CN115013999A

CN115013999A - Cold and heat exchange system, refrigeration suit and refrigeration cushion

Info

Publication number: CN115013999A
Application number: CN202210688139.4A
Authority: CN
Inventors: 王乾新
Original assignee: Individual
Current assignee: Individual
Priority date: 2022-06-17
Filing date: 2022-06-17
Publication date: 2022-09-06

Abstract

The invention provides a cold-heat exchange system, a refrigerating garment and a refrigerating pad, which relate to the technical field of refrigerating equipment, the cold-heat exchange system comprises a refrigerating bin, wherein the refrigerating bin is provided with a first air inlet and a cold air outlet; still include the heat dissipation storehouse, the heat dissipation storehouse is equipped with second air inlet, useless air conditioning import and hot-air exhaust mouth, the gas outlet intercommunication of leading cold pipe in useless air conditioning air inlet and the refrigeration clothes or the refrigeration pad, install heat exchanger and side air-out fan in the heat dissipation storehouse. The cold and heat exchange system has the advantages of good refrigeration effect, small volume and light weight when used in a high-temperature environment.

Description

Cold and heat exchange system, refrigeration suit and refrigeration cushion

Technical Field

The invention relates to the technical field of refrigeration equipment, in particular to a cold-heat exchange system, a refrigeration suit and a refrigeration cushion.

Background

In hot summer, even if the user sits on a chair for a long time in an air-conditioned vehicle or indoors, the back and the buttocks are often soaked by sweat, and particularly for people who work outdoors, clothes are soaked by sweat and possibly have heatstroke, so that the design of clothes, a seat cushion and a back cushion with a refrigerating function is necessary.

Compared with the compressor refrigeration technology, the semiconductor refrigeration technology is the most suitable technology for refrigeration clothes and refrigeration cushions due to small volume and light weight. Patent application No. CN202210118589.X discloses a refrigerating plant based on semiconductor refrigeration technology and a refrigeration clothes using the same, and the technical scheme has the advantage that heat exchange between the hot end and the cold end of a semiconductor refrigeration sheet can be promoted simultaneously by only using one fan. However, the technical solution of patent cn202210118589.x has the technical problems of energy waste and insufficient heat dissipation efficiency of the semiconductor cooling fin hot-end radiator in extreme high-temperature weather, which results in that the cooling effect of the semiconductor cooling fin does not meet the use requirement.

Disclosure of Invention

The invention aims to provide a cold-heat exchange system, a refrigerating garment and a refrigerating pad, and aims to solve the problem that the refrigerating effect of the existing refrigerating device based on the semiconductor refrigerating technology is poor when the refrigerating device is used at high temperature in the prior art.

In order to realize the purpose, the invention adopts the following technical scheme: a heat exchange system for a refrigeration garment or pad, comprising: the refrigerating bin is provided with a first air inlet and a cold air outlet, the cold air outlet is communicated with an air inlet of a cold guide pipe in the refrigerating suit or the refrigerating cushion, a cold exchanger is arranged in the refrigerating bin, and air entering from the first air inlet passes through the cold exchanger and then enters the cold guide pipe in the refrigerating suit or the refrigerating cushion from the cold air outlet; the cooling system comprises a cooling bin, a heat exchanger and a side air-out fan, wherein the cooling bin is provided with a second air inlet, a waste cold air inlet and a hot air outlet, the waste cold air inlet is communicated with an air outlet of a cold guide pipe in a cooling suit or a cooling pad, the heat exchanger and the side air-out fan are installed in the cooling bin, an air outlet of the side air-out fan faces the side surface of the heat exchanger, the air blowing direction is approximately parallel to the fin surface of the heat exchanger, the side air-out fan is used for introducing external air and waste cold air into the cooling bin from the second air inlet and the waste cold air inlet respectively, and the external air and the waste cold air are mixed and then discharged from the hot air outlet through the heat exchanger; the semiconductor refrigerating piece, the refrigeration face of semiconductor refrigerating piece is towards the refrigeration storehouse, and the face that generates heat of semiconductor refrigerating piece is towards the storehouse that dispels the heat.

According to a further technical scheme, the cold-heat exchanger comprises flat heat pipes, the cold exchanger and/or the heat exchanger comprises flat heat pipes, the flat heat pipes comprise a plurality of sub heat pipes, and cavities of the flat heat pipes and the sub heat pipes are integrally formed by extrusion of aluminum or aluminum alloy.

According to a further technical scheme, a groove is formed in the wall of a sub-heat pipe cavity of the flat heat pipe, and the flat heat pipe shell, the sub-heat pipe cavity and the groove are integrally formed by extrusion of aluminum or aluminum alloy.

According to the further technical scheme, the groove comprises a raised groove which is formed by enclosing two adjacent protrusions arranged on the wall of the neutron heat pipe cavity of the flat heat pipe, and the distance D between the bottoms of the adjacent protrusions is larger than or equal to 0.2mm and smaller than or equal to 1.2 mm.

The further technical scheme of the invention is that the length L of the bottom side of the cross section of the bulge is more than or equal to 0.2mm and less than or equal to 1.2 mm.

According to a further technical scheme, the height H of the cross section of the bulge is more than or equal to 0.2mm and less than or equal to 1.2 mm.

The further technical scheme of the invention is that the included angle beta between the bulge on the cavity wall and the cavity wall in the flat heat pipe is more than or equal to 92 degrees and less than or equal to 122 degrees.

The further technical scheme of the invention is that the groove comprises a round hole groove which is arranged on the wall of the sub heat pipe cavity and is approximately round in shape, the round hole groove is provided with an opening communicated with the sub heat pipe cavity, and the diameter phi of the round hole groove satisfies that the diameter phi is more than or equal to 0.3mm and less than or equal to 1.2 mm. A refrigeration garment comprising a heat exchange system as claimed in any one of the preceding claims.

A refrigeration mat comprising the heat exchange system of any one of the above.

The invention has the beneficial effects that:

the refrigerating sheet works, the temperature of a refrigerating surface of the refrigerating sheet is reduced, air entering from the first air inlet is refrigerated through the cold exchanger, the cooled air enters the cold guide pipe in the refrigerating suit or the refrigerating cushion through the cold air outlet, and the cold air absorbs heat in the process of flowing through the cold guide pipe in the refrigerating suit or the refrigerating cushion, so that the sensible temperature of a user is reduced; the air entering the heat exchanger is pre-cooled by the waste cold air to improve the heat dissipation effect, so that the refrigerating capacity used in a high-temperature environment is improved, and meanwhile, the side air outlet fan can be used for providing power, so that the cold air in the refrigerating bin, the refrigerating clothes and the refrigerating pad cold guide pipe flows.

Drawings

FIG. 1 is a schematic front view of a host computer for heat exchange according to an embodiment of the present disclosure;

FIG. 2 is a schematic diagram of an internal structure of a host for heat exchange according to an embodiment of the disclosure;

FIG. 3 is an exploded view of the internal structure of a host for heat exchange provided in the disclosed embodiment of the present invention;

FIG. 4 is a schematic diagram of a flat heat pipe structure according to an embodiment of the present disclosure;

FIG. 5 is a schematic structural diagram of a neutron-heat pipe in a flat-plate heat pipe structure according to an embodiment of the disclosure;

FIG. 6 is a schematic view of another flat heat pipe configuration according to an embodiment of the present disclosure;

FIG. 7 is a schematic structural diagram of a neutron-heat pipe in another flat-plate heat pipe structure selected for use in accordance with an embodiment of the present disclosure;

FIG. 8 is a schematic diagram of an arrangement of an apparatus for testing heat transfer performance of a heat pipe according to an embodiment of the disclosure.

Detailed Description

The invention relates to a cold-heat exchange system adopting a semiconductor refrigeration technology, which improves the refrigeration capacity of the cold-heat exchange system in a high-temperature environment and reduces the weight and the volume by adopting a new design scheme and adopting a flat heat pipe with heat superconductivity.

The following further describes embodiments of the present invention with reference to the drawings.

As shown in fig. 1 to 3, the heat exchange system for the refrigeration suit and the refrigeration cushion comprises a main unit 11, wherein the main unit 11 comprises a refrigeration chamber 12 and a heat dissipation chamber 13, the heat dissipation chamber 13 and the refrigeration chamber 12 can be separated by a partition 14, and the partition 14 is preferably made of a heat insulating material; a first air inlet 121 and a cold air outlet 122 which are communicated with the refrigerating bin 12 are respectively arranged at two opposite sides of the refrigerating bin 12, a cold exchanger 16 is arranged in the refrigerating bin 12, external air enters from the first air inlet 121, and after being cooled by the cold exchanger 16, the cold air is discharged from the cold air outlet 122; a second air inlet 132 and a hot air outlet 133 communicating with the heat-radiating chamber 13 are respectively provided at opposite sides of the heat-radiating chamber 13, and a waste cold air inlet 131 is provided beside the second air inlet 132, and waste cold air is mixed with air introduced from the second air inlet 132. The heat exchanger 17 is installed in the heat dissipation chamber 13, the side outlet fan 15 is provided between the heat exchange 17 and the second air inlet 132, the outlet of the fan 15 faces the heat exchanger 17, the direction of air blown by the side outlet fan 15 is substantially parallel to the fin surface of the heat exchanger 17, and the main unit 11 is further provided with a power supply inlet.

In order to cool the air entering the refrigerating chamber 12, an opening is arranged in the heat insulation plate 14, a refrigerating sheet 18 is placed in the opening, the refrigerating surface of the refrigerating sheet 18 faces the refrigerating chamber 12 and is attached to the cold exchanger 16, and the heating surface faces the heat dissipation chamber 13 and is attached to the heat exchanger 17; in order to isolate the heat exchange between the refrigeration chamber 12 and the heat dissipation chamber 13, a material for blocking heat convection, such as foam, may be disposed at the junctions between the refrigeration fins 18 and the partition 14 and between the partition 14 and the casing; the power supply can be supplied by a battery or a direct current power supply, and the battery can be placed in the host 11 of the cold-heat exchange system or externally connected with the direct current power supply; the heat exchanger 17 and the cold exchanger 16 may be extruded profiles of aluminum alloy or may be radiators of other types.

After the power is turned on, the refrigerating sheet 18 works, the temperature of the refrigerating surface of the refrigerating sheet is reduced, the air entering from the first air inlet 121 is refrigerated through the cold exchanger 16, the cooled air enters a cold guide pipe (not shown in the figure) in the refrigerating suit or the refrigerating cushion through the cold air outlet 122, and the cold air absorbs heat in the process of flowing through the cold guide pipe in the refrigerating suit or the refrigerating cushion, so that the sensible temperature of a user is reduced; the cold air flowing out from the air outlet of the cold conducting pipe in the refrigeration suit or the refrigeration cushion is called as "waste cold air", and the waste cold air enters the heat dissipation bin 13 through the waste cold air inlet 131 of the heat dissipation bin.

After the power is on, the heating surface of the refrigerating sheet 18 generates heat, and the generated heat is dissipated through the heat exchanger 17; when powered on, the side air outlet fan 15 rotates to suck air and waste cold air respectively through the second air inlet 132 and the waste cold air inlet 131, the external air and the waste cold air are mixed and blown together to the heat exchanger 17 to dissipate heat of the heat exchanger 17, and the hot air is discharged to the external environment through the air outlet 133; the design aims to utilize waste cold air to pre-cool air entering the heat exchanger so as to improve the heat dissipation effect and further improve the refrigerating capacity, and meanwhile, the side air outlet fan can be used for providing power so that cold air in the refrigerating bin and the refrigerating clothes/refrigerating pad cold guide pipe flows.

It should be noted that: the cold exchanger 16 and the heat exchanger 17 can be made of extruded aluminum alloy sections or other heat dissipation schemes, preferably, a technical scheme of 'flat heat pipes + fins' is selected, and the scheme has high cold-heat exchange efficiency and light weight. As shown in fig. 3, the cold exchanger 16 includes a first flat heat pipe 161 and a first fin 162 disposed on the first flat heat pipe 161, the first fin 162 may be folded or buckled on the first flat heat pipe 161 to increase the contact area with air and improve the heat dissipation effect, or may be a heat dissipation fin manufactured by other processes on the first flat heat pipe 161; the heat exchanger 17 comprises a second flat heat pipe 171 and a second fin 172 arranged on the second flat heat pipe 171, the second fin 172 can be folded or buckled on the second flat heat pipe 171, and a heat dissipation fin manufactured by other processes is also adopted on the second flat heat pipe 17; the refrigerating surface of the refrigerating plate 18 is connected to the first flat heat pipe 161 through one of the attaching methods such as a heat conductive paste, a heat conductive silicone grease, or a heat conductive pad, and the heating surface of the refrigerating plate 18 is connected to the second flat heat pipe 171 through one of the attaching methods such as a heat conductive paste, a heat conductive silicone grease, or a heat conductive pad.

In the present embodiment, the first plate heat pipe 161 and the second plate heat pipe 171 have substantially the same cross-sectional structure, and as shown in fig. 4, include a heat pipe housing 21, a sub heat pipe 22, a protrusion 23, a protrusion groove 24, and a circular hole groove 25. The heat pipe shell 21, the protrusion 23 and the circular hole groove 25 are integrally extruded and molded by aluminum or aluminum alloy. The first flat heat pipe 161 and the second flat heat pipe 171 in this embodiment include six sub-heat pipes 22, the number of the sub-heat pipes in the flat heat pipe is not limited in the present invention, and may be 1, 2, or 3 or more, and the number of the sub-heat pipes depends on the width of the first flat heat pipe 161 and the second flat heat pipe 171, the requirement of the temperature equalization of the product, and other requirements. The present invention also does not limit whether the sub-heat pipes 22 are uniformly distributed in the

flat heat pipes

161 and 171, and may be uniform or non-uniform, sometimes to meet the requirement of screw holes, and increasing solid portions between the sub-heat pipes 22 and/or the side edges of the flat heat pipes, sometimes to meet the requirement of bending resistance, adding round holes between the sub-heat pipes 22, and inserting a hard material, such as stainless steel, into the round holes. In the present embodiment, the sealing of the flat heat pipe port is performed by laser welding, but the sealing method of the flat heat pipe port is not limited in the present invention, and may be one or a combination of a plurality of pressure welding, brazing, and soldering. In the present embodiment and the present invention, the sub-heat pipes 22 in the flat heat pipe work independently, which means that the phase-change heat transfer working mediums in the sub-heat pipes 22 are isolated from each other. In this embodiment, the phase change heat transfer working medium in the sub-heat pipe 22 is ethanol, but the invention is not limited to the phase change heat transfer working medium, and may also be deionized water, acetone, ammonia water, or a composite working medium. The arrangement of aluminum/aluminum-based alloy/copper alloy wires or mesh or other materials in the sub-heat pipes 22 can further improve the reflux capacity of the liquid phase-change heat transfer working medium, but in this embodiment, no wires or mesh are arranged.

In this embodiment, the cross section of the sub-heat pipe 22 in the flat heat pipe is shown in fig. 5, and the cross section of the cavity wall of the sub-heat pipe 22 is quadrilateral, but the invention does not limit the shape of the cross section of the cavity wall of the sub-heat pipe 22, and the cross section of the cavity wall of the sub-heat pipe 22 may also be triangular, pentagonal, hexagonal or other curved surface shapes. The cavity wall of the sub heat pipe 22 is provided with the circular hole grooves 25, so that the heat exchange area between the vapor phase heat transfer working medium and the cavity wall can be further increased, and the backflow of the liquid phase heat transfer working medium can be increased. In this embodiment, two cavity walls of the quadrilateral cavity wall of the sub heat pipe 22 are respectively provided with 4 protrusions 23, the invention does not limit the position and the number of the protrusions arranged on the cavity walls, and can also be arranged on one or three or four cavity walls of the sub heat pipe 22, or only two protrusions or three protrusions can be arranged on one cavity wall.

The shape, size and distance of the bulges on the wall of the heat pipe cavity have important influence on the heat pipe performance, and the influence comes from two aspects, namely the change of the heat exchange area of the vapor phase heat transfer working medium and the wall of the heat pipe cavity, and the change of the surface tension of the liquid phase heat transfer working medium on the wall of the cavity, which influences the reflux speed of the liquid phase heat transfer working medium and further influences the heat transfer performance of the heat pipe. Therefore, it is necessary to evaluate the influence of the protrusion shape, the protrusion size and the protrusion distribution in the heat pipe on the heat transfer performance of the heat pipe.

First, parameters H, β, L, D, Φ related to the bump shape, bump size, bump distribution, and the size of the circular hole groove in the present invention are defined, and specific explanations of these parameters are as shown in fig. 5 and 7:

d is the distance between two adjacent side edge fitting extension lines of two adjacent bulges on the cross section of the wall of the heat pipe cavity and two intersection points of the wall fitting extension lines.

H is the vertical distance between the bulge high point on the cross section of the heat pipe cavity wall and the fit extension line of the cavity wall at the bulge.

L is the distance between two intersection points of two convex side fitting extension lines on the cross section of the wall of the heat pipe cavity and two convex cavity wall fitting extension lines.

Beta is the included angle between the tangent line at the intersection of the convex side edge fitting extension line and the convex part cavity wall fitting extension line on the cross section of the heat pipe cavity wall and the convex side edge fitting extension line.

Phi is the diameter of the round hole groove which is approximately round on the cross section of the wall of the heat pipe cavity, and is the diameter of the round hole with the highest fitting degree with the round hole groove.

The experimental design is carried out according to the following experimental principle, and the influence of H, beta and L, D parameters on the performance of the heat pipe is researched and analyzed:

the experimental principle is as follows:

fig. 8 is a schematic layout diagram of a heat transfer performance test of a heat pipe 31, which includes the heat pipe 31, a heat source 32, and three temperature measurement points (T1, T2, T3). Fig. 8 shows the heat pipe length, heat source position, and temperature measurement point position, with L1=250mm, L2=200mm, L3=25mm, and L4=5 mm. The temperature point T1 is close to the heat source and is the reference temperature point for whether the heat transfer performance test system of the heat pipe meets the test specification. The better the heat transfer performance of the heat pipe, the better the temperature uniformity in the length direction of the heat pipe, i.e. the smaller the temperature difference Δ T between T2 and T3. Thus, the heat transfer capabilities of the heat pipes can be compared by measuring Δ T of the heat pipe surfaces.

The experimental method comprises the following steps: 5 kinds of heat pipes with different cavity wall structures are prepared, and passivation treatment is carried out on the cavity walls of the heat pipes. The cavity of the heat pipe is quadrilateral, the cavity wall is provided with a bulge, the size of the bulge is shown in table 1, the overall size of the heat pipe is 7mm multiplied by 250mm, and the wall thickness is 0.5 mm. The phase-change heat transfer working medium is a deionized water composite heat transfer working medium. The heat source for the test is a constant temperature heat source, the test temperature of the heat source is 55 ℃, the temperature control precision is +/-1 ℃, and thermocouples are adopted to measure the temperature of three temperature measuring points T1, T2 and T3, and the temperature measuring precision is +/-0.1 ℃.

Explanation of the experiment:

after the heat pipe cavity is vacuumized and filled with a heat transfer working medium, negative pressure is formed in the heat pipe at normal temperature, and the strength of aluminum alloy is not high, so that the size of the cross section of the aluminum heat pipe cannot be too large, otherwise, the cavity wall of the heat pipe can be recessed due to the negative pressure, the requirements of testing different protrusion heights H, different protrusion bottom edge lengths L, different protrusion distances D and experimental test specifications are considered, the size of the cross section of the aluminum heat pipe cannot be too small, and therefore the external dimension of the experimental heat pipe is determined to be 7mm multiplied by 250mm, and the wall thickness of the heat pipe is 0.5 mm. When the heat pipe cavity wall protrusion parameters are designed, the minimum size of H, D, L is selected to be 0.2mm, because the limit process precision of the extrusion level of the current section bar is 0.2 mm. And because at least two bulges are arranged on the side wall of the heat pipe cavity wall to form a groove for improving the adsorption force of the liquid surface, the maximum distance of the bulges can only be 1.2mm for a heat pipe with the external dimension of 7mm multiplied by 250mm and the wall thickness of 0.5mm, otherwise, the bulge groove can not be formed on the side wall of the heat pipe cavity wall, so the maximum dimension of H, D is determined to be 1.2mm, and the maximum dimension of L is adjusted according to H, D and is basically close to 1.2 mm. The value range of the beta angle is determined to be 90-120 degrees according to experience, and after the maximum value and the minimum value of H, D, L and beta are determined, two groups of intermediate data are selected. As shown in Table 1, a heat pipe 5# having no projection was used as a control.

The test data are shown in Table 1, the heat pipe 5# without a raised structure has a delta T of 23.60 ℃ which is far greater than the evaluation standard for the heat transfer performance of the heat pipe (delta T is less than or equal to 5 ℃), which indicates that the heat pipe 5# has poor heat transfer capability under the horizontal use working condition. Experimental data of the heat pipe 1#, the heat pipe 2#, the heat pipe 3# and the heat pipe 4# show that the heat pipes delta T of the cavity wall structures are less than or equal to 5 ℃, which indicates that the heat pipes can meet the evaluation standard of heat transfer performance of the heat pipes. Δ T =1.20 ℃ for heat pipe 2#, the Δ T value is minimal, and the parameters that indicate the optimal cavity wall configuration are located between heat pipe 1# and heat pipe 3 #. The Δ T =4.8 ℃ for sample 4#, very close to the minimum standard 5.0 ℃ for heat pipe performance, indicating that structural parameters beyond the wall of heat pipe 4# chamber will not meet the application requirements. In addition, it was found during production that profile extrusion is not favoured when β =90 °. According to the analysis of the test data and the experience accumulated in the production process, the optimal value intervals of H, beta and L, D for describing the convex shape, size and distribution parameters of the heat pipe can be basically determined: h is more than or equal to 0.2mm and less than or equal to 1.2mm, L is more than or equal to 0.2mm and less than or equal to 1.2mm, D is more than or equal to 0.2mm and less than or equal to 1.2mm, and beta is more than or equal to 92 degrees and less than or equal to 122 degrees. According to the experimental data, the upper limit size of the diameter phi of the circular hole groove is 1.2mm, the surface tension obtained by the liquid-phase heat transfer working medium is maximum, the reflux speed of the liquid-phase heat transfer working medium is fastest, and the heat transfer performance is best, and the diameter phi is less than 0.3mm when the aluminum or aluminum alloy heat pipe shell and the circular hole groove are integrally extruded together, so that the current process level is difficult to realize, and the lower limit size of the diameter phi of the circular hole groove is 0.3mm, so that the optimal value interval of the diameter phi of the circular hole groove is not less than 0.3mm and not more than 1.2 mm.

Table 1: heat pipe cavity wall structure parameter and heat transfer performance data table

In this example, β is 115 °, L is 0.6mm, H is 0.6mm, D is 0.6mm, and φ is 0.6 mm. When the refrigeration suit and the refrigeration pad are used, the included angle between the axis of the sub heat pipe of the flat heat pipe in the heat exchange host and the horizontal plane may change from time to time, and if no protrusion is arranged or the selection of the structural parameters of the protrusion is not proper, the efficiency of the heat exchange system is affected. The projections in each heat pipe in the flat heat pipe are set according to the shape, size and distribution parameters of the projections which are optimized through experiments, so that the liquid-phase heat transfer working medium in the sub heat pipe 22 can obtain sufficient capillary force backflow, and the heat transfer performance of the flat heat pipe can meet the use requirements of products.

In this embodiment, the flat heat pipe may also adopt another structure, as shown in fig. 6 and 7, including a housing 21, a sub heat pipe 22 having a circular cavity wall, where the cavity wall of the sub heat pipe 22 is provided with a protrusion 23, a groove 24 is formed between adjacent protrusions, and the cavity wall of the sub heat pipe 22 is not provided with a circular hole groove. FIG. 7 is an enlarged view of one of the sub-heat pipes in the flat heat pipe, where β is 100 °, L is 0.5mm, D is 0.5mm, and H is 0.5mm in this alternative.

In the description of the invention, the cavity wall means that after the protrusion is cut off and/or the circular hole groove is filled, according to the surface characteristics of the cavity outside the protrusion and the circular hole groove, the virtual surface obtained by cutting off the protrusion and/or filling the circular hole groove is obtained by fitting, and the virtual surface and the uncut and/or filled area form the cavity wall.

In the description of the present invention, the meaning of horizontal, nearly horizontal, and substantially horizontal in the lengthwise direction of the heat pipe and the flat heat pipe appearance means that the angle η with the horizontal plane satisfies-5 ° η ≦ 5 °. The horizontal, approximately horizontal and approximately horizontal meaning of the axis of the sub heat pipe of the flat heat pipe means that the included angle theta between the horizontal plane and the horizontal plane is more than or equal to minus 5 degrees and less than or equal to 5 degrees.

A refrigeration garment comprising a heat exchange system as claimed in any one of the preceding claims.

A refrigeration mat comprising a heat exchange system as claimed in any one of the preceding claims.

In the description of the present invention, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.

It will be evident to those skilled in the art that the invention is not limited to the details of the foregoing illustrative embodiments, and that the present invention may be embodied in other specific forms without departing from the spirit or essential attributes thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein. Any reference sign in a claim should not be construed as limiting the claim concerned.

Furthermore, it should be understood that although the present description refers to embodiments, not every embodiment may contain only a single embodiment, and such description is for clarity only, and those skilled in the art should integrate the description, and the embodiments may be combined as appropriate to form other embodiments understood by those skilled in the art.

Claims

1. A heat exchange system for a refrigeration garment or pad, comprising:

the refrigerating bin is provided with a first air inlet and a cold air outlet, the cold air outlet is communicated with an air inlet of a cold guide pipe in the refrigerating suit or the refrigerating cushion, a cold exchanger is arranged in the refrigerating bin, and air entering from the first air inlet passes through the cold exchanger and then enters the cold guide pipe in the refrigerating suit or the refrigerating cushion from the cold air outlet;

the cooling system comprises a cooling bin, a heat exchanger and a side air-out fan, wherein the cooling bin is provided with a second air inlet, a waste cold air inlet and a hot air outlet, the waste cold air inlet is communicated with an air outlet of a cold guide pipe in a cooling suit or a cooling pad, the heat exchanger and the side air-out fan are installed in the cooling bin, an air outlet of the side air-out fan faces the side surface of the heat exchanger, the air blowing direction is approximately parallel to the fin surface of the heat exchanger, the side air-out fan is used for introducing external air and waste cold air into the cooling bin from the second air inlet and the waste cold air inlet respectively, and the external air and the waste cold air are mixed and then discharged from the hot air outlet through the heat exchanger;

the semiconductor refrigeration piece, the refrigeration face of semiconductor refrigeration piece is towards refrigeration storehouse, and the face that generates heat of semiconductor refrigeration piece is towards the storehouse that dispels the heat.

2. A heat exchange system according to claim 1, wherein the cold exchanger and/or the heat exchanger includes a flat heat pipe, the flat heat pipe includes a plurality of sub heat pipes, and the cavities of the flat heat pipe and the sub heat pipes are integrally formed by extrusion of aluminum or an aluminum alloy.

3. A heat exchange system according to claim 2, wherein the sub-heat pipe chamber walls of the flat heat pipe are provided with grooves, and the flat heat pipe shell, the sub-heat pipe chamber and the grooves are integrally formed by extrusion of aluminum or an aluminum alloy.

4. The heat exchange system according to claim 3, wherein the groove comprises a protrusion groove, the protrusion groove is formed by enclosing two adjacent protrusions arranged on the wall of the neutron heat pipe cavity of the flat heat pipe, and the distance D between the bottoms of the adjacent protrusions is 0.2mm or more and 1.2mm or less.

5. A heat exchanging system according to claim 4, wherein the length L of the bottom side of the convex cross section satisfies 0.2 mm. ltoreq. L.ltoreq.1.2 mm.

6. A heat exchanging system according to claim 4, wherein the raised cross-sectional height H satisfies 0.2mm ≦ H ≦ 1.2 mm.

7. A heat exchange system according to claim 4, wherein the angle β between the projection and the chamber wall satisfies 92 ° β 122 °.

8. A cold and heat exchange system according to claim 3, 4, 5, 6 or 7, wherein the grooves comprise circular hole grooves which are arranged on the wall of the heat pipe sub-chambers and are approximately circular in shape, the circular hole grooves are provided with openings communicated with the heat pipe sub-chambers, and the diameter phi of the circular hole grooves satisfies 0.3mm ≤ phi ≤ 1.2 mm.

9. A refrigeration garment comprising a heat exchange system according to any one of claims 1 to 8.

10. A refrigeration mat comprising the heat exchange system of any one of claims 1 to 8.