the temperature of the heat transfer working fluid is raised as a whole, forming a so-called piston effect, also known as fluid heating effect (Thermolization), forming a temperature difference at the cold end, making heat conduction The heat of the working fluid is taken away by the cold end.

Taking R134a as the heat transfer working medium, the experimentally measured pressure wave waveform is shown in Fig. 1. The formation and propagation process of the pressure wave can be captured by the numerical calculation of the compressible fluid, as shown in Fig. 2, and the waveform is stepped.

The present disclosure will be further described in detail below with reference to the specific embodiments thereof and the accompanying drawings.

Based on the above principle of hot press conversion effect, embodiments of the present disclosure provide a heat transfer method that utilizes a heat transfer system to achieve heat transfer of a hot press conversion effect.

First, the heat transfer system is introduced. As shown in FIG. 3, the heat transfer system includes: a heating end 12, a cooling end 13, and a heating end 12 and a cooling end 13 communicated by at least two connecting passages 11, the heating end 12. The cooling end 13 and the connecting passage 11 together form a closed loop, and the components forming the closed loop are rigid members, that is, the heating end 12, the cooling end 13 and the connecting passage 11 are rigid members.

Since the occurrence of the hot-pressing effect needs to meet certain conditions, if the heat transfer system is open, or the rigidity of the closed loop is insufficient, the pressure wave cannot be repeatedly propagated in the fluid circuit, and the hot pressing effect cannot cause the heating effect, so Nor can it form heat transfer capacity. The closed loop structure adopted in the present disclosure, and the component forming the closed loop is a rigid component, which is sufficient to withstand the working pressure of the heat transfer medium, so that the pressure wave generated by the heat transfer working fluid can repeatedly propagate to form a heating effect. The rigid member is generally a metal material selected from the group consisting of copper, copper alloy, aluminum, aluminum alloy, titanium alloy, nickel-based superalloy, steel, and the like.

As shown in FIG. 4, the heat transfer method of this embodiment includes the following steps:

Step S101: Providing a heat transfer system as shown in FIG. 3, the heat transfer system is a closed loop having a heating end and a cooling end.

Step S201: determining a working temperature interval and selecting a heat transfer working medium.

In this step, an operating temperature interval T is determined. In one example, the operating temperature interval T is -40 ° C ≤ T ≤ 100 ° C, and the heat transfer medium is selected from R134a. As shown in FIG. 5, the change of the corresponding working fluid pressure P of R134a in the working temperature range at this time can satisfy:

And R134a is in a gas-liquid two-phase coexistence state in the working temperature interval T, and the temperature difference forms a pressure difference sufficient to drive the heat-conducting working fluid to flow against the flow resistance of the circuit. In another example, the working temperature interval T is 80 ° C ≤ T ≤ 360 ° C, the heat transfer medium selects water, and the water is in a gas-liquid two-phase coexistence state in the working temperature interval T, and the temperature difference forms a pressure difference sufficient to drive The thermally conductive working fluid flows against the flow resistance of the circuit.

Step S301: filling the heat transfer working medium into the closed circulation loop of the heat transfer system.

In this step, the filling quality of the heat transfer working medium is determined by the following formula:

m=ρ ₁ V ₁ +ρ _g (VV ₁ ) (3)

Where m is the thermal mass of the working fluid, the unit is kg;

V is the total volume of the closed loop, in units of m ³ ;

V ₁ is the working liquid temperature T ₁ , the liquid volume of the heat transfer working medium in the closed loop circuit, so that the heat conductive working fluid can flow along the circuit during operation, or the heat conductive working gas proportions do not block the heat conductive medium The flow of liquid along the circuit is prevailing. V _{1 is} specifically selected as V ₁ = (60% ~ 99%) V, and the unit is m ³ , so that the internal liquid heat conductive working medium is maintained at 60% to 99%; T ₁ is the working temperature. When performing the filling quality calculation, the value is taken as the average value of the highest temperature and the lowest temperature of the working temperature interval T, and the unit is °C;

Step S401: The heating end of the heat transfer system is in close contact with the heat source, and the cooling end of the heat transfer system is in contact with the cold source or dissipates heat to the environment.

In this step, the liquid heat transfer medium of the heating end is thermally expanded by heat to form a pressure wave, and the pressure wave presses the liquid heat conductive medium to drive the liquid heat conductive medium to circulate and flow to the cooling end to dissipate heat and then flow to The heating end is circulated so that the hot press conversion effect is continuously maintained.

In the heat transfer method provided by the embodiment, if the heating end is continuously heated, the liquid heat transfer medium may enter the overheated state away from the saturated state, and the high heat transfer state will be removed. Only at the working temperature, the liquid heat conductive medium occupies the entire closed state. The hot-pressure conversion effect will continue in the range of 60% to 99% of the total volume of the circulation loop. The present disclosure selects a suitable heat transfer medium to make the change of the corresponding working medium pressure P of the heat conductive medium in the working temperature range satisfy:

That is, the heat transfer medium used is required to generate a large pressure difference under a small temperature change, and the temperature difference forms a pressure difference sufficient to drive the fluid to flow against the flow resistance of the circuit. When the heat transfer system forms a closed loop, the hot pressure wave at the heating end has a compressive action on the fluid heat transfer medium, and a pressure gradient is formed in the loop, so that the liquid heat transfer medium can be driven to perform the circulating flow, and the liquid heat transfer medium of the heating portion is heated. It is taken away to avoid superheated vaporization due to long-term residence. At the same time, the liquid heat transfer medium replenished from the cold end is nearly saturated, and can quickly enter the high-efficiency hot-pressure conversion state. In this cycle, the continuous hot-pressing effect is maintained.

The larger the pressure gradient is, the better the self-circulation effect is, and the more obvious the heat transfer phenomenon is.

Similarly, since the gas phase can strongly attenuate the pressure wave, if the liquid heat transfer medium in the circuit accounts for a small proportion, the gas phase space is large, and the heating effect is not formed, the present disclosure is to make the heat conductive medium at the working temperature. In the interval, the internal liquid heat transfer medium maintains a state of 60% to 99%, so that the liquid heat transfer medium is basically in a full liquid state, and when calculating according to the calculation formula, V ₁ = (60% to 99%) V is selected. Ensure that the hydraulic transfer heat transfer system works properly. In the range selected by the liquid working medium, the higher the volume ratio of the liquid working medium, the more obvious the hot heat transfer phenomenon.

In addition to thermal expansion, the heating part under high pressure will also have a partial boiling phenomenon and produce tiny boiling bubbles. The tiny boiling bubbles will pass through the phase change subtropical heat while generating pressure waves during the growth process, forming a hot-pressure conversion effect. Therefore, the heat transfer effect of the hot press conversion system during normal operation is generally superposed by three effects of hot press conversion, local phase change and loop convection.

Compared with the normal loop heat pipe, the liquid filling rate is less than 50%. In contrast, the hot-pressure conversion heat transfer system is basically in a full-liquid state, and the phase change effect is not obvious. Instead, the hot-pressure conversion effect and the local expansion pressure are replaced. The convection effect of the drive. Therefore, the present disclosure is superior to ordinary heat pipes regardless of the ability to transfer heat load or the equivalent thermal conductivity.

Figure 6 is an experimental test result of a heat-transfer heat transfer system using R134a as a heat-conducting working medium. It can be seen from the figure that with the increase of liquid filling amount, only a small heat supply is required, and the equivalent of the heat transfer system. The thermal conductivity can be very high. For example, when the liquid filling amount reaches 91%, the equivalent thermal conductivity of the heat transfer system is about 150 kW/m·K even if the heat input is below 100 W. The heat transfer performance of the heat transfer system is significantly higher than that of ordinary heat pipes. The equivalent thermal conductivity of a conventional heat pipe generally does not exceed 20 kW/m·K, and the heat transfer system of the present disclosure achieves an equivalent thermal conductivity of 50 to 150 kW/m·K.

At the working temperature, various common inorganic liquids, organic liquids, refrigerants and liquid metals can be used as heat-conducting working materials, which can be single heat-conducting working materials or miscible mixed heat-conducting working materials, according to working temperature and working occasions. In the calculation of the filling quality of the mixed heat medium, ρ ₁ and ρ _g are the density and saturation of the saturated liquid mixed working medium at the working temperature T ₁ in the calculation formula (3) of the filling quality. The density of gaseous mixed working fluids.

Preferably, the heat conductive medium is selected from the group consisting of water, acetone, methanol, refrigerant (R134a, R410A, etc.), NaK alloy, ammonia, thermal conductivity, potassium, sodium, and lithium.

In the heat transfer system adopted in the embodiment of the present disclosure, the heating end and the cooling end may be at any position of the closed loop circuit; the number of the heating end and the cooling end may be plural. In one example, the heating end and the cooling end need not be formed into a special shape, but in order to increase the heat exchange area or form a shape with the heat source, as shown in FIG. 7, the heating end and the cooling end are preferably in the form of a serpentine tube or a tube row. Coil, as well as plate-like channels, or other rigid structures with internal loops. As long as it can communicate with the overall circuit, the wall allows heat to be transmitted and discharged. The outer surfaces of the heating end and the cooling end may have fins, ribs, sleeves or other structures that enhance heat transfer.

As shown in FIG. 8, the connecting passage of the heat transfer system of the embodiment of the present disclosure does not need to define a shape, and only works to form a closed loop. Thus, it may be an elliptical channel 31, a curved channel 32, an inflated channel 33, or other variations, which may be formed by elliptical member body 310, cuboid member body 320, and sheet metal member body 330, respectively.

The heat transfer system of the embodiments of the present disclosure may be a single channel circuit, or a multi-channel parallel circuit, or a variant thereof, such as a dendritic branch circuit. The length or deformation of the loop is not limited. The closed loop structure adopted in the embodiment of the present disclosure has little influence on the pressure wave transmission, and the pressure wave transmission is not hindered.

In other examples, referring to Figure 9, due to the thermal expansion characteristics of the liquid, in order to accommodate the heat transfer requirements under different temperature conditions, it is necessary to adjust the liquid filling rate so that when operating at the corresponding temperature, the liquid is at a high liquid filling rate or even close to full. State, due to "overfilled" liquid can cause the channel to rupture once the work is "over temperature". To this end, a liquid storage device 15 can be arranged on the closed circulation circuit, and the liquid filling amount in the closed circulation circuit can be adjusted through the opening and closing valve 14. The hot-pressure conversion heat transfer system with the liquid storage device can be realized in a large temperature range. Working properly inside.

Referring again to Figure 10, under certain conditions, the ability of the gravity drive circuit to convect is reduced. To form a stable convection cycle, an auxiliary pumping device 16 can be installed on the closed circuit, which can be used for horizontal placement, The heat source position is higher than the cold source position or microgravity, and the acceleration overload frequently changes.

Claims

A heat transfer method based on a hot press conversion effect, comprising the steps of:

Step S101: providing a heat transfer system, the heat transfer system is a closed loop circuit having a heating end and a cooling end;

Step S201: determining a working temperature interval and selecting a heat conductive working medium, so that a change of the corresponding working fluid pressure of the heat conductive working medium in the working temperature interval is greater than or equal to a preset value;

Step S301: filling the heat transfer working medium into the closed circulation loop of the heat transfer system, so that the ratio of the volume of the liquid heat conductive working medium to the total volume of the closed circulation loop is in a preset range;

Step S401: The heating end of the heat transfer system is in close contact with the heat source, and the cooling end of the heat transfer system is in contact with the cold source or dissipates heat to the environment.
The heat transfer method according to claim 1, wherein the predetermined value is 1.0 kPa/° C., so that the heat transfer medium is in a gas-liquid two-phase coexistence state in the working temperature range.
The heat transfer method according to claim 1, wherein said predetermined range is from 60% to 99%.
The heat transfer method according to claim 3, wherein in the step S301,

The filling quality of the heat transfer medium is determined by the following formula:

m=ρ 1 V 1 +ρ g (VV 1 )

Where m is the thermal mass of the working fluid, the unit is kg;

V is the total volume of the closed loop, in units of m 3 ;

V 1 is the working liquid temperature T 1 , the liquid volume of the heat transfer medium in the closed circulation loop, V 1 = (60% ~ 99%) V, the unit is m 3 , T 1 is the working temperature, and the charging is performed. When the mass is calculated, the value is taken as the average value of the highest temperature and the lowest temperature in the working temperature range, and the unit is °C;

ρ 1 is the density of the saturated liquid heat transfer working medium at the working temperature T 1 , and the unit is kg/m 3 ,

ρ g is the density of the saturated gaseous heat transfer medium at the working temperature T 1 in units of kg/m 3 .
The heat transfer method according to claim 1, wherein in the step S401, the liquid heat transfer medium of the heating end is thermally expanded by heat to form a pressure wave, and the pressure wave is pressed against the liquid heat conductive medium. The liquid heat transfer medium is driven to circulate, flows to the cooling end to dissipate heat, and then flows to the heating end, so that the heat-pressure conversion effect is continuously maintained.
The heat transfer method according to claim 2, wherein said preset value is 2.7 kPa/°C.
The heat transfer method according to claim 3, wherein said predetermined range is from 75% to 90%.
The heat transfer method according to claim 1, wherein the heat transfer medium is selected from the group consisting of water, acetone, methanol, ethanol, refrigerant, carbon dioxide, ammonia, thermal conductivity, NaK alloy, One or more of potassium, sodium, and lithium.
A heat transfer system using the heat transfer method according to any one of claims 1 to 8 to effect a hot press conversion effect, comprising a heating end in contact with a heat source, a cooling end in contact with a cold source or a heat sinking to the environment The heating end and the cooling end are connected by at least two connecting passages, and the heating end, the cooling end and the connecting passage are all rigid parts, and together form a closed loop.
The heat transfer system according to claim 9, wherein the material of the rigid member is selected from the group consisting of copper, copper alloy, aluminum, aluminum alloy, titanium alloy, nickel-base superalloy, and steel.
The heat transfer system according to claim 9, wherein said heating end or cooling end is formed in any one of a serpentine tube form, a tube row form, and a plate-like passage form.
The heat transfer system according to claim 9, wherein said connecting passage is selected from any one of an elliptical passage, a curved passage, and an inflation passage.
The heat transfer system of claim 9 wherein said closed loop is a single channel loop.
The heat transfer system of claim 9 wherein said closed loop circuit is a multi-channel parallel circuit.
A heat transfer system according to claim 9, wherein a liquid storage means is provided on said connecting passage, and said liquid filling amount in said closed circulation circuit is adjusted by opening and closing the valve.
A heat transfer system according to claim 9, wherein an auxiliary pumping means is provided on said connecting passage.