阅读说明：本技术 一种热交换流体通道、热交换器及热交换方法 (Heat exchange fluid channel, heat exchanger and heat exchange method ) 是由 何戈宁 吴舸 李冬慧 李毅 邓丰 谈国伟 鲁佳 汤臣杭 苏桐 袁宏 田雅婧 张 于 2021-10-28 设计创作，主要内容包括：本发明公开了一种热交换流体通道及热交换器,在流体通道的横截面内,包括多个单元流道,所有单元流道均为紧密排布的的多边形,且每个单元流道周围分布的单元流道的个数与该单元流道的边数相等,任意相邻两个单元流道的相邻边相向对应,相邻单元流道的对应边与边之间的热导体作为流体间隔壁。本发明通过优化设有热交换流体通道的排布结构,利于显著提高换热效率。该换热流体通道是由多个单元流道构成,进一步优化设计该换热流体通道横向截面内单元流道的结构、以及所有单元流道的排布结构,以提高换热器整体的热交换效率。(The invention discloses a heat exchange fluid channel and a heat exchanger, wherein the cross section of the fluid channel comprises a plurality of unit flow channels, all the unit flow channels are polygons which are closely arranged, the number of the unit flow channels distributed around each unit flow channel is equal to the number of the edges of the unit flow channel, the adjacent edges of any two adjacent unit flow channels are opposite and corresponding, and heat conductors between the corresponding edges of the adjacent unit flow channels are used as fluid partition walls. The invention is beneficial to obviously improving the heat exchange efficiency by optimizing the arrangement structure provided with the heat exchange fluid channel. The heat exchange fluid channel is composed of a plurality of unit flow channels, and the structure of the unit flow channels in the transverse section of the heat exchange fluid channel and the arrangement structure of all the unit flow channels are further optimized and designed so as to improve the overall heat exchange efficiency of the heat exchanger.)

1. A heat exchange fluid channel comprises a plurality of unit flow channels in the cross section of the fluid channel and is characterized in that all the unit flow channels are polygons which are closely arranged, the number of the unit flow channels distributed around each unit flow channel is equal to the number of the edges of the unit flow channel, the adjacent edges of any two adjacent unit flow channels are opposite and corresponding, and heat conductors between the corresponding edges of the adjacent unit flow channels are used as fluid partition walls.

2. A heat exchange fluid path as set forth in claim 1 wherein all of the unit flow channels have equal side lengths.

3. A heat exchange fluid channel as claimed in claim 1, wherein the junctions between adjacent edges of the cell flow channels are transitioned through fillets or chamfers.

4. A heat exchange fluid channel as claimed in claim 1, wherein the shape of any one, or two or more sides of the unit flow channel includes arc, wave, triangular tooth, rectangular tooth.

5. A heat exchange fluid path as claimed in claim 1, wherein the planar subdivision is performed according to the thieson polygon algorithm to form a polygonal fluid path.

6. A heat exchange fluid channel according to claim 1, wherein all of the unit flow channels are deformed integrally in a certain direction or directions within the plane.

7. A heat exchange fluid channel according to any one of claims 1 to 6, wherein each unit flow channel has a cross section of a regular hexagon, a regular quadrangle or a regular triangle.

8. A heat exchange fluid channel as set forth in claim 7, wherein each unit flow channel has a side length of 0.005mm to 50 mm; the thickness of the partition wall is 0.001 mm-20 mm.

9. A heat exchanger comprising a heat exchange fluid channel as claimed in any one of claims 1 to 8.

10. A heat exchanger according to claim 9 wherein all of the unit flow passages are arranged spirally in the axial direction as spiral heat exchange fluid passages; or all the unit flow channels are in a linear structure along the axial direction and are used as straight-through heat exchange fluid channels; or all the unit flow channels extend along a space curve to serve as curved heat exchange fluid channels, extend along the space curve and are spirally arranged along the axial direction of the current fluid channel, or part of the unit flow channel sections serving as the curved heat exchange fluid channels are in a linear structure or a spiral structure.

11. A heat exchanger according to claim 10 wherein said heat exchange fluid channel longitudinal cross-sectional shape comprises a wave, triangular tooth, rectangular tooth.

12. A heat exchanger according to any one of claims 9 to 11, wherein the heat exchanger is integrally formed using smart manufacturing techniques including 3D printing.

13. A method of heat exchange using a heat exchange fluid channel as claimed in any one of claims 1 to 8, or using a heat exchanger as claimed in any one of claims 9 to 11; the fluid passage is characterized in that when two fluids flow through the fluid passage, the fluid passages around one fluid passage are the fluid passages of the other fluid.

Technical Field

The invention relates to the technical field of heat exchange, in particular to a heat exchange fluid channel, a heat exchanger and a heat exchange method.

Background

A heat exchanger is a device that transfers the heat of a certain fluid to another fluid in a certain heat transfer manner. Heat exchangers are becoming more and more popular in industrial production, and are spread throughout various industrial sectors such as power, metallurgy, chemical industry, petroleum, food, medicine, aerospace, and the like.

The heat exchange efficiency of the heat exchanger is improved, the structure of the heat exchanger is more compact, and the heat exchanger is a hot research topic in the world. At present, the high-efficiency heat exchanger used in industry usually adopts the modes of adding fins on a heat transfer pipe, adopting a plate-fin heat exchange mode, adopting a printed circuit board type heat exchanger and the like.

Disclosure of Invention

Based on the technical background, the invention provides a heat exchange fluid channel and a heat exchanger, and the heat exchange efficiency of the heat exchanger can be greatly improved by optimally designing a circulation channel arrangement structure and a heat exchanger structure.

The invention is realized by the following technical scheme:

a heat exchange fluid channel comprises a plurality of unit flow channels in the cross section of the fluid channel, wherein all the unit flow channels are polygons which are closely arranged, the number of the unit flow channels distributed around each unit flow channel is equal to the number of the sides of the unit flow channel, the adjacent sides of any two adjacent unit flow channels are opposite and corresponding, and the heat conductors between the corresponding sides of the adjacent unit flow channels are used as fluid partition walls. Preferably, when two fluids flow through the fluid channels, the two fluids can be divided into hot fluid and cold fluid, except for the fluid channels positioned at the edges, wherein the fluid channels around one fluid channel are the fluid channels of the other fluid; for example, the plurality of unit flow channels include a hot unit flow channel and a cold unit flow channel based on the kind division for the circulating fluid in each unit flow channel; and cold unit runners are distributed around each hot unit runner, or hot unit runners are distributed around each cold unit runner.

The invention is beneficial to obviously improving the heat exchange efficiency by optimizing the arrangement structure provided with the heat exchange fluid channel. The heat exchange fluid channel is composed of a plurality of unit flow channels, and the structure of the unit flow channels in the transverse section of the heat exchange fluid channel and the arrangement structure of all the unit flow channels are further optimized and designed so as to improve the overall heat exchange efficiency of the heat exchanger. The above description "the number of unit flow channels distributed around each unit flow channel is equal to the number of sides" means that the unit flow channels distributed around the unit flow channel and having corresponding sides are based on any one unit flow channel. Based on the type division for circulating fluid in each unit flow channel, a plurality of cold unit flow channels are distributed around each hot unit flow channel, and preferably, all the cold unit flow channels distributed around each hot unit flow channel are cold unit flow channels; a plurality of hot unit flow channels are distributed around each cold unit flow channel, and preferably all of the hot unit flow channels are distributed around each cold unit flow channel.

A plurality of channels can be arranged on the cross section of the heat exchanger to serve as fluid channels, each channel serves as a unit flow channel, at the moment, the heat conductor between the adjacent edges of the adjacent unit flow channels serves as a partition wall, and the heat conductor is the material of the heat exchanger, such as stainless steel and the like; the side walls of the heat exchange tubes can be sequentially and adjacently spliced to form a plurality of channel heat exchange bodies on the cross section, at the moment, the hollow part of each heat exchange tube is used as a unit runner, and the side walls butted between the adjacent heat exchange tubes are connected into a whole to be used as a heat conductor.

More preferably, all the partition walls have the same side length. I.e. it is further preferred that all polygons are identical in shape and size.

Further preferably, the joints between the adjacent edges of the unit flow channels are transited through fillets or chamfers; so as to further improve the structure and the thermal performance of the heat exchange fluid channel and prolong the service life of the heat exchange fluid channel.

Further preferably, the shape of any one, or two or more sides of the unit flow channel includes arc shape, wave shape, triangular tooth shape, and rectangular tooth shape. The edges of the cross section of the unit flow channel are derived into nonlinear structures, such as arc, wave or zigzag structures, so that the heat exchange area is further improved, and the heat exchange performance is improved.

Further preferably, the plane is split according to a Thiessen polygon algorithm to form a polygonal fluid channel.

Further preferably, all the unit flow channels are deformed integrally in a certain direction in a plane. The x-coordinate and y-coordinate of all features in the plane are multiplied by coefficients respectively.

Further preferably, the cross section of each unit flow channel is a regular polygon.

Further preferably, the cross section of each unit flow channel is a regular hexagon, a regular quadrangle or a regular triangle. Through further preferably designing the cross section of each fluid channel to be regular hexagon, regular quadrangle or regular triangle, the fluid channel structure which can realize the equal size of the cross section of each fluid channel, the equal length and the equal thickness of all the partition walls and the uniform distribution of all the runner units is further beneficial to realizing the full distribution of cold runner units around each hot unit runner or the full distribution of hot runner units of each cold runner unit; like a regular quadrangle and a triangle, the hot runners are also beneficial to simultaneously realizing that all the peripheries of each hot runner are distributed into the cold runners, and all the peripheries of each cold runner are distributed into the hot runners

Further preferably, for both fluids, for example, hot or cold fluids, a cold runner is distributed around each hot runner, and a hot runner is distributed around each cold runner. Is beneficial to improving the heat exchange efficiency.

Further preferably, the side length of each unit flow channel is 0.005 mm-50 mm; the thickness of the partition wall is 0.001 mm-20 mm. For example, the side length of each unit flow channel is 0.005mm to 50 mm; for the regular hexagon unit flow channel, the thickness of the partition wall is 0.001 mm-20 mm; for the unit flow channel of the regular quadrangle or the regular triangle, the thickness of the partition wall is 0.01 mm-10 mm.

A heat exchanger comprising a heat exchange fluid channel as described above.

Preferably, all the unit flow channels are spirally arranged along the axial direction and are used as spiral heat exchange fluid channels; or all the unit flow channels are in a linear structure along the axial direction and are used as straight-through heat exchange fluid channels; or all the unit flow channels extend along a space curve to serve as curved heat exchange fluid channels, extend along the space curve and are spirally arranged along the axial direction of the current fluid channel, or part of the unit flow channel sections serving as the curved heat exchange fluid channels are in a linear structure or a spiral structure.

It is further preferred that the cross-section and/or the longitudinal section of the heat exchanger profile is the same as the profile configuration of all the fluid channel arrangements.

Further preferably, the longitudinal section of the heat exchange fluid channel has a wave shape, a triangular tooth shape or a rectangular tooth shape.

Further preferably, the heat exchanger is integrally formed by machining and adopting an intelligent manufacturing technology including 3D printing.

A heat exchange method using the above-described one heat exchange fluid passage, or using the above-described one heat exchanger; when two fluids flow through the fluid channels, the fluid channels around one fluid channel are the fluid channels of the other fluid except the fluid channels at the edge. For example, hot fluid may be circulated within the hot unit runners and cold fluid may be circulated within the cold unit runners such that the cold unit runners are distributed around each hot unit runner and/or the hot unit runners are distributed around each cold unit runner.

The invention has the following advantages and beneficial effects:

the invention is beneficial to obviously improving the heat exchange efficiency by optimizing the arrangement structure provided with the heat exchange fluid channel. The heat exchange fluid channel is composed of a plurality of unit flow channels, and the structure of the unit flow channels in the transverse section of the heat exchange fluid channel and the arrangement structure of all the unit flow channels are further optimized and designed so as to improve the overall heat exchange efficiency of the heat exchanger.

The invention can be integrally prepared and molded by adopting intelligent manufacturing technologies such as 3D printing and the like, can break through the process limitation caused by a tube-type heat exchanger and a plate-type heat exchanger, realizes the arrangement of the factory public engineering fluid flow channels around the process fluid flow channels, and greatly improves the heat exchange efficiency of the process fluid. By applying the design concept of the invention, the replacement design of the existing heat exchanger is developed, namely the total heat exchange coefficient is greatly improved under the condition of completely meeting the heat exchange function and the pressure bearing function of the existing heat exchanger, and the weight, the volume and the manufacturing period can be greatly reduced.

Drawings

The accompanying drawings, which are included to provide a further understanding of the embodiments of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the principles of the invention. In the drawings:

FIG. 1 is a schematic cross-sectional view of a hexagonal close packed heat exchanger fluid channel of the present invention;

reference numbers and corresponding part names in fig. 1: 1-edge of unit flow channel, 2-partition wall, 3-fluid I, 4-fluid II.

FIG. 2 is a schematic cross-sectional view of the fluid passages of the heat exchanger of the present invention arranged in a hexagonal close packed arrangement using a fluid passage method in which the fluid passages around one fluid passage are all the other fluid;

reference numbers and corresponding part names in fig. 2: 14-fluid I, 15-fluid II;

FIG. 3 is a schematic representation of a cross-sectional derivative of the flow channels of a heat exchanger of the present invention in a hexagonal close packed arrangement;

reference numbers and corresponding part names in fig. 3: 5-round corner, 6-chamfer, 7-arc edge, 8-wave edge, 9-triangle tooth-shaped edge and 10-sawtooth edge.

FIG. 4 is a three-dimensional axial schematic view of the hexagonal close packed spiral heat exchanger fluid passages of the present invention;

FIG. 5 is a three-dimensional axial schematic view of the flow channels of a hexagonally close packed straight-through heat exchanger of the present invention;

FIG. 6 is a schematic three-dimensional axial view of fluid passages of a hexagonal close packed space three-dimensional heat exchanger according to the present invention;

FIG. 7 is a schematic cross-sectional view of the fluid passages of the quadrilateral closely packed heat exchanger of the present invention;

reference numbers and corresponding part names in fig. 7: 1-edge of unit flow channel, 2-partition wall, 3-fluid I, 4-fluid II.

FIG. 8 is a schematic representation of a cross-sectional derivative of the fluid passages of a quadrilateral closely packed heat exchanger according to the invention;

reference numbers and corresponding part names in fig. 8: 5-round corner, 6-chamfer, 7-arc edge, 8-wave edge, 9-triangle tooth-shaped edge and 10-rectangle tooth-shaped edge.

FIG. 9 is a three-dimensional axial view of the fluid passages of the quadrilateral closely packed spiral heat exchanger of the present invention;

FIG. 10 is a three-dimensional axial view of the flow channels of a quadrilateral closely packed straight-through heat exchanger of the present invention;

FIG. 11 is a schematic three-dimensional axial view of fluid passages of a quadrilateral closely packed space three-dimensional heat exchanger according to the present invention;

FIG. 12 is a schematic cross-sectional view of the triangular closely packed heat exchanger fluid passages of the present invention;

reference numbers and corresponding part names in fig. 12: 1-edge of unit flow channel, 2-partition wall, 3-fluid I, 4-fluid II.

FIG. 13 is a schematic representation of a cross-sectional derivative of the triangular closely packed heat exchanger fluid passages of the present invention;

reference numbers and corresponding part names in fig. 13: 5-round corner, 6-chamfer, 7-arc edge, 8-wave edge, 9-triangle tooth-shaped edge and 10-rectangle tooth-shaped edge.

FIG. 14 is a three-dimensional axial view of the triangular closely packed spiral heat exchanger fluid passages of the present invention;

FIG. 15 is a three-dimensional axial view of the triangular closely packed flow channels of a straight-through heat exchanger of the present invention;

FIG. 16 is a three-dimensional axial schematic view of the fluid passages of the closely spaced triangular-shaped three-dimensional heat exchanger of the present invention;

FIG. 17 is a schematic longitudinal cross-sectional derivative of a heat exchange fluid channel of the present invention; FIG. 17 (a), (b) and (c) show three forms of longitudinal sectional derivatives of the unit flow channel, respectively;

reference numbers and corresponding part names in fig. 17: 11-longitudinal section wave shape; 12-longitudinal section rectangular tooth form; 13-triangular tooth profile in longitudinal section.

FIG. 18 is a comparison of the arrangement of the flow channels of the heat exchanger of example 1; wherein (a) is a printed circuit board heat exchanger (PCHE) flow channel; (b) heat exchanger fluid channels are densely arranged in a hexagon;

FIG. 19 is the heat exchanger performance of example 1;

FIG. 20 is a schematic view of a straight-through flow channel heat exchanger according to embodiment 1;

FIG. 21 is a comparison of the arrangement of the flow channels of the heat exchanger of example 2; wherein (a) is a printed circuit board heat exchanger (PCHE) flow channel; (b) the fluid channels of the heat exchanger are closely arranged in a quadrilateral shape;

FIG. 22 is the heat exchanger performance of example 2; wherein (a) is the change relation of the total heat transfer coefficient with the Reynolds number; (b) the change relation of the Nurselt number with the Reynolds number;

FIG. 23 is a schematic view of a spiral fluid channel heat exchanger according to embodiment 2;

FIG. 24 is a schematic view of a space-curved fluid channel heat exchanger according to example 2;

FIG. 25 is a comparison of the arrangement of the flow channels of the heat exchanger of example 3; wherein (a) is a printed circuit board heat exchanger (PCHE) flow channel; (b) heat exchanger fluid channels are tightly arranged in a trilateral shape;

FIG. 26 is the heat exchanger performance of example 3;

FIG. 27 is a schematic view of a space-curved fluid channel heat exchanger according to example 3;

FIG. 28 is a schematic diagram of a cross-sectional structure of a heat exchange fluid channel designed by using the Thiessen polygon algorithm.

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is further described in detail below with reference to examples and accompanying drawings, and the exemplary embodiments and descriptions thereof are only used for explaining the present invention and are not meant to limit the present invention.

Example 1

The present embodiment provides a heat exchange fluid channel and a heat exchanger: as shown in fig. 1, in the cross section of the fluid channel, a plurality of unit runners are arranged, all the unit runners are regular hexagons with equal size, the number of the unit runners distributed around each unit runner is equal to the number of sides, and the adjacent sides of any two adjacent runners are correspondingly parallel in opposite directions. The heat conductors between the adjacent sides of the adjacent unit runners are used as partition walls, the thicknesses of all the partition walls are equal, and the side lengths of all the partition walls are equal; the side length of each unit flow channel is 0.01 mm-50 mm, such as 0.02mm, 0.05mm, 0.08mm, 1mm, 10mm, 20mm, 30mm and 40 mm; the thickness of the partition wall is 0.001 mm-20 mm, such as 0.003mm, 0.005mm, 0.01mm, 0.05mm, 0.10mm, 0.50mm, 1mm, 5mm, 10mm, 30mm, 40 mm. As shown in fig. 3, the joints between the adjacent edges of the unit flow channels may be transited by round corners or chamfers; the shape of any one, or two or more edges of the unit flow channel comprises an arc-shaped, wave-shaped or zigzag structure.

All the fluid channels are spirally arranged along the axial direction and are used as spiral heat exchange fluid channels; such as described in fig. 4, the cross-section of the fluid channel is stretched while rotating in the axial direction to form such a spiral heat exchange fluid channel. Or all the fluid channels are in a linear structure along the axial direction and are used as straight-through heat exchange fluid channels; such a straight-through heat exchanger fluid passage is formed by stretching the fluid passage cross-section along a straight line normal to the flow direction, as shown, for example, in fig. 5. Or all the fluid channels extend along a space curve to serve as curve-shaped heat exchange fluid channels, extend along the space curve and are spirally arranged along the axial direction of the current fluid channel, or the ends of partial channels serving as the curve-shaped heat exchange fluid channels are in a linear structure or a spiral structure; for example, as shown in fig. 6, the cross-section of the fluid channel is stretched along a space curve to form a space three-dimensional heat exchanger fluid channel, and the cross-section of the fluid channel can also be rotated along the stretching of the space curve or along the stretching of a part of the space curve or a part of a straight line. The cross-section and longitudinal section of the heat exchanger profile are identical to the profile configuration of all the fluid channel arrangements. The longitudinal cross-sectional shape of the fluid channel includes wave-shaped, zigzag-shaped, longitudinal fins, and other derivative structures, as shown in fig. 17.

The heat exchanger is preferably integrally formed, such as by 3D printing or smart manufacturing techniques.

Based on the type division for circulating fluid in each unit flow channel, the plurality of unit flow channels comprise a hot unit flow channel and a cold unit flow channel; the hexagonal fluid channel arrangement form of the embodiment mainly has two optimization schemes:

the first method comprises the following steps: as shown in fig. 1, the planning is performed according to the principle of the interval arrangement of a row of hot unit runners and a row of cold unit runners, four cold unit runners are distributed around each hot unit runner, and four hot unit runners are distributed around each cold unit runner.

And the second method comprises the following steps: as shown in fig. 2, the heat unit flow channels are all distributed around each cold unit flow channel, and three cold unit flow channels are distributed around each heat unit flow channel. For example, when one of the heat exchange fluids is a utility fluid and the other is a process fluid, for example, the utility fluid is used as a hot fluid and the process fluid is used as a cold fluid; the effective heat transfer efficiency can be maximized by planning all the utility flow channels around each process flow channel.

This embodiment is further described by taking the second scheme as an example, and is a comparison of the arrangement of the heat exchanger flow channels as shown in fig. 18. In the completed calculation analysis, the heat exchanger of the invention is applied under the working condition of single-phase flow heat exchange, as shown in fig. 19, the heat exchanger (water-water heat exchange as an example) based on the optimized design of the embodiment shows excellent performance, and in the high Reynolds number interval, the total heat exchange coefficient can be stably higher than 8000W/(m)²C.g. to be prepared into a preparation. Compared with various types of water-water phase-change-free heat exchange heat exchangers designed and manufactured by the conventional technology, the heat exchanger provided by the embodiment has obvious advantages, and is shown in table 1:

table 1 heat exchanger characteristic parameters of example 1 were compared with conventional heat exchangers

Serial number	Form of heat exchanger	Total heat transfer coefficient (water-water heat transfer) W/(m)2·℃)
			1	Shell-and-tube heat exchanger	300～2300
2	Sleeve type heat exchanger	700～1500
			3	Spiral tube type heat exchanger	300～530
4	Plate heat exchanger	2900～4650
			5	Spiral plate heat exchanger	1700～2200
6	Heat exchanger of example 1	2500～15000

Example 2

The present embodiment provides a heat exchange fluid channel and a heat exchanger: as shown in fig. 7, in the cross section of the fluid channel, a plurality of unit runners are arranged, all the unit runners are regular quadrangles with equal size, the number of the unit runners distributed around each unit runner is equal to the number of sides, and adjacent sides of any two adjacent runners are correspondingly parallel in opposite directions. The heat conductors between the adjacent sides of the adjacent unit runners are used as partition walls, the thicknesses of all the partition walls are equal, and the side lengths of all the partition walls are equal; the side length of each unit flow channel is 0.01 mm-50 mm, such as 0.02mm, 0.05mm, 0.08mm, 1mm, 10mm, 20mm, 30mm and 40 mm; the thickness of the partition wall is 0.01 mm-10 mm, such as 0.02mm, 0.05mm, 0.08mm, 1mm, 5mm, 9 mm. As shown in fig. 8, the joints between the adjacent edges of the unit flow channels may be transited by round corners or chamfers; the shape of any one, or two or more edges of the unit flow channel comprises an arc-shaped, wave-shaped or zigzag structure.

All the fluid channels are spirally arranged along the axial direction and are used as spiral heat exchange fluid channels; such as described in fig. 9, the cross-section of the fluid channel is stretched while rotating in the axial direction to form such a spiral heat exchange fluid channel. Or all the fluid channels are in a linear structure along the axial direction and are used as straight-through heat exchange fluid channels; such a straight-through heat exchanger fluid passage is formed by stretching the fluid passage cross-section along a straight line normal to the flow direction, as shown, for example, in fig. 10. Or all the fluid channels extend along a space curve to serve as curve-shaped heat exchange fluid channels, extend along the space curve and are spirally arranged along the axial direction of the current fluid channel, or the ends of partial channels serving as the curve-shaped heat exchange fluid channels are in a linear structure or a spiral structure; for example, as shown in fig. 11, the cross-section of the fluid channel is stretched along a space curve to form a space three-dimensional heat exchanger fluid channel, and the cross-section of the fluid channel can also be rotated along the stretching of the space curve or along the stretching of a part of the space curve or a part of a straight line. The cross-section and longitudinal section of the heat exchanger profile are identical to the profile configuration of all the fluid channel arrangements. The longitudinal cross-sectional shape of the fluid channel includes wave-shaped, zigzag-shaped, longitudinal fins, and other derivative structures, as shown in fig. 17.

The heat exchanger is preferably integrally formed, such as by 3D printing or smart manufacturing techniques.

Based on the type division for circulating fluid in each unit flow channel, the plurality of unit flow channels comprise a hot unit flow channel and a cold unit flow channel; the optimization scheme of the quadrilateral fluid channel arrangement form in the embodiment is as follows:

as shown in fig. 7, the heat unit flow channels are all distributed around each cold unit flow channel, and the heat unit flow channels are all distributed around each cold unit flow channel.

Further explanation is given by taking the optimization scheme as an example, and as shown in fig. 21, the heat exchanger flow channel arrangement is compared. In the completed calculation analysis, the heat exchanger of the present invention is applied under the working condition of single-phase flow heat exchange, as shown in fig. 22, the heat exchanger (water-water heat exchange as an example) based on the optimized design of the present embodiment shows superior performance, and in the high reynolds number region, the total heat exchange coefficient can be stably higher than 10000W/(m)²C.g. to be prepared into a preparation. Compared with various types of water-water phase-change-free heat exchange heat exchangers designed and manufactured by the conventional technology, the heat exchanger provided by the embodiment has obvious advantages, and is shown in table 2:

table 2 heat exchanger characteristic parameters of example 2 compared to conventional heat exchangers

Serial number	Form of heat exchanger	Total heat transfer coefficient (water-water heat transfer) W/(m)2·℃)
			1	Shell-and-tube heat exchanger	300～2300
2	Sleeve type heat exchanger	700～1500
			3	Spiral tube type heat exchanger	300～530
4	Plate heat exchanger	2900～4650
			5	Spiral plate heat exchanger	1700～2200
6	Heat exchanger of example 2	4200～13500

Example 3

The present embodiment provides a heat exchange fluid channel and a heat exchanger: as shown in fig. 12, in the cross section of the fluid channel, a plurality of unit runners are arranged, all the unit runners are regular triangles with equal size, the number of the unit runners distributed around each unit runner is equal to the number of sides, and adjacent sides of any two adjacent runners are correspondingly parallel in opposite directions. The heat conductors between the adjacent sides of the adjacent unit runners are used as partition walls, the thicknesses of all the partition walls are equal, and the side lengths of all the partition walls are equal; the side length of each unit flow channel is 0.01 mm-50 mm, such as 0.02mm, 0.05mm, 0.08mm, 1mm, 10mm, 20mm, 30mm and 40 mm; the thickness of the partition wall is 0.01 mm-10 mm, such as 0.02mm, 0.05mm, 0.08mm, 1mm, 5mm, 9 mm. As shown in fig. 13, the joints between the adjacent edges of the unit flow channels may be transited by round corners or chamfers; the shape of any one, or two or more edges of the unit flow channel comprises an arc-shaped, wave-shaped or zigzag structure.

All the fluid channels are spirally arranged along the axial direction and are used as spiral heat exchange fluid channels; such as described in fig. 14, the fluid channel cross-section is stretched in axial direction while rotating, forming such a spiral heat exchange fluid channel. Or all the fluid channels are in a linear structure along the axial direction and are used as straight-through heat exchange fluid channels; such a straight-through heat exchanger fluid passage is formed by stretching the fluid passage cross-section along a straight line normal to the flow direction, as shown, for example, in fig. 15. Or all the fluid channels extend along a space curve to serve as curve-shaped heat exchange fluid channels, extend along the space curve and are spirally arranged along the axial direction of the current fluid channel, or the ends of partial channels serving as the curve-shaped heat exchange fluid channels are in a linear structure or a spiral structure; for example, as shown in fig. 16, the cross-section of the fluid channel is stretched along a space curve to form a space three-dimensional heat exchanger fluid channel, and the cross-section of the fluid channel can also be rotated along the stretching of the space curve or along the stretching of a part of the space curve or a part of a straight line. The cross-section and longitudinal section of the heat exchanger profile are identical to the profile configuration of all the fluid channel arrangements. The longitudinal cross-sectional shape of the fluid channel includes wave-shaped, zigzag-shaped, longitudinal fins, and other derivative structures, as shown in fig. 17.

The heat exchanger is preferably integrally formed, such as by 3D printing or smart manufacturing techniques.

Based on the type division for circulating fluid in each unit flow channel, the plurality of unit flow channels comprise a hot unit flow channel and a cold unit flow channel; the optimization scheme of the triangular fluid channel arrangement form in the embodiment is as follows:

as shown in fig. 12, the heat unit flow channels are all distributed around each cold unit flow channel, and the heat unit flow channels are all distributed around each cold unit flow channel.

Further explanation is given by taking the optimization scheme as an example, and as shown in fig. 25, the heat exchanger flow channel arrangement is compared. In the completed calculation analysis, the heat exchanger applied with the present invention is subjected to calculation analysis under the working condition of single-phase flow heat exchange, as shown in fig. 26, the heat exchanger (water-water heat exchange as an example) optimally designed based on the present embodiment exhibits superior performance, and in the high reynolds number region, the total heat exchange coefficient can be stably higher than 10000W/(m) W²C.g. to be prepared into a preparation. Compared with various types of water-water phase-change-free heat exchange heat exchangers designed and manufactured by the conventional technology, the heat exchanger provided by the embodiment has obvious advantages, and is shown in table 3:

table 3 heat exchanger characteristic parameters of example 3 compared to conventional heat exchangers

The above-mentioned embodiments are intended to illustrate the objects, technical solutions and advantages of the present invention in further detail, and it should be understood that the above-mentioned embodiments are merely exemplary embodiments of the present invention, and are not intended to limit the scope of the present invention, and any modifications, equivalent substitutions, improvements and the like made within the spirit and principle of the present invention should be included in the scope of the present invention.