Heat exchanger and air conditioner

Abstract

The utility model 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; the maximum height of the intersection of the first slope section and the second slope section is H, the minimum height of the intersection of the transition area and the first slope section is H1, and H and H1 meet the relational expression that 1 / 3 * H < = H1 < = 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] This utility model relates to the field of air conditioning technology, and in particular to a heat exchanger and an air conditioner. Background Technology

[0002] As a core component of air conditioning systems, the heat exchanger's heat exchange capacity directly affects the cooling and heating performance of the air conditioner. Simultaneously, the heat exchanger's capacity directly impacts the energy efficiency ratio of the air conditioning system. Improving the heat exchanger's efficiency can also reduce the energy consumption of the air conditioning system. Currently, the main types of fins for outdoor heat exchangers used in air conditioners are corrugated fins and slotted fins. Slotted fins, due to their stronger ability to turbulent airflow, have a higher external convective heat transfer coefficient compared to corrugated fins. However, under heating conditions, slotted fins are prone to water bridging, resulting in poor drainage performance and easy frost formation, thus affecting heating capacity. Therefore, for both cooling and heating units, manufacturers primarily use corrugated fins. Corrugated fins generally involve adding transverse corrugations to the fin surface, with the number and angle of the corrugations being key design parameters.

[0003] In related technologies, the presence of the bottom ring and bottom angle of the perforation in the corrugated sheet results in an incomplete corrugated shape, which not only loses part of the corrugated area but also weakens the heat exchange capacity of the corrugated sheet for the incoming airflow. Utility Model Content

[0004] This invention aims to solve at least one of the technical problems existing in the prior art. Therefore, one objective of this invention is to provide a heat exchanger that can reasonably control the corrugation height before the heat exchange tubes, thereby reducing heat exchange area loss on the first corrugated section and lowering the flow resistance of the incoming flow, thus improving the overall heat exchange efficiency.

[0005] This utility model further proposes an air conditioner.

[0006] A heat exchanger according to a first aspect of the present invention includes: fins, each fin comprising a plurality of fin unit rows distributed along the width direction of the fins, each fin unit row comprising a plurality of fin units distributed along the length direction of the fins, each fin unit having a tube hole, the tube holes in adjacent fin unit rows being staggered; a heat exchange tube passing through the tube hole, the heat exchange tube containing a refrigerant; each fin unit comprising: a flat region arranged circumferentially along the tube hole; and a corrugated region surrounding the flat region and facing the fin unit. The material protrudes from one side in the thickness direction. The corrugated area includes a first corrugated segment, which includes a first inclined segment and a second inclined segment connected sequentially along the flow direction. The first inclined segment is inclined relative to the second inclined segment. A transition area is obliquely connected between the flat area and the corrugated area. The transition area intersects with the first inclined segment and the second inclined segment respectively. The maximum height at the intersection of the first inclined segment and the second inclined segment is H, and the minimum height at the intersection of the transition area and the first inclined segment is H1. H and H1 satisfy the relationship: 1 / 3×H≤H1≤2 / 3×H.

[0007] Therefore, by setting up this heat exchanger, the corrugation height in front of the heat exchange tube can be reasonably controlled, which reduces the loss of heat exchange area on the first corrugated section and reduces the flow resistance of the incoming flow, thereby improving the overall heat exchange efficiency.

[0008] In some examples of this utility model, the corrugated area includes: a second corrugated segment, along the incoming flow direction, the second corrugated segment being located downstream of the first corrugated segment, the second corrugated segment including a third inclined segment and a fourth inclined segment connected sequentially along the incoming flow direction, the third inclined segment being inclined relative to the fourth inclined segment, and the transition zone intersecting with the third inclined segment and the fourth inclined segment respectively; wherein, the minimum height at the intersection of the transition zone and the fourth inclined segment 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 this utility model, along the flow direction, the plane perpendicular to the flow direction and passing through the central axis of the pipe hole is the interface, and the first corrugated segment and the second corrugated segment are symmetrical about the interface.

[0010] In some examples of this utility model, the plane containing the flat area is a first reference plane, the width of the projection of the first inclined segment onto the first reference plane is d1, the width of the projection of the second inclined segment onto 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 inclined segment onto the first reference plane is d3, and the width of the projection of the fourth inclined segment onto the first reference plane is d4, and d3 and d4 satisfy the relationship: d3≥d4.

[0011] In some examples of this utility model, the plane parallel to the incoming flow direction and passing through the central axis of the pipe 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. The relationship between A and B is: B = (180° - A) / 2.

[0012] In some examples of this utility model, B satisfies the relationship 30°≤B≤45°.

[0013] In some examples of this utility model, the flat region is constructed in an annular shape, the outer diameter of the flat region is D, and the radial distance from the intersection of the first inclined segment and the second inclined segment to the central axis of the pipe hole is d5. The relationships d1, d5, D, H1, and tanB satisfy: d5≤D / 2+H1×tanB≤d1+d5. d5≤D / 2 and (D / 2+H1×tanB)≤d5+d1.

[0014] In some examples of this utility model, the fin unit further includes: a drainage section disposed between the first corrugated section and the second corrugated section, the drainage section being coplanar with the flat area; and / or a straight section connected to both ends of the fin unit in the width direction.

[0015] In some examples of this utility model, the flat region is constructed in a circular shape, and the outer diameter of the flat region is D, which satisfies the relationship: D≥9mm.

[0016] An air conditioner according to a second aspect of the present invention includes: the heat exchanger described above.

[0017] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0018] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0019] Figure 1 This is a schematic diagram of the structure of a heat exchanger according to an embodiment of the present utility model;

[0020] Figure 2 This is a schematic diagram of the fin structure according to an embodiment of the present utility model;

[0021] Figure 3 This is a front view of the fin according to an embodiment of the present utility model;

[0022] Figure 4 yes Figure 3 A cross-sectional view along the AA direction;

[0023] Figure 5 This is a front view of a finned unit according to an embodiment of the present utility model;

[0024] Figure 6 This is a schematic diagram of the fin mechanism from another angle according to an embodiment of the present invention;

[0025] Figure 7 yes Figure 6 Enlarged view of region B in the middle;

[0026] Figure 8 This is a comparative schematic diagram of the surface temperature field of the fins according to an embodiment of the present invention;

[0027] Figure 9 This is a schematic diagram comparing heat transfer and j / f (1 / 3) under different wave heights according to an embodiment of the present invention.

[0028] Figure label:

[0029] 100. Heat exchanger;

[0030] 1. Fin; 11. Fin unit; 111. Pipe 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;

[0031] 2. Heat exchange tubes. Detailed Implementation

[0032] The embodiments of this utility model are described in detail below, and the embodiments described with reference to the accompanying drawings are exemplary.

[0033] Reference below Figures 1-9According 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, thereby reducing the loss of heat exchange area on the first corrugated section 1131 and reducing the flow resistance of the incoming flow.

[0034] Combination Figures 1-9 As shown, the heat exchanger 100 according to the first aspect of this utility model includes fins 1 and heat exchange tubes 2. The heat exchange tubes 2 serve as the medium for heat exchange between the refrigerant and the outside air. The refrigerant (a low-temperature, low-pressure liquid in the evaporator and a high-temperature, high-pressure gas in the condenser) can circulate inside the tubes. The fins 1 are typically tightly attached to the outer surface of the heat exchange tubes 2, thus effectively increasing the heat exchange contact area between the air and the heat exchange tubes 2, thereby accelerating the heat transfer rate and improving the heat exchange efficiency.

[0035] Combination Figure 1 and Figure 2 As shown, the heat exchanger 100 includes several heat exchange tubes 2 and several fins 1. The fins 1 are arranged side by side in parallel, with a certain distance between adjacent fins 1. Several heat exchange tubes 2 extend through each fin 1. Each heat exchange tube 2 is connected to an adjacent heat exchange tube 2 through a bend, thereby forming a fluid channel for the heat exchange tube 2. Fluid (e.g., coolant) can flow through the fluid channel of the heat exchange tube 2, and the fluid within the fluid channel of the heat exchange tube 2 can exchange heat with the airflow flowing in the fluid channel of the fins 1 and the heat exchange tube 2.

[0036] 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 properties. 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 properties. The length and width of the fins 1 can be adjusted according to the dimensions of the finned tube heat exchanger 100.

[0037] Specifically, in combination Figure 2 and Figure 3 As shown, the fin 1 includes multiple fin unit rows 12, which are distributed in the width direction of the fin 1, for example, as... Figure 3 As shown, fin 1 may include two fin unit rows 12, which are sequentially connected in the width direction of fin 1. However, this invention is not limited to this; fin 1 may also include three or more fin unit rows 12. When fin 1 includes multiple fin unit rows 12, the heat exchange tube 2 also forms multiple rows accordingly. The width direction of fin 1 is... Figure 4 The direction of the incoming flow is shown.

[0038] Among them, Figure 2and Figure 3 As shown, each finned unit row 12 includes multiple finned units 11 distributed along the length of the fin 1. Each finned unit 11 is provided with a tube hole 111, and a heat exchange tube 2 passes through the tube hole 111, through which a refrigerant flows. In other words, each finned unit 11 can be connected to the heat exchange tube 2 through the tube hole 111, thereby ultimately achieving the heat exchange effect between the fin 1 and the heat exchange tube 2, and thus improving the heat exchange efficiency.

[0039] Furthermore, such as Figure 2 and Figure 3 As shown, the tube holes 111 in two adjacent fin unit rows 12 are staggered. That is, each fin unit row 12 is mainly composed of multiple fin units 11 connected sequentially 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 the adjacent fin unit row 12 are staggered. This allows the heat exchange tubes 2 passing through the corresponding tube holes 111 to also be staggered accordingly, which can avoid the heat exchange tubes 2 in different rows from blocking each other in the incoming flow direction, and can further improve the heat exchange efficiency of the heat exchanger 100.

[0040] Specifically, in combination Figure 2 , Figure 5 and Figure 7 As shown, the fin unit 11 includes a flat region 112, which is arranged circumferentially around the tube hole 111. The flat region 112 surrounds the outer periphery of the tube hole 111 along its circumference. This flat arrangement increases the contact area between the fin 1 and the tube hole 111, thus facilitating better heat conduction; it also reduces the flow resistance of the fluid in the flat region 112 (i.e., reduces turbulence between the fins 1), thereby improving fluid flowability; it provides a smoother flow channel, reducing fluid friction loss and increasing flow velocity; and it simplifies the manufacturing process, reducing complex processing steps and improving production efficiency.

[0041] Furthermore, combined Figure 2 and Figure 5 As shown, the fin unit 11 also includes a corrugated region 113, which is arranged around the flat region 112. The corrugated region 113 protrudes towards one side of the thickness direction of the fin unit 11, and the corrugated region 113 changes continuously in the thickness direction (that is, the corrugated region 113 forms an undulating shape in the thickness direction).

[0042] The corrugated area 113 includes a first corrugated section 1131, which includes a first inclined section 1132 and a second inclined section 1133 connected sequentially along the incoming flow direction. The first inclined section 1132 is inclined relative to the second inclined section 1133.

[0043] It is understandable that the first inclined section 1132 and the second inclined section 1133 connected sequentially along the direction of the incoming flow are constructed together in an inverted V-shaped convex shape. This allows the mutually inclined first inclined section 1132 and the second inclined section 1133 to define the windward slope and the leeward slope, thereby increasing their heat exchange contact area with the airflow and increasing the disturbance effect on the airflow, thereby improving the heat exchange efficiency between the airflow and the fin 1.

[0044] Specifically, in combination Figure 2 , Figure 4 , Figure 5 and Figure 7 As shown, the fin unit 11 also includes a transition region 114, which is obliquely connected between the flat region 112 and the corrugated region 113. The transition region 114 intersects with the first inclined section 1132 and the second inclined section 1133, respectively.

[0045] The transition zone 114 can change the extension direction of the flat zone 112 and the corrugated zone 113, thereby connecting the three into a tight whole; the transition zone 114 can also smoothly transition the area from the flat zone 112 to the corrugated zone 113, thereby reducing the flow resistance of the fluid between different areas, reducing the turbulence of the fluid between different areas, and thus improving the smoothness of fluid flow.

[0046] In particular, combined Figure 4 As shown, the maximum height at the intersection of the first inclined section 1132 and the second inclined section 1133 is H, and the minimum height at the intersection of the transition zone 114 and the first inclined section 1132 is H1. H and H1 can satisfy the relationship: 1 / 3 × H ≤ H1. For example, H1 can be 1 / 3 × H, 0.4 H, or 0.5 H.

[0047] In other words, the maximum height of the intersection of the first inclined section 1132 and the second inclined section 1133 (such as the crest) is H, and the minimum height of the intersection of the transition zone 114 and the first inclined section 1132 (that is, the windward slope) is H1. Since the smaller the minimum height of the intersection of the transition zone 114 and the first inclined section 1132, the larger the corrugated loss area, when 1 / 3×H>H1, the portion of the first inclined section 1132 adjacent to the transition zone 114 is smaller, the loss area of ​​the first inclined section 1132 is larger, and the fin unit 11 itself has a poor heat dissipation effect on the heat exchange tube 2 using the corrugated area 113, which affects the heat exchange effect of the heat exchanger 100.

[0048] 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 section 1132, the greater the fluid resistance of the incoming flow. When H1 > 2 / 3 × H, the portion of the first inclined section 1132 adjacent to the transition zone 114 is larger, and the loss area of ​​the first inclined section 1132 is smaller. However, because the height of the portion of the first inclined section 1132 adjacent to the transition zone 114 is larger, it will hinder the fluid flow between two adjacent fins 1, which will have a significant impact on the smoothness of fluid flow and will also affect the heat exchange effect of the heat exchanger 100.

[0049] 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 incoming flow; it can also reduce the flow resistance of the first inclined section 1132 for the incoming flow (that is, reduce the pressure drop when the incoming flow passes through the first corrugated section 1131), thereby improving the smoothness of fluid flow at the first corrugated section 1131, and thus improving the overall heat exchange efficiency of the heat exchanger 100.

[0050] Therefore, by setting up the heat exchanger 100, the corrugation height in front of the heat exchange tube 2 can be reasonably controlled, which reduces the loss of heat exchange area on the first corrugated section 1131 on the one hand, and reduces the flow resistance of the incoming flow on the other hand, thereby improving the overall heat exchange efficiency.

[0051] According to some optional embodiments of the present invention, combined with Figure 2 , Figure 4 and Figure 5 As shown, the corrugated region 113 includes a second corrugated section 1134. Along the 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 profile of the corrugated region 113, thereby increasing the heat exchange contact area of ​​the corrugated region 113 and thus improving the heat exchange efficiency of the fin unit 11.

[0052] Furthermore, the above arrangement allows the airflow to pass sequentially through multiple corrugated sections formed on the corrugated sheet, thereby creating periodic disturbances to the heat exchange airflow and improving the heat exchange efficiency of fin 1.

[0053] Specifically, in combination Figure 5 and Figure 7 As shown, the second corrugated section 1134 includes a third inclined section 1135 and a fourth inclined section 1136 connected sequentially along the incoming flow direction. The third inclined section 1135 is inclined relative to the fourth inclined section 1136, and the transition zone 114 intersects with the third inclined section 1135 and the fourth inclined section 1136 respectively.

[0054] It is understandable that the third inclined section 1135 and the fourth inclined section 1136, which are connected sequentially along the direction of the incoming flow, are constructed together in an inverted V-shaped convex shape. This allows the mutually inclined third inclined section 1135 and the fourth inclined section 1136 to define the windward slope and the leeward slope, thereby increasing their heat exchange contact area with the airflow and increasing the disturbance effect on the airflow, thereby improving the heat exchange efficiency between the airflow and the fin 1.

[0055] Among them, combined 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 segment 1136 is H2, and H and H2 satisfy the relationship: 1 / 3×H≤H2. For example, H2 can be 1 / 3×H, 0.4H, or 0.5H.

[0056] In other words, the maximum height at the intersection of the third inclined section 1135 and the fourth inclined section 1136 (such as the crest) is H2, and the minimum height at the intersection of the transition zone 114 and the first inclined 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 section 1135, the larger the corrugated loss area, when 1 / 3×H>H2, the portion of the third inclined section 1135 adjacent to the transition zone 114 is smaller, the loss area of ​​the third inclined section 1135 is larger, and the fin unit 11 itself has a poor heat dissipation effect on the heat exchange tube 2 using the corrugated area 113, which affects the heat exchange effect of the heat exchanger 100.

[0057] H and H2 can also satisfy the relationship: H2 ≤ 2 / 3 × H. For example, H2 can be 2 / 3 × H or 0.6H. The greater the minimum height at the intersection of the transition zone 114 and the third inclined section 1135, the greater the fluid resistance of the incoming flow. When H2 > 2 / 3 × H, the portion of the third inclined section 1135 adjacent to the transition zone 114 is larger, and the loss area of ​​the third inclined section 1135 is smaller. However, because the portion of the third inclined section 1135 adjacent to the transition zone 114 is relatively large, it will hinder the fluid flow between two adjacent fins 1, which will have a significant impact on the smoothness of fluid flow and will also affect the heat exchange effect of the heat exchanger 100.

[0058] H and H2 can also satisfy the relationship: 1 / 3×H≤H2≤2 / 3×H. When 1 / 3×H≤H2≤2 / 3×H, the corrugation loss area of ​​the second corrugated section 1134 can be reduced, thereby increasing the heat transfer area of ​​the second corrugated section 1134 for the incoming flow; it can also reduce the flow resistance of the third inclined section 1135 for the incoming flow, thereby improving the smoothness of fluid flow at the second corrugated section 1134, and thus improving the overall heat transfer efficiency of the heat exchanger 100.

[0059] Optionally, H1 and H2 satisfy the relationship: H1=H2. It is understood that the minimum height at the intersection of the transition zone 114 and the first inclined section 1132 is equal to the minimum height at the intersection of the transition zone 114 and the fourth inclined section 1136, which can improve the manufacturing consistency of the first corrugated section 1131 and the second corrugated section 1134.

[0060] Specifically, in combination Figure 2 , Figure 4 , Figure 5 and Figure 7 As shown, along the flow direction, the plane perpendicular to the flow direction and passing through the central axis of the pipe hole 111 is the interface, and the first corrugated segment 1131 and the second corrugated segment 1134 are symmetrical about the interface.

[0061] In other words, the first corrugated section 1131 and the second corrugated section 1134 are symmetrically arranged about the interface. This makes the first inclined section 1132 and the second inclined section 1133 on the first corrugated section 1131 symmetrically arranged about the interface with the third inclined section 1135 and the fourth inclined section 1136 on the second corrugated section 1134, respectively. This arrangement facilitates manufacturing and helps to balance the heat distribution of the airflow, avoiding structural warping and angular deviation caused by thermal asymmetry, thereby improving manufacturability and heat exchange efficiency.

[0062] Furthermore, combined 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 segment 1132 on the first reference plane is d1, and the width of the projection of the second inclined segment 1133 on the first reference plane is d2. d1 and d2 satisfy the relationship: d1≤d2.

[0063] It is understandable that, when projected onto the first reference plane, the projected width of the first inclined section 1132 is not less than the projected width of the second inclined section 1133. When the projected width of the first inclined section 1132 is less than the projected width of the second inclined section 1133, it helps the intersection of the first inclined section 1132 and the second inclined section 1133 to shift away from the center of the tube hole 111. This can reduce the loss of corrugated area on the first corrugated section 1131, thereby effectively preserving the corrugated shape on the first corrugated section 1131 and improving the heat exchange efficiency of the fin 1.

[0064] Furthermore, when the projected width of the first inclined section 1132 is equal to the projected width of the second inclined section 1133, that is, the two are symmetrical to each other, manufacturing consistency can be improved, manufacturing process can be simplified, and production efficiency can be improved.

[0065] Optionally, combined Figure 4As shown, the width of the projection of the third inclined segment 1135 onto the first reference plane is d3, and the width of the projection of the fourth inclined segment 1136 onto the first reference plane is d4. d3 and d4 satisfy the relationship: d3≥d4.

[0066] In other words, when projected onto the first reference plane, the projected width of the fourth inclined section 1136 is not less than the projected width of the third inclined section 1135. When the projected width of the fourth inclined section 1136 is less than the projected width of the third inclined section 1135, it helps the intersection of the third inclined section 1135 and the fourth inclined section 1136 to shift away from the center of the tube hole 111. This can reduce the loss of corrugated area on the second corrugated section 1134, thereby effectively preserving the corrugated shape on the second corrugated section 1134 and improving the heat exchange efficiency of the fin 1.

[0067] Furthermore, when the projected width of the third inclined section 1135 is equal to the projected width of the fourth inclined section 1136, that is, when the two are symmetrical, manufacturing consistency can be improved, manufacturing process can be simplified, and thus production efficiency can be improved.

[0068] Specifically, in combination Figure 4 As shown, the plane parallel to the incoming flow direction and passing through the central axis of the pipe hole 111 is the second reference plane. The transition zone 114 forms an angle A on 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.

[0069] It is understandable that the transition zone 114 extends outward at an angle away from the tube hole 111 along the radial direction of the tube hole 111. The included angle A formed by the transition zone 114 on the second reference plane and the included angle B formed by the transition zone 114 and the first reference plane are parametrically related. This allows the inclination angle of the transition zone 114 at the first corrugated section 1131 and the second corrugated section 1134 to be the same, thereby ensuring manufacturing consistency and improving production efficiency. Furthermore, by reasonably controlling the included angle A (under the premise that the projected widths of the first corrugated section 1131 and the second corrugated section 1134 remain unchanged), the minimum height H1 at the intersection of the transition zone 114 and the first inclined section 1132 and the minimum height H2 at the intersection of the transition zone 114 and the second inclined section 1133 can be controlled. This simultaneously reduces the loss of heat exchange area on the corrugated plate and reduces the flow resistance of the incoming flow, thereby improving the overall heat exchange efficiency of the heat exchanger 100.

[0070] Furthermore, combined Figure 4 As shown, B satisfies the relationship 30°≤B≤45°. For example, B can be 30°, 35°, 40°, and 45°, etc., and is not limited to this.

[0071] The angle B formed between the transition zone 114 and the first reference plane is relatively small, which helps to guide and collect water vapor near the fin 1 onto the transition zone 114, thereby improving the drainage effect.

[0072] Specifically, in combination Figure 4 and Figure 5 As shown, the flat region 112 is constructed in a ring shape, and the outer diameter of the flat region 112 is D. The radial distance between the central axis of the pipe hole 111 at the intersection of the first inclined section 1132 and the second inclined section 1133 is d5. d1, d5, D, H1 and tanB satisfy the relationship: d5≤D / 2+H1×tanB≤d1+d5.

[0073] It is understandable that by establishing a relationship between the magnitude parameters d1, d5, D, H1 and the included angle B, the position of the intersection of the transition zone 114 and the first inclined section 1132 can be limited to the intersection of the first inclined section 1132 and the second inclined section 1133 and the position of the first corrugated section 1131 away from the control center. This arrangement can preserve the corrugated shape of the first corrugated section 1131 to the greatest extent, thereby reducing the loss of corrugated area. Secondly, the corrugated height before the heat exchange tube 2 (that is, the minimum height at the intersection of the transition zone 114 and the first inclined section 1132) can be reasonably controlled to reduce the flow resistance when the incoming flow passes through the first inclined section 1132, thereby improving the overall heat exchange efficiency of the fins 1.

[0074] Furthermore, combined Figure 2 , Figure 4 and Figure 5 As shown, the fin unit 11 also includes a drainage section 115, which is disposed between the first corrugated section 1131 and the second corrugated section 1134, and the drainage section 115 is coplanar with the flat area 112.

[0075] It is understandable that the drainage section 115 is straight and extends perpendicular to the incoming flow direction. The drainage section 115 is connected between the second inclined section 1133 of the first corrugated section 1131 and the third inclined section 1135 of the second corrugated section 1134. In this way, the water droplets formed on the outer wall of the heat exchange tube 2 can be collected in 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 avoiding the condensate from clogging in the flat area 112 and thus improving the drainage effect of the fin 1.

[0076] Optionally, combined Figure 2 , Figure 4 and Figure 5 As shown, the heat exchanger 100 also includes a straight section 116, which is connected to both ends of the finned unit 11 in the width direction.

[0077] The fin unit 11 has straight sections 116 connected to both ends in the width direction. This allows the straight sections 116 to guide the airflow in advance, enabling the airflow to flow more smoothly to the corrugated area 113, thereby improving the smoothness of the heat exchange airflow. The straight sections 116 can also enhance the structural strength of the fin unit 11 to a certain extent.

[0078] Alternatively, if the protrusion height of the corrugated fins on the side facing the thickness direction of the fin unit 11 is too large, it will increase the overall volume of the fin unit 11; if it is too low, it will reduce the heat exchange effect. Therefore, the protrusion height H of the corrugated fins on the side facing 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. This ensures the heat exchange effect while avoiding an excessively large overall volume, reducing production costs, and thus balancing practicality and economy. For example, h3 can be 0.3 mm, 0.4 mm, 0.5 mm, and 7 mm, and is not limited to these.

[0079] According to some optional embodiments of the present invention, combined with Figure 2 , Figure 4 and Figure 5 As shown, the flat region 112 is constructed in a circular shape, and the outer diameter of the flat region 112 is D, which satisfies the relationship: D≥9mm. For example, D can be 9mm, 10mm, 12mm, and 15mm, etc., and is not limited to these.

[0080] Among them, the annular flat area 112 better fits 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 own radial direction, thereby effectively improving the heat exchange uniformity; moreover, the outer diameter of the flat area 112 is greater than 9mm, which can avoid the problem of the mold life being too short due to the size of the flat area 112 being too small, thereby reducing manufacturing costs and improving economy.

[0081] The air conditioner according to the second aspect of the present invention includes the heat exchanger 100 of the above embodiment. The air conditioner having the heat exchanger 100 can reduce the loss of 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 incoming flow, thereby improving the overall heat exchange efficiency.

[0082] Moreover, compared to conventional fin types in heat exchangers (such as ΛΛ-type corrugated fins), the fins 1 in this invention can increase the heat exchange area and enhance the turbulence of the incoming flow while achieving the same heat exchange capacity, thereby improving the external heat transfer coefficient and the amount of heat exchanged. Therefore, by using the fin structure 1 provided in this invention, the number of fins 1 can be reduced while achieving the same heat exchange capacity, thus lowering the cost of the heat exchanger 100.

[0083] For example, combining Figure 8As shown, when d5=4.32mm, H=0.9mm, and H1=0.56mm, compared with conventional ΛΛ corrugated fins, the heat transfer area of ​​fin 1 is increased by 1.73%. Further numerical simulation shows that the external heat transfer coefficient is increased by 5.16%, the heat transfer capacity is increased by 3.82%, and the comprehensive heat transfer factor j / f(1 / 3) is increased by 1.38%. Therefore, it can be concluded that fin 1 in this design has better heat transfer performance and a lower surface temperature. Furthermore, combined with… Figure 9 As shown, the fin 1 designed according to the embodiment of this case exhibits good heat exchange performance at different wave heights compared to conventional fins.

[0084] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0085] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0086] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example.

[0087] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

[0088] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example.

[0089] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A heat exchanger, comprising: The fin includes multiple fin unit rows, which are distributed in the width direction of the fin. Each fin unit row includes multiple fin units distributed along the length direction of the fin. Each fin unit 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 refrigerant flows through the heat exchange tube; Its features are, The fin unit includes: A flat area is provided along the circumference of the pipe hole; A corrugated area is provided around the flat area. The corrugated area protrudes towards one side of the thickness direction of the fin unit. The corrugated area includes a first corrugated segment. The first corrugated segment includes a first inclined segment and a second inclined segment connected sequentially along the incoming flow direction. The first inclined segment is inclined relative to the second inclined segment. A transition zone, which is obliquely connected between the flat zone and the corrugated zone, 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, and the minimum height at the intersection of the transition zone and the first inclined section is H1, wherein H and H1 satisfy the following relationship: 1 / 3×H≤H1≤2 / 3×H.

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

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

4. The heat exchanger according to claim 2, characterized in that, The plane containing the flat region is the first reference plane. The width of the projection of the first inclined segment onto the first reference plane is d1, and the width of the projection of the second inclined segment onto the first reference plane is d2. The d1 and d2 satisfy the following relationship: d1≤d2; and / or, The width of the projection of the third inclined segment onto the first reference plane is d3, and the width of the projection of the fourth inclined segment onto the first reference plane is d4. d3 and d4 satisfy the following relationship: d3≥d4.

5. The heat exchanger according to claim 4, characterized in that, A second reference plane is defined as a plane parallel to the incoming flow direction and passing through the central axis of the pipe orifice. The transition zone forms an angle A on the second reference plane, and an angle B is formed between the transition zone and the first reference plane. The relationships A and B satisfy the following equation: 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 constructed in a ring shape, and 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, d5, D, H1 and tanB satisfy the following relationship: d5≤D / 2+H1×tanB≤d1+d5.

8. The heat exchanger according to claim 2, characterized in that, Also includes: A drainage section is provided 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, which connects the two ends of the fin unit in the width direction.

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

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

Images