Heat exchanger and air conditioner

Abstract

The invention discloses a heat exchanger and an air conditioner, the heat exchanger comprises a fin, the fin comprises a plurality of fin unit rows, each fin unit row comprises a plurality of fin units, and each fin unit is provided with a pipe hole; the heat exchange tubes are arranged in the tube holes in a penetrating manner; each fin unit comprises a flat area; the corrugated area protrudes towards one side, in the thickness direction, of the fin unit, the corrugated area comprises a first corrugated section, and the first corrugated section comprises a first inclined plane section and a second inclined plane section which are sequentially connected in the incoming flow direction; the transition area is respectively intersected with the first inclined plane section and the second inclined plane section; wherein the maximum height of the intersection of the first inclined plane section and the second inclined plane section is H, the minimum height of the intersection of the transition area and the first inclined plane section is H1, and H and H1 meet the relational expression that H1 is larger than or equal to 1 / 3 * H and smaller than or equal to 2 / 3 * H. By controlling the corrugation height in front of the heat exchange pipe, on one hand, the loss of the heat exchange area on the first corrugation section is reduced, and on the other hand, the flowing resistance of incoming flow can be reduced, so that the comprehensive heat exchange efficiency is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of air conditioners, and more particularly to a heat exchanger and an air conditioner. Background Art

[0002] As one of the core components of an air conditioning system, the heat exchange capacity of a heat exchanger directly affects the cooling and heating effects of the air conditioner. At the same time, the heat exchange capacity of the heat exchanger directly affects the energy efficiency ratio of the air conditioning system. Improving the heat exchange effect of the heat exchanger can also reduce the operating energy consumption of the air conditioner. Currently, the main forms of the fins of the outdoor heat exchanger used in air conditioners are corrugated fins and slotted fins. Due to the strong ability to disturb the air flow, the slotted fins have a higher convective heat transfer coefficient outside the tube compared to the corrugated fins. However, in the heating condition, the slotted fins are prone to form water bridges, have poor drainage performance, and are prone to frosting, which affects the heating capacity. Therefore, for heat pump air conditioners, each manufacturer mainly uses the form of corrugated fins. The corrugated fins generally have transverse corrugations added to the fin surface, and the number of corrugations, the corrugation angle, etc. are key design parameters.

[0003] In the related art, due to the existence of the hole bottom ring and the hole bottom angle in the corrugated fin, the corrugation shape is incomplete, resulting in the loss of part of the corrugation area and also weakening the heat exchange capacity of the corrugated fin for the incoming air flow. Summary of the Invention

[0004] The present invention aims to at least solve one of the technical problems existing in the prior art. For this reason, an object of the present invention is to provide a heat exchanger that can reasonably control the corrugation height in front of the heat exchange tube, on the one hand, reducing the loss of the heat exchange area on the first corrugation section, and on the other hand, reducing the flow resistance of the incoming flow, thereby improving the comprehensive heat exchange efficiency.

[0005] The present invention further provides an air conditioner.

[0006] The heat exchanger according to the first aspect of the present invention includes: fins, the fins include a plurality of rows of fin units, the plurality of rows of fin units are distributed in the width direction of the fins, each row of fin units includes a plurality of fin units distributed in the length direction of the fins, each fin unit is provided with a tube hole, and the tube holes in two adjacent rows of fin units are arranged staggeredly; heat exchange tubes, the heat exchange tubes are inserted into the tube holes, and a refrigerant flows through the heat exchange tubes; the fin unit includes: a flat area, the flat area is arranged along the circumferential direction of the tube hole; a corrugated area, the corrugated area surrounds the flat area, the corrugated area protrudes toward one side in the thickness direction of the fin unit, the corrugated area includes a first corrugated section, the first corrugated section includes a first inclined section and a second inclined section connected in sequence along the oncoming flow direction, and the first inclined section is inclined relative to the second inclined section; a transition area, the transition area is inclined and connected between the flat area and the corrugated area, and the transition area intersects with the first inclined section and the second inclined section respectively; wherein, the maximum height at the intersection of the first inclined section and the second inclined section is H, the minimum height at the intersection of the transition area and the first inclined section is H1, and H and H1 satisfy the relationship: 1 / 3×H≤H1≤2 / 3×H.

[0007] Thus, by providing this heat exchanger, the corrugation height in front of the heat exchange tubes can be reasonably controlled. On the one hand, the loss of the heat exchange area on the first corrugated section is reduced, and on the other hand, the flow resistance of the oncoming flow can be reduced, thereby improving the comprehensive heat exchange efficiency.

[0008] In some examples of the present invention, the corrugated area includes: the second corrugated section, along the oncoming flow direction, the second corrugated section is located downstream of the first corrugated section, the second corrugated section includes a third inclined section and a fourth inclined section connected in sequence along the oncoming flow direction, the third inclined section is inclined relative to the fourth inclined section, and the transition area intersects with the third inclined section and the fourth inclined section respectively; wherein, the minimum height at the intersection of the transition area and the fourth inclined section is H2, and H and H2 satisfy the relationship: 1 / 3×H≤H2≤2 / 3×H; or H1 and H2 satisfy the relationship: H1 = H2.

[0009] In some examples of the present invention, along the oncoming flow direction, the plane passing through the central axis of the tube hole and perpendicular to the oncoming flow direction is the interface, and the first corrugated section and the second corrugated section are symmetrical about the interface.

[0010] In some examples of the present invention, the plane where the flat area is located is the first reference plane. The width of the projection of the first inclined section on the first reference plane is d1, and the width of the projection of the second inclined section on the first reference plane is d2. The d1 and the d2 satisfy the relation: d1 ≤ d2; and / or the width of the projection of the third inclined section on the first reference plane is d3, and the width of the projection of the fourth inclined section on the first reference plane is d4. The d3 and the d4 satisfy the relation: d3 ≥ d4.

[0011] In some examples of the present invention, the plane parallel to the oncoming flow direction and passing through the central axis of the pipe hole is the second reference plane. The transition area forms an angle A on the second reference plane, and the transition area forms an angle B with the first reference plane. The A and the B satisfy the relation: B = (180° - A) / 2.

[0012] In some examples of the present invention, the B satisfies the relation: 30° ≤ B ≤ 45°.

[0013] In some examples of the present invention, the flat area is configured to be circular. The outer diameter of the flat area is D. The radial distance from the intersection of the first inclined section and the second inclined section to the central axis of the pipe hole is d5. The d1, the d5, the D, the H1, and the tanB satisfy the relation: d5 ≤ D / 2 + H1×tanB ≤ d1 + d5. d5 ≤ D / 2 and (D / 2 + H1×tanB) ≤ d5 + d1.

[0014] In some examples of the present invention, the fin unit further includes: a drainage section, which is arranged between the first corrugated section and the second corrugated section and is coplanar with the flat area; and / or a straight section, which is connected to both ends in the width direction of the fin unit.

[0015] In some examples of the present invention, the flat area is configured to be circular. The outer diameter of the flat area is D. The D satisfies the relation: D ≥ 9mm.

[0016] The air conditioner according to the second aspect of the present invention includes: the above-mentioned heat exchanger.

[0017] The additional aspects and advantages of the present invention will be partially given in the following description, partially will become obvious from the following description, or will be understood through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The above and / or additional aspects and advantages of the present invention will become obvious and easy to understand from the description of the embodiments in conjunction with the following drawings, wherein: Figure 1It is a schematic structural diagram of a heat exchanger according to an embodiment of the present invention; Figure 2 It is a schematic structural diagram of a fin according to an embodiment of the present invention; Figure 3 It is a front view of the fin according to an embodiment of the present invention; Figure 4 It is Figure 3 The cross-sectional view in the A-A direction in Figure 5 It is a front view of a fin unit according to an embodiment of the present invention; Figure 6 It is a schematic diagram of the mechanism of the fin from another angle according to an embodiment of the present invention; Figure 7 It is Figure 6 The enlarged view of area B in Figure 8 It is a schematic diagram of the comparison of the surface temperature field of the fin according to an embodiment of the present invention; Figure 9 It is a schematic diagram of the comparison of the heat transfer amount and j / f(1 / 3) under different wave heights according to an embodiment of the present invention.

[0019] Reference numerals: 100, heat exchanger; 1, fin; 11, fin unit; 111, tube hole; 112, flat area; 113, corrugated area; 1131, first corrugated section; 1132, first inclined section; 1133, second inclined section; 1134, second corrugated section; 1135, third inclined section; 1136, fourth inclined section; 114, transition area; 115, drainage section; 116, straight section; 12, fin unit row; 2, heat exchange tube. Detailed implementation manners

[0020] The embodiments of the present invention will be described in detail below. The embodiments described with reference to the drawings are exemplary.

[0021] Below with reference to Figures 1 - 9 Describe the heat exchanger 100 according to an embodiment of the present invention. The heat exchanger 100 can reasonably control the corrugation height in front of the heat exchange tube 2. On the one hand, it reduces the loss of the heat transfer area on the first corrugated section 1131, and on the other hand, it can also reduce the flow resistance of the oncoming flow.

[0022] Combined with Figures 1 - 9As shown, the heat exchanger 100 according to an embodiment of the first aspect of the present invention includes fins 1 and heat exchange tubes 2. Among them, the heat exchange tubes 2 can serve as a medium for heat exchange between the refrigerant and the outside air, and the refrigerant can flow inside (as a low-temperature and low-pressure liquid in the evaporator and a high-temperature and high-pressure gas in the condenser). The fins 1 are usually closely attached to the outer surface of the heat exchange tubes 2, so that the heat exchange contact area between the air and the heat exchange tubes 2 can be effectively increased, thereby accelerating the heat transfer speed and improving the heat exchange efficiency.

[0023] Combined with Figure 1 and Figure 2 As shown, the heat exchanger 100 includes several heat exchange tubes 2 and several fins 1. The several fins 1 are arranged side by side in parallel, with a certain distance between adjacent fins 1. The several heat exchange tubes 2 extend through each fin 1, and each heat exchange tube 2 in the several heat exchange tubes 2 is connected to the adjacent heat exchange tube 2 through a bent pipe, thereby forming a fluid channel for the heat exchange tubes 2. A fluid (such as a coolant) can flow in the fluid channel of the heat exchange tubes 2, and the fluid in the fluid channel of the heat exchange tubes 2 can exchange heat with the air flowing in the fin 1 fluid channel through the heat exchange tubes 2 and the fins 1.

[0024] The heat exchange tubes 2 can have any suitable size. The number of heat exchange tubes 2 can be arbitrary. The heat exchange tubes 2 can be made of any suitable material with good heat transfer performance. The number of fins 1 can also be arbitrary. The fins 1 can also have any suitable size. The fins 1 can be made of aluminum or any suitable metal material with good heat transfer performance. The length and width of the fins 1 can be adjusted according to the size of the fin-tube heat exchanger 100.

[0025] Specifically, combined with Figure 2 and Figure 3 As shown, the fin 1 includes a plurality of fin unit rows 12, and the plurality of fin unit rows 12 are distributed in the width direction of the fin 1. For example, as Figure 3 shown, the fin 1 can include two fin unit rows 12, and the two fin unit rows 12 are sequentially connected in the width direction of the fin 1. Of course, the present invention is not limited to this, and the fin 1 can also include three or more fin unit rows 12. When the fin 1 includes a plurality of fin unit rows 12, the heat exchange tubes 2 also correspondingly form multiple rows. The width direction of the fin 1 is the Figure 4 incoming flow direction shown.

[0026] Among them, as Figure 2 and Figure 3As shown, each fin unit row 12 includes a plurality of fin units 11 distributed along the length direction of the fin 1. Each fin unit 11 is provided with a tube hole 111, and the heat exchange tube 2 is inserted into the tube hole 111, and a refrigerant flows through the heat exchange tube 2. That is to say, each fin unit 11 can be connected to the heat exchange tube 2 through the tube hole 111, so as to finally achieve the heat exchange effect between the fin 1 and the heat exchange tube 2, thereby improving the heat exchange efficiency.

[0027] Furthermore, as Figure 2 and Figure 3 shown, the tube holes 111 in two adjacent fin unit rows 12 are arranged staggeredly. That is to say, each fin unit row 12 is mainly composed of a plurality of fin units 11 connected in sequence along the length direction of the fin 1, and the tube holes 111 in one fin unit row 12 and the tube holes 111 in another adjacent fin unit row 12 are arranged staggeredly. In this way, the heat exchange tubes 2 passing through the corresponding tube holes 111 can also be arranged staggeredly, which can avoid the mutual shielding of the heat exchange tubes 2 in different rows in the oncoming flow direction, and can further improve the heat exchange efficiency of the heat exchanger 100.

[0028] Specifically, in combination with Figure 2 , Figure 5 and Figure 7 shown, the fin unit 11 includes a flat area 112, and the flat area 112 is arranged along the circumferential direction of the tube hole 111. Among them, the flat area 112 is arranged around the outer periphery of the tube hole 111 along the circumferential direction of the tube hole 111, and the flat area 112 is flat. Such an arrangement can increase the contact area between the fin 1 and the tube hole 111, thereby helping to better conduct heat; it can also reduce the flow resistance of the fluid on the flat area 112 (that is, it can reduce the turbulence of the fluid between the fins 1), thereby improving the fluidity of the fluid; it can also provide a smoother flow channel, reduce the friction loss of the fluid, thereby increasing the flow velocity; it can also simplify the manufacturing process, reduce complex processing steps, and improve the production and manufacturing efficiency.

[0029] Furthermore, in combination with Figure 2 and Figure 5 shown, the fin unit 11 further includes a corrugated area 113, the corrugated area 113 is arranged around the flat area 112, and the corrugated area 113 protrudes toward one side in the thickness direction of the fin unit 11, and the corrugated area 113 continuously changes in the thickness direction (that is, the corrugated area 113 forms undulations in the thickness direction).

[0030] Among them, the corrugated area 113 includes a first corrugated section 1131, and the first corrugated section 1131 includes a first inclined section 1132 and a second inclined section 1133 connected in sequence along the oncoming flow direction, and the first inclined section 1132 is inclined relative to the second inclined section 1133.

[0031] It can be understood that, along the oncoming flow direction, the first inclined surface section 1132 and the second inclined surface section 1133 connected in sequence together form a convex shape in an inverted V shape. In this way, the mutually inclined first inclined surface section 1132 and the second inclined surface section 1133 can define a windward slope and a leeward slope, thereby increasing the heat exchange contact area with the air flow and also increasing the disturbance effect on the air flow, and further improving the heat exchange efficiency between the air flow and the fin 1.

[0032] Specifically, as shown in combination with Figure 2 , Figure 4 , Figure 5 and Figure 7 , the fin unit 11 further includes a transition region 114. The transition region 114 is inclinedly connected between the flat region 112 and the corrugated region 113, and the transition region 114 intersects with the first inclined surface section 1132 and the second inclined surface section 1133 respectively.

[0033] Among them, the transition region 114 can change the extension directions of the flat region 112 and the corrugated region 113, thereby connecting the three into a closely integrated whole; the transition region 114 can also smoothly transition the region from the flat region 112 to the corrugated region 113, thereby reducing the flow resistance of the fluid between different regions and reducing the turbulence of the fluid between different regions, thereby improving the flow smoothness of the fluid.

[0034] Particularly, as shown in combination with Figure 4 , the maximum height at the intersection of the first inclined surface section 1132 and the second inclined surface section 1133 is H, and the minimum height at the intersection of the transition region 114 and the first inclined surface section 1132 is H1. H and H1 can satisfy the relationship: 1 / 3×H ≤ H1. For example, H1 can be 1 / 3×H, or 0.4H, or 0.5H.

[0035] That is to say, the maximum height at the intersection of the first inclined surface section 1132 and the second inclined surface section 1133 (such as at the wave crest) is H, and the minimum height at the intersection of the transition region 114 and the first inclined surface section 1132 (that is, the windward slope) is H1. Since the smaller the minimum height at the intersection of the transition region 114 and the first inclined surface section 1132, the larger the corrugation loss area. When 1 / 3×H > H1, the part of the first inclined surface section 1132 adjacent to the transition region 114 is less, and the loss area of the first inclined surface section 1132 is more. The heat dissipation effect of the fin unit 11 itself using the corrugated region 113 on the heat exchange tube 2 is poor, affecting the heat exchange effect of the heat exchanger 100.

[0036] H and H1 can also satisfy the relationship: H1 ≤ 2 / 3 × H. For example, H1 can be 2 / 3 × H or 0.6H. The greater the minimum height at the intersection of the transition zone 114 and the first inclined surface section 1132, the greater the fluid resistance of the oncoming flow. When H1 > 2 / 3 × H, there are more parts of the first inclined surface section 1132 adjacent to the transition zone 114, and the loss area of the first inclined surface section 1132 is smaller. However, since the height of the part of the first inclined surface section 1132 adjacent to the transition zone 114 is larger, it will hinder the fluid flow between two adjacent fins 1, which has a greater impact on the smoothness of the fluid flow and will also affect the heat exchange effect of the heat exchanger 100.

[0037] H and H1 can also satisfy the relationship: 1 / 3 × H ≤ H1 ≤ 2 / 3 × H. When 1 / 3 × H ≤ H1 ≤ 2 / 3 × H, the corrugation loss area of the first corrugated section 1131 can be reduced, thereby increasing the heat exchange area of the first corrugated section 1131 for the oncoming flow; the flow resistance of the first inclined surface section 1132 for the oncoming flow can also be reduced (that is, the pressure drop when the oncoming flow passes through the first corrugated section 1131), thereby improving the smoothness of the fluid flow at the first corrugated section 1131, and further improving the comprehensive heat exchange efficiency of the heat exchanger 100.

[0038] Thus, by setting the heat exchanger 100, it can reasonably control the corrugation height in front of the heat exchange tube 2, reduce the loss of the heat exchange area on the first corrugated section 1131 on the one hand, and reduce the flow resistance of the oncoming flow on the other hand, thereby improving the comprehensive heat exchange efficiency.

[0039] According to some optional embodiments of the present invention, as shown in Figure 2 、 Figure 4 and Figure 5 shown, the corrugated area 113 includes a second corrugated section 1134. Along the oncoming flow direction, the second corrugated section 1134 is located downstream of the first corrugated section 1131. The second corrugated section 1134 can further increase the undulating contour of the corrugated area 113, thereby increasing the heat exchange contact area of the corrugated area 113, and further improving the heat exchange efficiency of the fin unit 11.

[0040] In addition, the above arrangement can also make the air flow pass through multiple corrugated sections formed on the corrugated sheet in sequence, thereby forming a periodic disturbance to the heat exchange air flow, and further improving the heat exchange efficiency of the fin 1.

[0041] Specifically, as shown in Figure 5 and Figure 7 shown, the second corrugated section 1134 includes a third inclined surface section 1135 and a fourth inclined surface section 1136 connected in sequence along the oncoming flow direction. The third inclined surface section 1135 is inclined relative to the fourth inclined surface section 1136, and the transition zone 114 intersects with the third inclined surface section 1135 and the fourth inclined surface section 1136 respectively.

[0042] It can be understood that, along the oncoming flow direction, the third inclined plane section 1135 and the fourth inclined plane section 1136 connected in sequence together form a convex shape in an inverted V shape. In this way, the mutually inclined third inclined plane section 1135 and the fourth inclined plane section 1136 can define a windward slope and a leeward slope, thereby increasing the heat exchange contact area with the air flow and also increasing the disturbance effect on the air flow, and further improving the heat exchange efficiency between the air flow and the fin 1.

[0043] Among them, in combination with Figure 2 , Figure 4 , Figure 5 and Figure 7 as shown, the minimum height at the intersection of the transition zone 114 and the fourth inclined plane section 1136 is H2, and H and H2 satisfy the relationship: 1 / 3×H ≤ H2. For example, H2 can be 1 / 3×H, or 0.4H, or 0.5H.

[0044] That is to say, the maximum height at the intersection of the third inclined plane section 1135 and the fourth inclined plane section 1136 (such as at the wave crest) is H2, and the minimum height at the intersection of the transition zone 114 and the first inclined plane section 1132 (that is, the windward slope) is H2. Since the smaller the minimum height at the intersection of the transition zone 114 and the third inclined plane section 1135, the larger the corrugation loss area. When 1 / 3×H > H2, the part of the third inclined plane section 1135 adjacent to the transition zone 114 is less, and the loss area of the third inclined plane section 1135 is more. The heat dissipation effect of the fin unit 11 itself on the heat exchange tube 2 using the corrugated area 113 is poor, affecting the heat exchange effect of the heat exchanger 100.

[0045] H and H2 can also satisfy the relationship: H2 ≤ 2 / 3×H. For example, H2 can be 2 / 3×H, or 0.6H. The larger the minimum height at the intersection of the transition zone 114 and the third inclined plane section 1135, the greater the fluid resistance of the oncoming flow. When H2 > 2 / 3×H, the part of the third inclined plane section 1135 adjacent to the transition zone 114 is more, and the loss area of the third inclined plane section 1135 is less. However, since the height of the part of the third inclined plane section 1135 adjacent to the transition zone 114 is larger, it will hinder the fluid flow between two adjacent fins 1, having a greater impact on the fluid flow smoothness and also affecting the heat exchange effect of the heat exchanger 100.

[0046] H and H2 can also satisfy the relationship: 1 / 3×H ≤ H2 ≤ 2 / 3×H. When 1 / 3×H ≤ H2 ≤ 2 / 3×H, in this way, the corrugation loss area of the second corrugated section 1134 can be reduced, thereby increasing the heat exchange area of the second corrugated section 1134 for the oncoming flow; the flow resistance of the third inclined plane section 1135 for the oncoming flow can also be reduced, thereby improving the fluid flow smoothness at the second corrugated section 1134, and further improving the comprehensive heat exchange efficiency of the heat exchanger 100.

[0047] Optionally, H1 and H2 satisfy the relationship: H1 = H2. It can be understood that the minimum height at the intersection of the transition region 114 and the first inclined surface segment 1132 is equal to the minimum height at the intersection of the transition region 114 and the fourth inclined surface segment 1136, so that the manufacturing consistency of the first corrugated segment 1131 and the second corrugated segment 1134 can be improved.

[0048] Specifically, in combination with Figure 2 , Figure 4 , Figure 5 and Figure 7 as shown, along the oncoming flow direction, the plane perpendicular to the oncoming flow direction passing through the central axis of the tube hole 111 is the interface plane, and the first corrugated segment 1131 and the second corrugated segment 1134 are symmetric about the interface plane.

[0049] That is to say, the first corrugated segment 1131 and the second corrugated segment 1134 are symmetrically arranged with respect to the interface plane, so that the first inclined surface segment 1132 and the second inclined surface segment 1133 on the first corrugated segment 1131 are symmetrically arranged with respect to the interface plane with the third inclined surface segment 1135 and the fourth inclined surface segment 1136 on the second corrugated segment 1134 respectively. Such an arrangement is convenient for production and manufacturing, and also helps to achieve a balanced heat distribution of the air flow, avoiding structural warping and angular deviation caused by thermal asymmetry, thereby improving the processability and heat transfer efficiency.

[0050] Furthermore, in combination with Figure 4 as shown, the plane where the flat region 112 is located is the first reference plane. The width of the projection of the first inclined surface segment 1132 on the first reference plane is d1, and the width of the projection of the second inclined surface segment 1133 on the first reference plane is d2. d1 and d2 satisfy the relationship: d1 ≤ d2.

[0051] It can be understood that when projected onto the first reference plane, the projection width of the first inclined surface segment 1132 is not less than that of the second inclined surface segment 1133. When the projection width of the first inclined surface segment 1132 is less than that of the second inclined surface segment 1133, it helps the intersection of the first inclined surface segment 1132 and the second inclined surface segment 1133 to shift away from the center of the tube hole 111, so that the loss of the corrugated area on the first corrugated segment 1131 can be reduced, effectively retaining the corrugated shape on the first corrugated segment 1131, and further improving the heat transfer efficiency of the fin 1.

[0052] In addition, when the projection width of the first inclined surface segment 1132 is equal to that of the second inclined surface segment 1133, that is, they are symmetric with each other, the manufacturing consistency can be improved, the manufacturing process can be simplified, and the production efficiency can be improved.

[0053] Optionally, in combination with Figure 4As shown, the width of the projection of the third inclined plane section 1135 on the first reference plane is d3, and the width of the projection of the fourth inclined plane section 1136 on the first reference plane is d4. d3 and d4 satisfy the relationship: d3 ≥ d4.

[0054] That is to say, when projected onto the first reference plane, the projected width of the fourth inclined plane section 1136 is not less than that of the third inclined plane section 1135. When the projected width of the fourth inclined plane section 1136 is less than that of the third inclined plane section 1135, it helps the intersection of the third inclined plane section 1135 and the fourth inclined plane section 1136 to shift away from the center of the tube hole 111. In this way, the loss of the corrugated area on the second corrugated section 1134 can be reduced, thereby effectively retaining the corrugated shape on the second corrugated section 1134, and further improving the heat exchange efficiency of the fin 1.

[0055] In addition, when the projected width of the third inclined plane section 1135 is equal to that of the fourth inclined plane section 1136, that is, they are symmetrical to each other, the manufacturing consistency can be improved, the manufacturing process can be simplified, and the production efficiency can be increased.

[0056] Specifically, as shown in Figure 4 In a plane parallel to the oncoming flow direction and passing through the central axis of the tube hole 111, it is the second reference plane. The transition zone 114 forms an angle A with the second reference plane, and the transition zone 114 forms an angle B with the first reference plane. A and B satisfy the relationship: B = (180° - A) / 2.

[0057] It can be understood that the transition zone 114 extends outwardly inclined away from the tube hole 111 along the radial direction of the tube hole 111. The angle A formed by the transition zone 114 on the second reference plane and the angle B formed by the transition zone 114 and the first reference plane establish a parameter relationship. In this way, the inclination angles of the transition zone 114 at the first corrugated section 1131 and the second corrugated section 1134 can be made the same, thus ensuring manufacturing consistency and improving production efficiency; it is also possible to control the minimum height H1 of the intersection of the transition zone 114 and the first inclined plane section 1132 and the minimum height H2 of the intersection of the transition zone 114 and the second inclined plane section 1133 by reasonably controlling the angle A (on the premise that the projected widths of the first corrugated section 1131 and the second corrugated section 1134 remain unchanged), so as to simultaneously take into account the reduction of the heat exchange area loss on the corrugated sheet and the reduction of the oncoming flow resistance, and further improve the comprehensive heat exchange efficiency of the heat exchanger 100.

[0058] Furthermore, as shown in Figure 4 B satisfies the relationship, 30° ≤ B ≤ 45°. For example, B can be 30°, 35°, 40°, 45°, etc., not limited to this.

[0059] Among them, the included angle B formed by the transition region 114 and the first reference plane is relatively small, so that it is beneficial to smoothly guide and converge the water vapor near the fin 1 onto the transition region 114, thereby improving the drainage effect.

[0060] Specifically, as shown in Figure 4 and Figure 5 , the flat region 112 is configured to be circular, the outer diameter of the flat region 112 is D, and the radial distance from the intersection of the first inclined surface segment 1132 and the second inclined surface segment 1133 to the central axis of the duct hole 111 is d5. The relationship satisfied by d1, d5, D, H1, and tanB is: d5 ≤ D / 2 + H1×tanB ≤ d1 + d5.

[0061] It can be understood that by establishing the size parameter relationship among d1, d5, D, H1, and the included angle B, the position of the intersection of the transition region 114 and the first inclined surface segment 1132 can be restricted between the intersection of the first inclined surface segment 1132 and the second inclined surface segment 1133 and the position on the side of the first corrugated segment 1131 far from the control center. Such an arrangement can maximize the retention of the corrugated shape of the first corrugated segment 1131, that is, reduce the loss of the corrugated area. Secondly, the corrugated height in front of the heat exchange tube 2 (that is, the minimum height of the intersection of the transition region 114 and the first inclined surface segment 1132) is reasonably controlled, and the flow resistance when the oncoming flow passes through the first inclined surface segment 1132 is reduced, thereby improving the comprehensive heat exchange efficiency of the fin 1.

[0062] Furthermore, as shown in Figure 2 , Figure 4 and Figure 5 , the fin unit 11 further includes a drainage section 115, and the drainage section 115 is arranged between the first corrugated segment 1131 and the second corrugated segment 1134, and the drainage section 115 is coplanar with the flat region 112.

[0063] It can be understood that the drainage section 115 is straight and extends along the direction perpendicular to the oncoming flow. The drainage section 115 is connected between the second inclined surface segment 1133 of the first corrugated segment 1131 and the third inclined surface segment 1135 of the second corrugated segment 1134. In this way, the water droplets formed on the outer wall of the heat exchange tube 2 can be converged to the drainage section 115 (that is, the low-lying area of the fin unit 11) and then flow out along the drainage section 115, thereby preventing the condensed water from being blocked in the flat region 112 and further improving the drainage effect of the fin 1.

[0064] Optionally, as shown in Figure 2 , Figure 4 and Figure 5 , the heat exchanger 100 further includes a straight section 116, and the straight section 116 is connected to both ends of the fin unit 11 in the width direction.

[0065] Among them, flat sections 116 are connected to both ends of the fin unit 11 in the width direction. In this way, the flat sections 116 can pre-guid the flow direction of the air flow, so that the air flow can flow more smoothly to the corrugated area 113, thereby improving the air intake smoothness of the heat exchange air flow. Among them, the flat sections 116 can also enhance the structural strength of the fin unit 11 to a certain extent.

[0066] Alternatively, if the height of the corrugated sheet protruding towards one side in the thickness direction of the fin unit 11 is too large, it will increase the overall volume of the fin unit 11, and if it is too low, it will reduce the heat exchange effect. Therefore, the height H of the corrugated sheet protruding towards one side in the thickness direction of the fin unit 11 is designed to be greater than or equal to 0.3 mm and less than or equal to 0.7 mm, which not only ensures the heat exchange effect but also avoids excessive overall volume and reduces production costs, thus taking into account both practicality and economy. For example, h3 can be 0.3 mm, 0.4 mm, 0.5 mm, and 7 mm, and is not limited thereto.

[0067] According to some alternative embodiments of the present invention, in combination with Figure 2 、 Figure 4 and Figure 5 As shown, the flat area 112 is configured in a circular ring shape, and the outer diameter of the flat area 112 is D, and D satisfies the relationship: D≥9 mm. For example, D can be 9 mm, 10 mm, 12 mm, 15 mm, etc., and is not limited thereto.

[0068] Among them, the circular-ring-shaped flat area 112 fits better with the contour of the circular tube and can evenly transfer the heat from the circular tube to the transition area 114 and the corrugated area 113 along its radial direction, thereby effectively improving the heat exchange uniformity; moreover, the outer diameter of the flat area 112 is greater than 9 mm, so that the problem of too short service life of the die due to too small size of the flat area 112 can be avoided, thereby reducing the manufacturing cost and improving the economy.

[0069] The air conditioner according to the embodiment of the second aspect of the present invention includes the heat exchanger 100 of the above embodiment. In this way, the air conditioner with the heat exchanger 100 can reduce the loss of the heat exchange area on the corrugated area 113 by reasonably controlling the corrugation height in front of the heat exchange tube 2, and can also reduce the flow resistance of the oncoming flow, thereby improving the comprehensive heat exchange efficiency.

[0070] Moreover, compared with the conventional fin type of the heat exchanger (such as ΛΛ-type corrugated sheet), when achieving the same heat exchange capacity, the fin 1 in this case can increase the heat exchange area and enhance the oncoming flow turbulence, thereby improving the heat transfer coefficient and heat transfer amount outside the tube. Therefore, when using the fin 1 structure form provided in this case, when achieving the same heat exchange capacity, the number of fins 1 can be reduced, and the cost of the heat exchanger 100 can be reduced.

[0071] For example, in combination with Figure 8As shown, when d5 = 4.32 mm, H = 0.9 mm, and H1 = 0.56 mm, compared with the conventional ΛΛ corrugated fins, the heat transfer area of fin 1 is increased by 1.73%. Through numerical simulation, it is further obtained that the heat transfer coefficient outside the tube is increased by 5.16%, the heat transfer amount is increased by 3.82%, and the comprehensive heat transfer factor j / f(1 / 3) is increased by 1.38%. It can be seen that fin 1 in this case has better heat transfer performance and a lower surface temperature. In addition, combined with Figure 9 As shown, fin 1 designed according to the embodiment in this case shows good heat transfer effects at different wave heights compared with the conventional fins.

[0072] In the description of the present invention, it should be understood that the orientation or positional relationships indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc. are based on the orientation or positional relationships shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present invention.

[0073] In the description of the present application, it should be noted that unless otherwise clearly specified and defined, the terms "installed", "connected", and "connected" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific circumstances.

[0074] In the description of this specification, the description with reference to terms such as "one embodiment", "some embodiments", "schematic embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example.

[0075] Although the embodiments of the present invention have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and purposes of the present invention, and the scope of the present invention is defined by the claims and their equivalents.

[0076] In the description of this specification, the description with reference to terms such as "one embodiment", "some embodiments", "schematic embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example.

[0077] Although the embodiments of the present invention have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and spirit of the present invention, and the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A heat exchanger, comprising: A fin, wherein the fin comprises a plurality of fin unit rows, the plurality of fin unit rows are distributed in the width direction of the fin, each of the fin unit rows comprises a plurality of fin units distributed along the length direction of the fin, each of the fin units is provided with a tube hole, and the tube holes in two adjacent fin unit rows are staggered; A heat exchange tube, wherein the heat exchange tube is inserted into the tube hole and a refrigerant flows through the heat exchange tube; It is characterized in that The fin unit comprises: A flat area, wherein the flat area is arranged along the circumference of the tube hole; a corrugated area, the corrugated area being arranged around the flat area, the corrugated area protruding toward one side in the thickness direction of the fin unit, the corrugated area comprising a first corrugated section, the first corrugated section comprising a first inclined surface section and a second inclined surface section connected in sequence along the incoming flow direction, the first inclined surface section being arranged obliquely relative to the second inclined surface section; A transition zone, the transition zone is obliquely connected between the flat zone and the corrugated zone, and the transition zone intersects with the first inclined surface segment and the second inclined surface segment respectively; The maximum height of the intersection of the first slope segment and the second slope segment is H, the minimum height of the intersection of the transition zone and the first slope segment is H1, and H and H1 satisfy the relationship: 1 / 3×H≤H1≤2 / 3×H.

2. The heat exchanger according to claim 1, characterized in that: The corrugated area comprises: The second corrugated section is located downstream of the first corrugated section along the incoming flow direction, the second corrugated section comprises a third inclined surface section and a fourth inclined surface section connected in sequence along the incoming flow direction, the third inclined surface section is inclined relative to the fourth inclined surface section, and the transition zone intersects the third inclined surface section and the fourth inclined surface section respectively; The minimum height of the intersection of the transition zone and the fourth slope segment is H2, and H and H2 satisfy the relationship: 1 / 3×H≤H2≤2 / 3×H; or, The H1 and the H2 satisfy the relationship: H1=H2.

3. The heat exchanger according to claim 2, characterized in that: Along the incoming flow direction, a plane passing through the central axis of the tube hole and perpendicular to the incoming flow direction is a dividing interface, and the first corrugated section and the second corrugated section are symmetrical about the dividing interface.

4. The heat exchanger according to claim 2, characterized in that: The plane where the flat area is located is a first reference plane, the width of the projection of the first inclined surface segment on the first reference plane is d1, the width of the projection of the second inclined surface segment on the first reference plane is d2, and d1 and d2 satisfy the relationship: d1≤d2; and / or, The width of the projection of the third slope segment on the first reference plane is d3, the width of the projection of the fourth slope segment on the first reference plane is d4, and d3 and d4 satisfy the relationship: d3≥d4.

5. The heat exchanger according to claim 4, characterized in that The plane parallel to the incoming flow direction and passing through the central axis of the tube hole is the second reference plane, the transition zone forms an angle A on the second reference plane, and the transition zone forms an angle B with the first reference plane, and the A and B satisfy the relationship: B=(180°-A) / 2.

6. The heat exchanger according to claim 5, characterized in that The B satisfies the relationship: 30°≤B≤45°.

7. The heat exchanger according to claim 4, characterized in that The flat area is configured in a circular ring shape, the outer diameter of the flat area is D, the radial distance between the intersection of the first slope segment and the second slope segment and the central axis of the tube hole is d5, and d1, d5, D, H1 and tanB satisfy the relationship: d5≤D / 2+H1×tanB≤d1+d5.

8. The heat exchanger according to claim 2, characterized in that: Also includes: A drainage section, wherein the drainage section is disposed between the first corrugated section and the second corrugated section, and the drainage section is coplanar with the flat area; and / or, A straight section is connected to two ends of the fin unit in a width direction.

9. The heat exchanger according to claim 1, characterized in that: The flat area is configured in a circular ring shape, and the outer diameter of the flat area is D, and D satisfies the relationship: D≥9mm.

10. An air conditioner, characterized in that: include: The heat exchanger according to any one of claims 1 to 9.

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