Heat exchanger and heat exchange system

Abstract

The application relates to a heat exchanger and a heat exchange system, wherein the heat exchanger comprises a first heat exchange part, the first heat exchange part is provided with a heat exchange cavity, a first interface and a second interface, the first interface and the second interface are arranged at intervals along the length direction of the first heat exchange part and are respectively communicated with the heat exchange cavity; a plurality of turbulence columns are arranged at intervals on the wall surface of the heat exchange cavity, the turbulence columns are provided with a first side and a second side, the first side and the second side are respectively inclined to the length direction of the first heat exchange part, and the first side and the second side are connected to each other on the side facing the first interface, the included angle between the first side and the second side is defined as alpha, and 45 DEG <= alpha <= 90 DEG; the heat exchanger can reduce the flow resistance generated on the refrigerant.

Description

Technical Field

[0001] This application relates to the field of heat dissipation technology for electronic components, specifically to a heat exchanger and heat exchange system. Background Technology

[0002] In heat exchangers that utilize the phase change and thermosiphon principle of refrigerant to exchange heat with electronic components, the electronic components are arranged on the surface of the evaporator. When the electronic components dissipate heat during operation, the liquid refrigerant in the evaporator absorbs heat, evaporates, and continuously flows upward. At the top of the evaporator, it becomes a refrigerant with high dryness but not completely vaporized. The incompletely vaporized refrigerant enters the condenser, exchanges heat with the air, and then condenses into a subcooled liquid. The subcooled liquid returns to the bottom of the evaporator, and the next cycle begins. Multiple turbulence columns can be arranged in a row inside the evaporator to divert and turbulent the refrigerant, thereby improving heat exchange. However, in related technologies, the turbulence columns are rectangular or circular, which create significant flow resistance for the refrigerant during its upward evaporation, hindering the refrigerant's evaporation flow. Utility Model Content

[0003] The first aspect of this application provides a heat exchanger that can reduce the flow resistance to the refrigerant.

[0004] The heat exchanger provided in the first aspect of this application includes a first heat exchange section, the first heat exchange section having a heat exchange cavity, a first interface and a second interface, the first interface and the second interface being arranged at intervals along the length direction of the first heat exchange section and respectively communicating with the heat exchange cavity; the wall surface of the heat exchange cavity is provided with a plurality of turbulence columns at intervals, the turbulence columns being provided with a first side and a second side, the first side and the second side being inclined to the length direction of the first heat exchange section respectively, and the first side and the second side being connected to each other on the side facing the first interface, the included angle between the first side and the second side being defined as α, then 45°≤α≤90°.

[0005] The heat exchanger has a first side and a second side, which are connected to each other on the side facing the first interface, with an included angle α of 45° to 90°. When the heat exchanger operates as an evaporator, the refrigerant in the heat exchange chamber absorbs heat and evaporates. During the flow from the first interface to the second interface, because the first and second sides facing the first interface are inclined along the length of the first heat exchange section at an angle of 45° to 90°, this arrangement can both disturb the refrigerant and reduce the flow resistance to the refrigerant, which is beneficial to the evaporation flow of the refrigerant.

[0006] A second aspect of this application provides a heat exchange system including a first heat exchanger and a second heat exchanger. The first heat exchanger is the same as the heat exchanger provided in the first aspect. The first interface and the second interface are respectively connected to the second heat exchanger and the heat exchange chamber. The second heat exchanger is closer to the second interface than the first interface.

[0007] When the heat exchange system is working, the first heat exchanger can act as an evaporator and the second heat exchanger can act as a condenser. The refrigerant enters the second heat exchanger through the second port, condenses into a subcooled liquid in the second heat exchanger, and then circulates back to the first heat exchanger through the first port. During this process, because the heat exchanger in the first aspect can reduce the flow resistance to the refrigerant, the refrigerant can circulate more quickly, thereby improving the heat exchange efficiency of the heat exchange system. Attached Figure Description

[0008] Figure 1 A schematic diagram of the overall structure of the heat exchanger provided in this application in a specific embodiment; Figure 2 A schematic diagram of the structure of the heat exchanger provided in this application in a second specific embodiment; Figure 3 for Figure 2 A schematic diagram of the turbulence column of the intermediate heat exchanger in one specific embodiment; Figure 4 A schematic diagram of the structure of the heat exchanger provided in this application in a second specific embodiment; Figure 5 for Figure 4 A schematic diagram of the turbulence column of the intermediate heat exchanger in one specific embodiment; Figure 6 for Figure 1 Schematic diagram of the planar structure of the intermediate heat exchanger; Figure 7 A schematic diagram of the structure of the heat exchanger provided in this application in a fourth specific embodiment; Figure 8 A schematic diagram of the structure of the heat exchange system provided in this application in a specific embodiment.

[0009] Reference numerals: First heat exchange section 1, heat exchange cavity 11, turbulence column 12, first side 121, second side 122, third side 123, fourth side 124, transition fillet 125, arc edge 126, first column 127, second column 128, first interface 13, second interface 14, base plate 15, cover plate 16, second heat exchanger 2, first manifold 21, second manifold 22, first connecting pipe 23, second connecting pipe 24, heat exchange tube 25, first surface 3.

[0010] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. Detailed Implementation

[0011] To better understand the technical solution of this application, the embodiments of this application will be described in detail below with reference to the accompanying drawings.

[0012] It should be understood that the term "and / or" used in this application is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, or B existing alone. Furthermore, the character " / " in this document generally indicates that the preceding and following related objects have an "or" relationship.

[0013] It should be noted that the directional terms such as "up," "down," "left," and "right" described in this application are used to describe the angles shown in the accompanying drawings and should not be construed as limiting the embodiments of this application. Furthermore, in the context, it should be understood that when an element is mentioned as being connected "up" or "down" to another element, it can be directly connected to the other element "up" or "down," or indirectly connected to the other element "up" or "down" through an intermediate element.

[0014] like Figure 1-7 As shown, the first aspect of this application provides a heat exchanger, which mainly includes a first heat exchange section 1. The first heat exchange section 1 has a heat exchange cavity 11, a first interface 13 and a second interface 14. The first interface 13 and the second interface 14 are arranged at intervals along the length direction of the first heat exchange section 1 and are respectively connected to the heat exchange cavity 11. The wall surface of the heat exchange cavity 11 is provided with a plurality of turbulence columns 12 at intervals. The turbulence columns 12 are provided with a first side 121 and a second side 122. The first side 121 and the second side 122 are respectively inclined to the length direction of the first heat exchange section 1, and the first side 121 and the second side 122 are connected to each other on the side facing the first interface 13. The included angle between the first side 121 and the second side 122 is defined as α, then 45°≤α≤90°.

[0015] like Figure 1As shown, the outer wall of the first heat exchange section 1 has a mounting surface for attaching and mounting electronic components. The heat emitted by the electronic components during operation can be transferred through the first heat exchange section 1 to the heat exchange cavity 11. The refrigerant filled in the heat exchange cavity 11 absorbs heat and evaporates, carrying away the heat emitted by the electronic components, thereby dissipating heat from the electronic components. In this embodiment, the first interface 13 and the second interface 14 are arranged at intervals along the length direction of the first heat exchange section 1, preferably located on both sides of the first heat exchange section 1 near its end along its length direction. That is, the first interface 13 is located on the side of the first heat exchange section 1 near the bottom, and the second interface 14 is located on the side of the first heat exchange section 1 near the top. The refrigerant evaporates and flows from the side of the first interface 13 to the side of the second interface within the first heat exchange section 1. Of course, in some other embodiments, the first interface 13 and the second interface 14 can also be located on both sides of the first heat exchange section 1 along its width direction, equal to the length direction, as long as the first interface 13 is near the bottom and the second interface 14 is near the top during use. This will not be elaborated upon further in this article.

[0016] The heat exchanger's turbulence column 12 is provided with a first side 121 and a second side 122, which are connected to each other on the side facing the first interface 13, and the included angle α between the first side 121 and the second side 122 is 45°~90°. When the heat exchanger operates as an evaporator, the refrigerant in the heat exchange chamber 11 absorbs heat and evaporates. During the flow from the first interface 13 to the second interface 14, because the first side 121 and the second side 122 facing the first interface 13 are respectively inclined to the length direction of the first heat exchange section 1, and the included angle is 45°~90°, this arrangement angle can reduce the flow resistance to the refrigerant while creating a disturbance, which is beneficial to the evaporation flow of the refrigerant.

[0017] It should be further explained that during the flow of refrigerant from the first port 13 to the second port 14, if the turbulence column 12 is rectangular or circular, the contact area with the refrigerant on the side facing the first port 13 is large, resulting in greater flow resistance and reducing the refrigerant's flow rate. In this embodiment, the angle between the first side 121 and the second side 122 of the turbulence column 12 on the side facing the first port 13 is 45°~90°, that is, the first side 121 and the second side 122 have a small-angled sharp corner. After passing the sharp corner, the refrigerant is more easily split into two streams, and such splitting has a smaller impact on the refrigerant flow rate. After being split, the refrigerant flows along the surfaces of the first side 121 and the second side 122 respectively. Due to the change in the angle of the turbulence column 12, the cross-section of the turbulence column 12 gradually expands, the fluid velocity decreases, and the static pressure increases, causing a lateral pressure gradient to be generated on the surface of the turbulence column 12. Some fluid detaches from the wall and forms a shear layer, forcing some fluid to flow laterally from the high-pressure area to the low-pressure area. This lateral flow, combined with the mainstream direction, forms a smaller vortex. The shear layers on both sides detach in opposite directions, forming symmetrical but oppositely rotating vortices in the channel, i.e., "bidirectional vortices", thereby destroying the fluid boundary layer and improving the convective heat transfer coefficient.

[0018] Furthermore, since the turbulence columns 12 are arranged at intervals, the fluid can enter the region of the next turbulence column 12 along the flow direction before the vortex generated by the previous turbulence column 12 has completely decayed. The vortex maintains periodic regeneration in the channel, avoids flow dead zones, reduces local overheating, and can improve the overall temperature uniformity.

[0019] like Figure 1 As shown, in one specific embodiment, the first heat exchange section 1 further includes a substrate 15 and a cover plate 16. The heat exchange cavity 11 is located between the substrate 15 and the cover plate 16, and the turbulence column 12 is integrally disposed on the inner wall of the substrate 15. Specifically, the substrate 15 is a plate with a certain depth and has a groove extending along the thickness direction. The heat exchange cavity 11 is formed by the substrate 15 and the cover plate 16 closing the groove. The first interface 13 and the second interface 14 are disposed on the cover plate 16. In addition, to ensure structural strength, the substrate 15 and the cover plate 16 can be integrally formed by welding. During installation and use, electronic components can be connected to the substrate 15 by bolts, and thermally conductive silicone grease is filled between the contact surfaces of the electronic components and the substrate 15 to reduce the contact thermal resistance between the electronic components and the substrate 15. The thermal conductivity of the thermally conductive silicone grease is 3 W / mK. The refrigerant filled in the heat exchange chamber 11 can be R134A, R1234yf, R1233zd, etc., and can be selected according to the actual heat exchange requirements and costs. This article does not make specific restrictions on this.

[0020] like Figure 3As shown, in one specific embodiment, the turbulence column 12 is provided with a third side 123 and a fourth side 124. The third side 123 and the fourth side 124 are respectively inclined to the length direction of the first heat exchange section 1, and the third side 123 and the fourth side 124 are connected to each other on the side facing the second interface 14. The other side of the third side 123 is connected to the first side 121, and the other side of the fourth side 124 is connected to the second side 122. The included angle between the third side 123 and the fourth side 124 is defined as β, then 45°≤β≤90°.

[0021] Based on the angle between the first side 121 and the second side 122 being 45°~90°, in this embodiment, the angle between the third side 123 and the fourth side 124, which face the second interface 14 (away from the first interface 13), is also 45°~90°. That is, the cross-section of the turbulence column 12 gradually decreases at the tail end, which can guide the refrigerant after it has been diverted, allowing it to smoothly turn and flow to the next turbulence column 12. The refrigerant is continuously diverted and merged by the action of multiple turbulence columns 12, thereby making the refrigerant flow more evenly and more widely in the heat exchange cavity 11, improving the overall heat exchange efficiency.

[0022] Furthermore, the included angle α between the first side 121 and the second side 122 and the included angle β between the third side 123 and the fourth side 124 may be the same or different, but in general, α and β are approximately the same. In addition, the angle between α and β is preferably an acute angle of 75°.

[0023] like Figure 4-5 As shown, in one specific embodiment, the first side 121 and the second side 122 are provided with a transition fillet 125 on the side where they are connected to each other. The turbulence column 12 is also provided with an arc edge 126. One side of the arc edge 126 is connected to the first side 121 and the other side is connected to the second side 122. The arc edge 126 protrudes outward from the first side 121 and the second side 122 on the side facing the second interface 14.

[0024] In this embodiment, the arc edge 126 connects to the first side 121 and the second side 122, and the shape of the turbulence column 12 formed by these three components is approximately teardrop-shaped. The function of the arc edge 126 is roughly the same as that of the third side 123 and the fourth side 124 in the previous embodiment, which is to guide and direct the refrigerant after it is split, allowing it to smoothly turn and flow to the next turbulence column 12. In addition, the curvature of the arc edge 126 can be preset according to the gap between two adjacent turbulence columns 12 and the angle of the flow, etc., which are not specifically limited in this article.

[0025] like Figure 4 and Figure 6-7As shown, in one specific embodiment, the plurality of turbulence columns 12 include a plurality of first columns 127 and a plurality of second columns 128. The plurality of first columns 127 are arranged at intervals along the length and width directions of the first heat exchange section 1, and the second columns 128 are staggered between at least a portion of two adjacent first columns 127 along the length of the first heat exchange section 1. The first columns 127 and the second columns 128 are similar in shape, and their sizes can be the same or different. In this embodiment, it is preferred that the first columns 127 and the second columns 128 have the same shape and size to facilitate processing.

[0026] In this embodiment, the second column 128 is offset between at least a portion of two adjacent first columns 127 along the length of the first heat exchange section 1. Of course, the second column 128 can also be offset between all adjacent two first columns 127 along the length of the first heat exchange section 1. Specifically, the reason for arranging the second column 128 is as follows: If only the first column 127 is arranged at intervals along the length and width of the first heat exchange section 1, although the flow resistance is low, the fluid "straight-through" effect is obvious. That is, a part of the refrigerant will flow straight through the gap of the unobstructed part of the first column 127 along the direction from the first interface 13 to the second interface 14. The heat transfer uniformity is poor, which can easily lead to a large temperature gradient inside the electronic components, which is not conducive to the safe use of the electronic components. After adding the second column 128, the second column 128, which is offset from the first column 127, can disturb a part of the "straight-through" refrigerant flowing along the gap, effectively avoiding the problem of flow dead zone, enhancing the turbulence effect, increasing the Nusselt number, and thus improving the convective heat transfer coefficient.

[0027] Specifically, when the heat exchanger is working, the refrigerant flows in the heat exchange chamber 11 along the direction from the first port 13 to the second port 14. The second column 128 can create disturbances to the passing refrigerant, so that at least part of the refrigerant can deviate from the original "straight-through" flow direction and flow, thereby enhancing the turbulence effect and improving heat exchange.

[0028] like Figure 6 As shown, in one specific embodiment, a surface perpendicular to the length direction of the first heat exchange section 1 and passing through at least two first pillars 127 is defined as the first surface 3, and the projection of the second pillar 128 on the first surface 3 is located between two adjacent first pillars 127.

[0029] In this embodiment, the projection of the second column 128 on the first surface 3 is located between two adjacent first columns 127, meaning that the projection of the second column 128 between the two adjacent first columns 127 maintains a certain gap with either of the two first columns 127. This arrangement allows a small portion of the refrigerant to maintain a "straight-through" flow. Because the refrigerant flows faster in this way, it can drive the diverted and converged refrigerant to flow upward more quickly, which is beneficial to improving heat exchange efficiency.

[0030] like Figure 7 As shown, in one specific embodiment, in the direction from the first interface 13 to the second interface 14, the gap between two adjacent first pillars 127 gradually increases, and / or, the gap between two adjacent second pillars 128 gradually increases.

[0031] Given that during the phase change heat transfer process, the refrigerant changes from a liquid phase to a gas phase as it flows from the first port 13 to the second port 14, its density gradually decreases while its volume gradually increases, resulting in a gas phase pressure greater than the liquid phase pressure. Therefore, in the direction from the first port 13 to the second port 14, when the gap between two adjacent first pillars 127 gradually increases, and / or the gap between two adjacent second pillars 128 gradually increases, the flow resistance to the gaseous refrigerant can be reduced while ensuring heat exchange, which is beneficial for the evaporative flow of the refrigerant during heat exchange. Generally, in the direction from the first port 13 to the second port 14, the gap between two adjacent first pillars 127 and the gap between two adjacent second pillars 128 gradually increase.

[0032] It should be noted that the gradual increase mentioned in this embodiment can refer to a linear gradual increase or a step-like gradual increase, which will not be elaborated upon in this article.

[0033] like Figure 7 As shown, in one specific embodiment, in the direction from the first interface 13 to the second interface 14, the distance between the centerline of the Nth first pillar 127 and the centerline of the adjacent second pillar 128 is defined as d. N If N≥2, the distance between the centerline of the (N-1)th first pillar 127 and the centerline of the adjacent second pillar 128 is d. N-1 , then d N =1.1d N-1 .

[0034] As can be seen from the previous embodiment, when the gap between two adjacent first pillars 127 gradually increases from the first interface 13 to the second interface 14, and / or the gap between two adjacent second pillars 128 gradually increases, the flow resistance can be reduced while ensuring heat exchange. Furthermore, in this embodiment, when the change trend of the distance between the centerline of the (N-1)th first pillar 127 and the centerline of the adjacent second pillar 128 remains at approximately 1.1 times, such a distance change is more reasonable, reducing flow resistance while maintaining disturbance to the refrigerant, which is beneficial for the evaporative flow of the refrigerant during heat exchange. In this embodiment, the relationship between the distance change between the first pillar 127 and the other second pillar 128 is the linear change mentioned in the previous embodiment.

[0035] like Figure 7 As shown, in a specific embodiment, along the length direction of the first heat exchange section 1, the distance between two adjacent first columns 127 is defined as Z, and the distance between one side of the first column 127 and one side of the adjacent second column 128 is defined as H. Then: 1≤H / Z≤1.5.

[0036] When the ratio of the distance Z between two adjacent first columns 127 to the distance H between one side of the first column 127 and one side of the adjacent second column 128 is kept between 1 and 1.5, a more reasonable distance can be maintained between the first columns 127 and between the first column 127 and the adjacent second column 128. This will not only play a role in turbulence but also avoid generating a large flow resistance to the refrigerant, thus balancing the overall performance.

[0037] like Figure 7 As shown, in one specific embodiment, if the length of the turbulence column 12 in the length direction of the first heat exchange section 1 is defined as L, and the width in the width direction of the first heat exchange section 1 is defined as W, then: 1 ≤ W / L ≤ 2. Along the refrigerant flow direction, if the included angle between the first side 121 and the second side 122 of the turbulence column 12 is too small, the ratio of the length L of the turbulence column 12 to its width W will be very large, which will have an adverse effect on the turbulence of the refrigerant, thereby affecting the heat exchange performance; however, if the included angle between the first side 121 and the second side 122 is too large, the ratio of the length L of the turbulence column 12 to its width W will become smaller, which will easily form excessive flow resistance. Therefore, when the ratio of the length L of the turbulence column 12 to its width W is kept within a reasonable range based on the angle, it can also play a role in balancing the overall performance.

[0038] like Figure 8As shown, the second aspect of the present application provides a heat exchange system, which mainly includes a first heat exchanger and a second heat exchanger 2. The first heat exchanger is the heat exchanger mentioned in the first aspect embodiment. The first interface 13 and the second interface 14 are respectively connected to the second heat exchanger 2 and the heat exchange chamber 11. The second heat exchanger 2 is closer to the second interface 14 than the first interface 13.

[0039] When the heat exchange system is working, the first heat exchanger can act as an evaporator, and the second heat exchanger 2 can act as a condenser. The refrigerant enters the second heat exchanger 2 through the second port 14, and after condensing into a subcooled liquid in the second heat exchanger 2, it circulates back to the first heat exchanger through the first port 13. In this process, since the heat exchanger in the first aspect embodiment can reduce the flow resistance to the refrigerant, the refrigerant can circulate more quickly, thereby improving the heat exchange efficiency of the heat exchange system.

[0040] like Figure 8 As shown, in one specific embodiment, the second heat exchanger 2 includes a first manifold 21, a second manifold 22, a first connecting pipe 23, a second connecting pipe 24, and a plurality of heat exchange tubes 25. The heat exchange tubes 25 are connected to the first manifold 21 and the second manifold 22. The first connecting pipe 23 is connected to the first interface 13 and the cavity of the first manifold 21, and the second connecting pipe 24 is connected to the second interface 14 and the cavity of the second manifold 22.

[0041] like Figure 8 As shown, after installation, the second heat exchanger 2 is positioned above the first heat exchanger at a certain height; that is, the vertical height of the second heat exchanger 2 is higher than that of the first heat exchanger. For better heat exchange, the second heat exchanger 2 can be a double-row structure, meaning the first manifold 21, the second manifold 22, and the heat exchange tubes 25 are all arranged in two rows. Furthermore, the heat exchange system includes a fan used to blow cool air onto the second heat exchanger 2, enabling forced convection heat exchange between the refrigerant and the air within the second heat exchanger 2, releasing heat. Figure 8 As shown, the second heat exchanger 2 can also be inclined to the horizontal plane at an angle of 5° to 15°, so that the liquid refrigerant condensed in the second heat exchanger 2 can be circulated back to the heat exchanger 11 by gravity through the first pipe 23 and the first interface 13.

[0042] The above examples illustrate the principles and implementation methods of this application. The descriptions of the embodiments are merely for the purpose of helping to understand the methods and core ideas of this application. It should be noted that those skilled in the art can make various improvements and modifications to this application without departing from its principles, and these improvements and modifications should also fall within the protection scope of this application.

Claims

1. A heat exchanger, characterized in that, The device includes a first heat exchange section (1), which has a heat exchange cavity (11), a first interface (13), and a second interface (14). The first interface (13) and the second interface (14) are arranged at intervals along the length direction of the first heat exchange section (1) and are respectively connected to the heat exchange cavity (11). The wall of the heat exchange cavity (11) is provided with a plurality of turbulence columns (12) at intervals. The turbulence columns (12) are provided with a first side (121) and a second side (122). The first side (121) and the second side (122) are respectively inclined to the length direction of the first heat exchange section (1), and the first side (121) and the second side (122) are connected to each other on the side facing the first interface (13). The included angle between the first side (121) and the second side (122) is defined as α, then 45°≤α≤90°.

2. The heat exchanger according to claim 1, characterized in that, The turbulence column (12) is provided with a third side (123) and a fourth side (124). The third side (123) and the fourth side (124) are inclined to the length direction of the first heat exchange part (1), and the third side (123) and the fourth side (124) are connected to each other on the side facing the second interface (14). The other side of the third side (123) is connected to the first side (121), and the other side of the fourth side (124) is connected to the second side (122). The included angle between the third side (123) and the fourth side (124) is defined as β, then 45°≤β≤90°.

3. The heat exchanger according to claim 1, characterized in that, The first side (121) and the second side (122) are provided with a transition fillet (125) on the side where they are connected to each other. The spoiler column (12) is also provided with an arc edge (126). One side of the arc edge (126) is connected to the first side (121), and the other side is connected to the second side (122). The arc edge (126) protrudes outward from the first side (121) and the second side (122) on the side facing the second interface (14).

4. The heat exchanger according to any one of claims 1-3, characterized in that, The plurality of the turbulence columns (12) include a plurality of first columns (127) and a plurality of second columns (128). The plurality of first columns (127) are arranged at intervals along the length and width directions of the first heat exchange section (1). The second columns (128) are staggered and disposed between at least a portion of two adjacent first columns (127) along the length of the first heat exchange section (1).

5. The heat exchanger according to claim 4, characterized in that, Define a surface perpendicular to the length direction of the first heat exchange section (1) and passing through at least two of the first columns (127) as the first surface (3), then the projection of the second column (128) on the first surface (3) is located between two adjacent first columns (127).

6. The heat exchanger according to claim 4, characterized in that, In the direction from the first interface (13) to the second interface (14), the gap between two adjacent first pillars (127) gradually increases, and / or the gap between two adjacent second pillars (128) gradually increases.

7. The heat exchanger according to claim 6, characterized in that, In the direction from the first interface (13) to the second interface (14), the distance between the centerline of the Nth first column (127) and the centerline of the adjacent second column (128) is defined as d. N N≥2, the distance between the centerline of the (N-1)th first column (127) and the centerline of the adjacent second column (128) is d. N-1 , then d N =1.1d N-1 .

8. The heat exchanger according to any one of claims 5-7, characterized in that, Along the length direction of the first heat exchange section (1), the distance between two adjacent first columns (127) is defined as Z, and the distance between one side of the first column (127) and one side of the adjacent second column (128) is defined as H. Then: 1≤H / Z≤1.

5.

9. The heat exchanger according to any one of claims 1-3 or 5-7, characterized in that, Let L be the length of the turbulence column (12) in the length direction of the first heat exchange section (1), and W be the width in the width direction of the first heat exchange section (1). Then: 1≤W / L≤2.

10. The heat exchanger according to any one of claims 1-3 or 5-7, characterized in that, The first heat exchange section (1) further includes a substrate (15) and a cover plate (16), the heat exchange cavity (11) is located between the substrate (15) and the cover plate (16), and the turbulence column (12) is integrally disposed on the inner wall of the substrate (15).

11. A heat exchange system, characterized in that, It includes a first heat exchanger and a second heat exchanger (2), the first heat exchanger is the heat exchanger according to any one of claims 1-10, the first interface (13) and the second interface (14) are respectively connected to the second heat exchanger (2) and the heat exchange chamber (11), and the second heat exchanger (2) is closer to the second interface (14) than the first interface (13).

12. The heat exchange system according to claim 11, characterized in that, The second heat exchanger (2) includes a first manifold (21), a second manifold (22), a first connecting pipe (23), a second connecting pipe (24), and a plurality of heat exchange tubes (25). The heat exchange tubes (25) connect the first manifold (21) and the second manifold (22). The first connecting pipe (23) connects the first interface (13) and the cavity of the first manifold (21). The second connecting pipe (24) connects the second interface (14) and the cavity of the second manifold (22).

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