Heat exchanger and air conditioner

Abstract

The invention discloses a heat exchanger and an air conditioner. The heat exchanger comprises fins and a heat exchanger, each fin strip comprises a plurality of flat areas and a plurality of fins, wherein the flat areas are arranged in the circumferential direction of the pipe holes. Each bridge piece area comprises a plurality of bridge pieces distributed at intervals in the width direction of the fin strip, and through holes are formed in the positions, corresponding to the bridge pieces, of the bridge piece areas; wherein in each bridge piece sub-region, the plurality of bridge pieces comprise end bridge pieces, and the end bridge pieces extend in the length direction of the fin strip; the middle bridge piece is located between the end bridge pieces, and an included angle larger than 0 degree and smaller than 90 degrees is formed between the length direction of the middle bridge piece and the width direction of the fin strip. Therefore, the turbulent flow effect can be achieved, the turbulence degree of fluid can be increased, the convective heat transfer coefficient can be further increased, the heat exchange amount can be improved, the effect of cutting airflow can be achieved, the airflow is subjected to segmentation steering multiple times in the width direction of the fin strips, and the turbulence intensity of the fluid can be further improved.

Description

Technical Field

[0001] The present invention relates to the technical field of air conditioners, and in particular 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 the 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. By improving the heat exchange effect of the heat exchanger, the operating energy consumption of the air conditioner can also be reduced.

[0003] With the improvement of the national air conditioner energy efficiency standard and the increase in raw material prices, the cost pressure has further increased. The small-diameter heat exchanger is one of the most effective methods to reduce costs. In addition, after the Kigali Amendment comes into effect, the air conditioning system needs to reduce the refrigerant charge or the proportion of HCs refrigerants, and the small-diameter heat exchanger can reduce the refrigerant charge. Whether it is a small-diameter or an aluminum tube heat exchanger, there are certain disadvantages compared with traditional heat exchangers. The former has a relatively small heat exchange area, and the latter has a lower thermal conductivity coefficient of the aluminum tube than that of the copper tube.

[0004] In the prior art, the main forms of the fins of the heat exchanger for air conditioners are corrugated fins and slotted fins (window fins, bridge fins, etc.). Due to the strong ability of the slotted fins to disturb the air flow, the convective heat transfer coefficient outside the tube is higher than that of the corrugated fins. Therefore, for the indoor unit and the outdoor unit of the single-cooling machine, each manufacturer mainly adopts the form of slotted fins. Among them, the bridge fin is one of the main application forms. The heat exchange efficiency of the bridge fins on the fins of the heat exchanger is relatively low, and the distribution of the high-speed air flow is relatively narrow. Its air flow disturbance ability is relatively weak, and there is a problem of poor heat exchange effect. Summary of the Invention

[0005] The present invention aims to solve at least one of the technical problems existing in the prior art. For this purpose, the present invention provides a heat exchanger, which can play a role in disturbing the flow and increasing the turbulence of the fluid, thereby further improving the convective heat transfer coefficient and increasing the heat transfer amount. It can also play a role in cutting the air flow. The air flow passes through multiple divisions and turns along the width direction of the fin strip, which can further increase the turbulence intensity of the fluid and also increase the stiffness of the fins.

[0006] The present invention also provides an air conditioner.

[0007] A heat exchanger according to an embodiment of the first aspect of the present invention, the heat exchanger includes: fins, the fins include a plurality of fin strips, the plurality of fin strips are distributed and connected in the width direction of the fins, each fin strip is provided with a plurality of tube holes spaced along the length direction of the fin strip, and the tube holes in two adjacent fin strips are staggered; heat exchange tubes, the heat exchange tubes are inserted into the tube holes, and a refrigerant flows through the heat exchange tubes; the fin strip includes: a plurality of flat areas, the flat areas are arranged along the circumferential direction of the tube holes; a plurality of bridge areas, the plurality of bridge areas and the plurality of flat areas are staggered along the length direction of the fin strip, each bridge area has a first center line extending along the length direction of the fin strip and a second center line extending along the width direction of the fin strip, the bridge area is separated into a plurality of bridge sub-areas by the intersecting first center line and second center line, each bridge sub-area includes a plurality of bridge pieces spaced along the width direction of the fin strip, the bridge pieces protrude from one side of the fin strip facing the thickness direction of the fin; a through hole is formed in the bridge area at the position corresponding to the bridge piece; wherein, in each bridge sub-area, the plurality of bridge pieces include: end bridge pieces, the end bridge pieces extend along the length direction of the fin strip; middle bridge pieces, the middle bridge pieces are located between the end bridge pieces, and the length direction of the middle bridge pieces has an angle greater than 0° and less than 90° with the width direction of the fin strip.

[0008] Thus, the heat exchanger can play a role in disturbing the flow, and can also increase the turbulence of the fluid, thereby further improving the convective heat transfer coefficient, increasing the heat transfer amount, and can also play a role in cutting the air flow. The air flow passes through multiple divisions and turns along the width direction of the fin strip, which can further increase the turbulence intensity of the fluid, and at the same time can also increase the stiffness of the fins.

[0009] According to some embodiments of the present invention, there are at least two of the middle bridge pieces and include:

[0010] The first bridge piece;

[0011] The second bridge piece, the second bridge piece is located on the side of the first bridge piece close to the first center line, and the angle between the length direction of the first bridge piece and the width direction of the fin strip is different from the angle between the length direction of the second bridge piece and the width direction of the fin strip.

[0012] According to some embodiments of the present invention, the angle formed by the length direction of the first bridge piece and the width direction of the fin strip is α, and α satisfies the relational expression: 45° ≤ α < 90°; and / or the angle formed by the length direction of the second bridge piece and the width direction of the fin strip is β, and β satisfies the relational expression: 68° ≤ β < 90°.

[0013] According to some embodiments of the present invention, the distance from the edge of one end of the second bridge plate close to the tube hole to the center of the tube hole is d, along the length direction of the fin strip, the distance between the centers of two adjacent tube holes is L1, the outer diameter of the heat exchange tube is D1, and the diameter of the flat area is D2. Wherein, the relational expression satisfied by d, L1, D1 and D2 is: D2 + 0.4×(L1 - D2) ≤ d ≤ D2 + 0.6×(L1 - D2).

[0014] According to some embodiments of the present invention, the end bridge plate includes: a third bridge plate located on the side of the first bridge plate away from the first center line; a fourth bridge plate located on the side of the second bridge plate close to the first center line, the first center line passes through the fourth bridge plate, and a plurality of the bridge plate areas share one fourth bridge plate.

[0015] According to some embodiments of the present invention, the included angle formed by the length direction of the first bridge plate and the width direction of the fin strip is α, the included angle formed by the length direction of the second bridge plate and the width direction of the fin strip is β, and the included angle formed by the length direction of the fourth bridge plate and the width direction of the fin strip is δ. The relational expression satisfied by β is: β = (α + δ) / 2.

[0016] According to some embodiments of the present invention, the tube hole has a third center line, the third center line passes through the center of the tube hole and extends along the width direction of the fin strip. The intersection point of the extension line of the edge of the end of the third bridge plate away from the third center line and the outer diameter of the heat exchange tube is A, and the included angle formed by the connection line between A and the center of the tube hole and the width direction of the fin strip is γ; the intersection point of the extension line of the edge of the end of the third bridge plate close to the third center line and the outer diameter of the heat exchange tube is B, and the included angle formed by the connection line between B and the center of the tube hole and the width direction of the fin strip is θ. The relational expression satisfied by γ and θ is: 90° ≤ γ ≤ θ ≤ 180°.

[0017] According to some embodiments of the present invention, along the length direction of the fin strip, the distance between the centers of two adjacent tube holes is L1, the maximum distance from the end of the third bridge plate away from the third center line to the third center line is L2, and the relational expression satisfied by L1 and L2 is: L2 ≥ 0.25L1; and / or the minimum distance from the end of the third bridge plate close to the third center line to the third center line is L3, the width of the bridge plate is W, and the outer diameter of the heat exchange tube is D1. The relational expression satisfied by L3, W and D1 is: W ≤ L3 < 0.5D1.

[0018] According to some embodiments of the present invention, the bridge sub-regions located on both sides of the first center line are symmetrically arranged with respect to the first center line, and the bridge sub-regions located on both sides of the second center line are symmetrically arranged with respect to the second center line.

[0019] An air conditioner according to an embodiment of the second aspect of the present invention includes: the heat exchanger described above.

[0020] The additional aspects and advantages of the present invention will be partially given in the following description, partially become apparent from the following description, or be understood through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The above and / or additional aspects and advantages of the present invention will become apparent and be readily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0022] Figure 1 is a schematic structural diagram of a heat exchanger according to an embodiment of the present invention;

[0023] Figure 2 is a schematic structural diagram of a fin according to an embodiment of the present invention;

[0024] Figure 3 is Figure 2 an enlarged view of region A in;

[0025] Figure 4 is a partial schematic diagram of a fin according to an embodiment of the present invention;

[0026] Figure 5 is a side view of a fin along the air flow direction according to an embodiment of the present invention;

[0027] Figure 6 is a partial schematic diagram of the side of a fin along the air flow direction according to an embodiment of the present invention;

[0028] Figure 7 is a side view of a fin according to an embodiment of the present invention;

[0029] Figure 8 is an axonometric view of a fin according to an embodiment of the present invention;

[0030] Figure 9 is Figure 8 an enlarged view of region B in;

[0031] Figure 10 In (a) is a schematic diagram of the flow field of a conventional fin;

[0032] Figure 10 In (b) is a schematic diagram of the flow field of a fin according to the present invention;

[0033] Figure 11In Figure (c), it is a schematic diagram of the temperature field of a conventional fin;

[0034] Figure 11 In Figure (d), it is a schematic diagram of the temperature field of the fin according to the embodiment of the present invention.

[0035] Reference signs:

[0036] 100, heat exchanger;

[0037] 1, fin; 11, fin strip; 111, tube hole;

[0038] 2, heat exchange tube;

[0039] 3, flat area;

[0040] 4, bridge piece area; 41, first center line; 42, second center line; 43, third center line;

[0041] 5, bridge piece sub - area; 51, bridge piece; 511, through - hole;

[0042] 6, middle bridge piece; 61, first bridge piece; 62, second bridge piece;

[0043] 7, end bridge piece; 71, third bridge piece; 72, fourth bridge piece. Detailed implementation manners

[0044] The embodiments of the present invention will be described in detail below. The embodiments described with reference to the drawings are exemplary. The embodiments of the present invention will be described in detail below.

[0045] Reference will be made below to Figures 1 - 11 Describe the heat exchanger 100 according to the embodiment of the present invention.

[0046] Referring to Figures 1 - 5 As shown, the heat exchanger 100 according to the first - aspect embodiment of the present invention includes: a fin 1 and a heat exchange tube 2. Among them, the heat exchange tube 2 can serve as a medium for heat exchange between the refrigerant and the outside air, and the refrigerant (a low - temperature and low - pressure liquid in the evaporator and a high - temperature and high - pressure gas in the condenser) can flow inside it. The fin 1 is usually closely attached to the outer surface of the heat exchange tube 2. In this way, the heat - transfer contact area between the air and the heat exchange tube 2 can be effectively increased, thereby accelerating the heat - transfer speed and improving the heat - exchange efficiency.

[0047] Moreover, the fin 1 includes a plurality of fin strips 11. The plurality of fin strips 11 are distributed and connected in the width direction of the fin 1. Each fin strip 11 is provided with a plurality of tube holes 111 that are spaced apart along the length direction of the fin strip 11. The tube holes 111 in two adjacent fin strips 11 are staggered. The heat exchange tube 2 passes through the tube holes 111, and the refrigerant flows inside the heat exchange tube 2.

[0048] Among them, 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. Each heat exchange tube 2 among 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 airflow flowing in the fin 1 fluid channel through the heat exchange tubes 2 and the fins 1.

[0049] Furthermore, 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, and 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 heat exchanger 100.

[0050] Each fin strip 11 includes a plurality of tube holes 111 distributed along the length direction of the fin strip 11. The heat exchange tubes 2 are inserted into the tube holes 111, and a refrigerant flows in the heat exchange tubes 2. That is to say, each fin strip 11 can be connected to the heat exchange tubes 2 through the tube holes 111, thereby finally realizing the heat exchange effect between the fins 1 and the heat exchange tubes 2, and further improving the heat exchange efficiency.

[0051] Furthermore, the tube holes 111 in two adjacent fin strips 11 are arranged staggeredly. That is to say, the tube holes 111 in one fin strip 11 and the tube holes 111 in another adjacent fin strip 11 are arranged staggeredly, so that the heat exchange tubes 2 passing through the corresponding tube holes 111 on the fins 1 are all arranged staggeredly accordingly, which can further improve the heat exchange efficiency of the heat exchanger 100.

[0052] In addition, the fin strip 11 includes a plurality of flat areas 3 and a plurality of bridge areas 4. The plurality of flat areas 3 are arranged along the circumferential direction of the tube holes 111. Among them, the flat areas 3 surround the outer periphery of the tube holes 111 along the circumferential direction of the tube holes 111, and the flat areas 3 are flat. Such an arrangement can increase the contact area between the fins 1 and the tube holes 111, thereby contributing to better heat conduction. It can also reduce the flow resistance of the fluid on the flat areas 3 (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 frictional loss of the fluid, and thereby increase the flow rate.

[0053] Furthermore, the plurality of bridge areas 4 and the plurality of flat areas 3 are distributed alternately along the length direction of the fin strip 11, which can reduce the flow resistance of the fluid between different regions, reduce the turbulence of the fluid between different regions, and thereby improve the flow smoothness of the fluid.

[0054] In addition, each bridge section 4 has a first center line 41 extending along the length direction of the fin strip 11 and a second center line 42 extending along the width direction of the fin strip 11. The bridge section 4 is divided into a plurality of bridge sub-sections 5 by the intersecting first center line 41 and second center line 42. Each bridge sub-section 5 includes a plurality of bridge pieces 51 spaced apart along the width direction of the fin strip 11.

[0055] Specifically, by dividing the bridge section 4 into a plurality of bridge sub-sections 5 and arranging a plurality of bridge pieces 51 spaced apart in each bridge sub-section 5, it is possible to ensure the uniform distribution of the air flow in the entire fin area, and it is also possible to reduce the phenomenon of too high or too low local flow velocity, thereby reducing the flow resistance. Moreover, the plurality of bridge pieces 51 spaced apart can generate more disturbances when the air flow enters and leaves the fin 1, and can also break the boundary layer effect, thereby increasing the contact area between the air flow and the fin surface and improving the heat transfer efficiency.

[0056] Furthermore, the bridge piece 51 protrudes from one side of the fin strip 11 toward the thickness direction of the fin 1. The bridge section 4 is formed with a through hole 511 at the position corresponding to the bridge piece 51. Among them, the protruding arrangement of the bridge piece 51 can generate additional disturbances to the fluid flowing through the surface of the fin 1, break the boundary layer effect, and promote turbulence, thereby increasing the contact area between the fluid and the surface of the fin 1 and improving the heat transfer efficiency. Moreover, the plurality of through holes 511 corresponding to the plurality of bridge sections 4 on the fin strip 11 can divide the air flow into multiple air flow channels, and can also increase the heat dissipation speed, thereby improving the heat exchange efficiency of the fin 1.

[0057] In addition, in each bridge sub-section 5, the plurality of bridge pieces 51 include: an end bridge piece 7 and a middle bridge piece 6. The end bridge piece 7 is the bridge piece 51 on the side close to the edge of the fin strip 11. The end bridge piece 7 extends along the length direction of the fin strip 11, that is, the included angle between the length direction of the end bridge piece 7 and the width direction of the fin strip 11 is 90°.

[0058] Among them, the extension of the end bridge piece 7 along the length direction of the fin strip 11 can play a role in disturbing the flow, increase the turbulence degree of the fluid, thereby increasing the convective heat transfer coefficient, increasing the heat transfer amount, and ensuring that the air flow can flow more smoothly, thereby reducing unnecessary energy loss and reducing the flow resistance.

[0059] Furthermore, the middle bridge piece 6 is located between the end bridge pieces 7. For example, two end bridge pieces 7 can be provided in the bridge piece sub-region 5, so that two middle bridge pieces 6 can be provided between the two end bridge pieces 7. The length direction of the middle bridge piece 6 and the width direction of the fin strip 11 have an included angle greater than 0° and less than 90°. In this way, the middle bridge piece 6 is inclined, so that the end bridge piece 7 and the middle bridge piece 6 can be staggered with each other along the width direction of the fin strip 11, which can play a role in cutting the air flow. The air flow passes through the division and turning multiple times along the width direction of the fin strip 11, which can increase the turbulence intensity of the fluid and also improve the heat exchange quantity.

[0060] At the same time, the length direction of the middle bridge piece 6 and the width direction of the fin strip 11 have an included angle greater than 0° and less than 90°, which can provide better bending resistance, can disperse mechanical stress to a certain extent, thereby increasing the stiffness of the fin 1 and also extending the service life of the fin 1.

[0061] Thus, the heat exchanger 100 can play a role in disturbing the flow and increasing the turbulence degree of the fluid, thereby further enhancing the convective heat transfer coefficient and improving the heat exchange quantity. It can also play a role in cutting the air flow. The air flow passes through the division and turning multiple times along the width direction of the fin strip 11, which can further increase the turbulence intensity of the fluid and also increase the stiffness of the fin 1.

[0062] According to some embodiments of the present invention, as Figure 3 and Figure 4 shown, there are at least two middle bridge pieces 6, and the middle bridge piece 6 includes: a first bridge piece 61 and a second bridge piece 62. The second bridge piece 62 is located on the side of the first bridge piece 61 close to the first center line 41, which can effectively guide the fluid to flow to the central region of the fin strip 11, thereby realizing a more uniform fluid distribution. Moreover, the position of the second bridge piece 62 close to the first center line 41 can provide a stronger supporting effect, especially in a high-vibration environment, which can help maintain the overall structural integrity of the fin strip 11, thereby preventing it from deforming or being damaged.

[0063] Furthermore, the included angle between the length direction of the first bridge piece 61 and the width direction of the fin strip 11 is different from the included angle between the length direction of the second bridge piece 62 and the width direction of the fin strip 11. In this way, the first bridge piece 61 and the second bridge piece 62 can play a role in guiding the air flow direction. Since the length directions of the first bridge piece 61 and the second bridge piece 62 and the width direction of the fin strip 11 have different included angles, the air flow can be cut by the first bridge piece 61 and the second bridge piece 62 to form different air flow directions. In this way, the air flowing through the surface of the fin strip 11 can stay for a longer time, thereby playing a role in strengthening heat transfer.

[0064] According to some embodiments of the present invention, as Figure 4As shown, the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 satisfies the relation: 45° ≤ α < 90°.

[0065] Among them, the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 is not less than the first parameter value. If the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 is less than the first parameter value, the contact area between the air flow and the first bridge piece 61 will be reduced, and the heat exchange efficiency at the first bridge piece 61 will be lowered. Therefore, the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 cannot be less than 45°.

[0066] The first parameter value can be 30° - 45°. Preferably, the first parameter value can be 45°. When the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 is 45°, the air flow can just contact the entire first bridge piece 61, so as to ensure the heat exchange effect of the first bridge piece 61.

[0067] Among them, the value range of the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 can be 45° to 60°. Preferably, when the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 is 60°, the air flow can fully contact the first bridge piece 61, and the contact time between the air flow and the first bridge piece 61 can also be extended, thereby improving the heat exchange efficiency of the first bridge piece 61.

[0068] In addition, it is set that the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 is less than the second parameter value. If the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 is greater than the second parameter value, the contact area between the air flow and the first bridge piece 61 will be reduced, thereby reducing the heat exchange effect of the first bridge piece 61. Therefore, the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 cannot be greater than the second parameter value.

[0069] The second parameter value can be 90° to 100°. Preferably, the second parameter value can be set to 90°. When the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 is 90°, the contact area between the air flow and the first bridge piece 61 is just smaller, resulting in a lower heat exchange effect of the first bridge piece 61.

[0070] Among them, the value range of the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 can be from 60° to 90°. For example, the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 can be set to 65°, 75°, and 85°. Preferably, if the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 is 65°, the contact area between the air flow and the first bridge piece 61 can be further increased, and more turbulences can also be increased, so that the air flow is more evenly distributed in the entire fin 1 area, thereby improving the heat exchange efficiency of the entire first bridge piece 61.

[0071] Furthermore, as Figure 4 shown, the included angle formed by the length direction of the second bridge piece 62 and the width direction of the fin strip 11 is β, and β satisfies the relational expression: 68° ≤ β < 90°.

[0072] Among them, the included angle β formed by the length direction of the second bridge piece 62 and the width direction of the fin strip 11 is not less than the third parameter value. If the included angle β formed by the length direction of the second bridge piece 62 and the width direction of the fin strip 11 is less than the third parameter value, the boundary layer effect of the fluid cannot be effectively destroyed, more turbulences cannot be generated, and the air flow direction cannot be changed to a large extent, affecting the heat exchange efficiency of the second bridge piece 62.

[0073] The third parameter value can be 50° - 68°. Preferably, the third parameter value can be 68°. When the included angle β formed by the length direction of the second bridge piece 62 and the width direction of the fin strip 11 is 68°, the boundary layer effect of the fluid can be just destroyed, more turbulences can be generated, and the air flow direction flowing from the first bridge piece 61 through the second bridge piece 62 can be just changed, thereby prolonging the heat exchange time of the second bridge piece 62.

[0074] Among them, the value range of the included angle β formed by the length direction of the second bridge piece 62 and the width direction of the fin strip 11 can be from 68° to 70°. Preferably, when the included angle β formed by the length direction of the second bridge piece 62 and the width direction of the fin strip 11 is 70°, the air flow direction flowing through the second bridge piece 62 can be better changed, so that the air flow can stay on the surface of the second bridge piece 62 for a longer time, thereby enhancing the heat exchange efficiency of the second bridge piece 62.

[0075] In addition, the included angle β formed between the length direction of the second bridge piece 62 and the width direction of the fin strip 11 is set to be less than the fourth parameter value. If the included angle formed between the length direction of the second bridge piece 62 and the width direction of the fin strip 11 is greater than the fourth parameter value, it will cause the contact area between the air flow and the second bridge piece 62 to decrease, and the air flow direction flowing through the second bridge piece 62 cannot be changed to a greater extent, thereby reducing the heat exchange effect of the second bridge piece 62. Therefore, the included angle β formed between the length direction of the second bridge piece 62 and the width direction of the fin strip 11 cannot be greater than the fourth parameter value.

[0076] The fourth parameter value can be 90° to 100°. Preferably, the fourth parameter value can be set to 90°. When the included angle β formed between the length direction of the second bridge piece 62 and the width direction of the fin strip 11 is 90°, it just makes the contact area between the air flow and the second bridge piece 62 smaller, resulting in a lower heat exchange effect of the second bridge piece 62.

[0077] Among them, the value range of the included angle β formed between the length direction of the second bridge piece 62 and the width direction of the fin strip 11 can be 60° to 90°. For example, the included angle β formed between the length direction of the second bridge piece 62 and the width direction of the fin strip 11 can be set to 60°, 75°, and 80°. Preferably, if the included angle β formed between the length direction of the second bridge piece 62 and the width direction of the fin strip 11 is 75°, the contact area between the air flow and the second bridge piece 62 can be further increased, and more turbulences can also be increased, so that the air flow is more evenly distributed in the entire fin 1 area, thereby improving the overall heat exchange efficiency of the second bridge piece 62.

[0078] According to some embodiments of the present invention, as Figure 4 shown, the distance from the edge of one end of the second bridge piece 62 close to the tube hole 111 to the center of the tube hole 111 is d, along the length direction of the fin strip 11, the distance between the centers of two adjacent tube holes 111 is L1, the outer diameter of the heat exchange tube 2 is D1, and the diameter of the flat area 3 is D2. Among them, the relational expression satisfied by d, L1, D1, and D2 is: D2 + 0.4×(L1 - D2) ≤ d ≤ D2 + 0.6×(L1 - D2).

[0079] Among them, the size parameter relationship is established among L1, D1, D2, and d. In this way, it can be ensured that the air flow after flowing through the first bridge piece 61 is effectively cut, thereby increasing the kinetic energy of the turbulence. Moreover, by setting it in this way, the distances from the edges of one ends of the second bridge piece 62, the first bridge piece 61, and the end bridge piece 7 close to the tube hole 111 to the center of the tube hole 111 are not equal, so that the air flow can pass through multiple divisions and turns along the flow direction, thereby increasing the turbulence degree of the fluid and also increasing the stiffness of the fin 1.

[0080] For example, along the length direction of the fin strip 11, the distance from the edge of one end of the second bridge piece 62 close to the tube hole 111 to the center of the tube hole 111 can be set to be greater than the distances from the edges of one ends of the first bridge piece 61 and the end bridge piece 7 close to the tube hole 111 to the center of the tube hole 111. In this way, the distance from the edge of one end of the first bridge piece 61 close to the tube hole 111 to the center of the tube hole 111 is relatively close, which can more directly affect the fluid flow near the heat exchange tube 2, so that the air flow at the first bridge piece 61 can fully exchange heat with the refrigerant in the heat exchange tube 2, and the heat exchange efficiency between the first bridge piece 61 and the refrigerant in the heat exchange tube 2 can also be improved.

[0081] Furthermore, the distance from the edge of one end of the second bridge piece 62 close to the tube hole 111 to the center of the tube hole 111 is relatively far, which can cause the first bridge piece 61 and the second bridge piece 62 to be arranged in a dislocation manner in the length direction of the fin strip 11. In the air flow direction (i.e., the width direction of the fin strip 11), the flow path of the air flow can be further adjusted on the basis of the first bridge piece 61 to form a more complex fluid disturbance pattern, which helps to break the boundary layer effect, thereby promoting the uniform distribution of the air flow in the entire fin 1 area.

[0082] According to some embodiments of the present invention, as Figure 4 shown, the end bridge piece 7 includes: a third bridge piece 71 and a fourth bridge piece 72. The third bridge piece 71 is located on the side of the first bridge piece 61 away from the first center line 41. Among them, the third bridge piece 71 extends horizontally along the length direction of the fin strip 11, which can reduce the resistance and enable the air flow to flow smoothly, thereby reducing the energy loss. Moreover, the third bridge piece 71 is away from the side of the first bridge piece 61 away from the first center line 41, so that the third bridge piece 71 can expand the range of the air flow flowing towards the first center line 41, thereby further improving the heat exchange efficiency of the fin 1.

[0083] In addition, the fourth bridge piece 72 is located on the side of the second bridge piece 62 close to the first center line 41, so that the fourth bridge piece 72 can further refine the flow path of the air flow, thereby ensuring the uniform distribution of the air flow in the entire fin 1 area. Moreover, the first center line 41 penetrates through the fourth bridge piece 72, and multiple bridge piece areas 4 share one fourth bridge piece 72. Among them, the fourth bridge piece 72 extends horizontally along the direction of the first center line 41, which can guide the air flow towards the heat exchange tube 2, thereby further enhancing the heat transfer effect.

[0084] According to some embodiments of the present invention, as Figure 4 shown, the included angle formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 is α, the included angle formed by the length direction of the second bridge piece 62 and the width direction of the fin strip 11 is β, and the included angle formed by the length direction of the fourth bridge piece 72 and the width direction of the fin strip 11 is δ. β satisfies the relational expression: β = (α + δ) / 2.

[0085] Among them, the parameter relationship for establishing the size between α, δ and β is β = (α + δ) / 2. The included angle δ formed by the length direction of the fourth bridge piece 72 and the width direction of the fin strip 11 and the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 together determine the included angle β formed by the length direction of the second bridge piece 62 and the width direction of the fin strip 11.

[0086] For example, if the included angle α formed by the length direction of the first bridge piece 61 and the width direction of the fin strip 11 is set to 70°, and the included angle δ formed by the length direction of the fourth bridge piece 72 and the width direction of the fin strip 11 is set to 90°, then the included angle β formed by the length direction of the second bridge piece 62 and the width direction of the fin strip 11 is 80°. In this way, the angle sizes of β, δ and α can be different, so that when the air flow passes from the first bridge piece 61 through the second bridge piece 62, the direction of the air flow can be changed. Moreover, when the air flow passing through the second bridge piece 62 passes through the fourth bridge piece 72, the direction of the air flow can be changed again, enabling the air flow to fully exchange heat with the refrigerant in the heat exchange tube 2 and also extending the residence time of the air flow on the surface of the fin 1, thereby improving the heat transfer effect.

[0087] According to some embodiments of the present invention, as Figure 4 shown, the tube hole 111 has a third center line 43. The third center line 43 passes through the center of the tube hole 111 and extends along the width direction of the fin strip 11. The intersection point of the extension line of the edge of the end of the third bridge piece 71 far from the third center line 43 and the outer diameter of the heat exchange tube 2 is A, and the intersection point of the extension line of the edge of the end of the third bridge piece 71 close to the third center line 43 and the outer diameter of the heat exchange tube 2 is B.

[0088] Among them, inclined surfaces are provided on both sides of the third bridge piece 71, and the inclined surfaces are all inclined towards the heat exchange tube 2. Since there is an intersection point A between the extension line of the edge of the end of the third bridge piece 71 far from the third center line 43 and the outer diameter of the heat exchange tube 2, and the intersection point of the extension line of the edge of the end of the third bridge piece 71 close to the third center line 43 and the outer diameter of the heat exchange tube 2 is B, the air flow can be accurately guided to the heat exchange tube 2. The heat comes from the refrigerant in the heat exchange tube 2 (the heat exchange tube 2 can be set as a copper tube), that is, the heat exchange tube 2 is the source of heat. For the heat exchanger 100 used in an air conditioner, the heat is released from the surface of the heat exchange tube 2, transferred to the surface of the heat exchange tube 2 through convective heat transfer, and then conducted to the surface of the fin 1. Due to the setting of the third bridge piece 71, the third bridge piece 71 with air flow guiding can accelerate the air flow impact on the heat exchange tube 2, thereby improving the convective heat transfer coefficient.

[0089] Further, the included angle γ formed by the connecting line between the intersection point A of the extension line of the edge of the end of the third bridge piece 71 far from the third central line 43 and the outer diameter of the heat exchange tube 2 and the center of the tube hole 111 and the width direction of the fin strip 11, and the included angle θ formed by the connecting line between the intersection point B of the extension line of the edge of the end of the third bridge piece 71 close to the third central line 43 and the outer diameter of the heat exchange tube 2 and the center of the tube hole 111 and the width direction of the fin strip 11 satisfy the relational expression: 90° ≤ γ ≤ θ ≤ 180°.

[0090] Among them, γ is not greater than θ, that is to say, the third bridge piece 71 can completely direct the air flow to the heat exchange tube 2, or can further accelerate the air flow impacting the heat exchange tube 2, thereby improving the convective heat transfer coefficient. For example, θ can be set to 100°, 120° and 160°, and correspondingly, γ can be set to 95°, 110° and 140°. When θ is set to 160° and γ is set to 140°, the air flow flowing out of the third bridge piece 71 can completely blow directly against the windward surface of the heat exchange tube 2.

[0091] Specifically, when the third bridge piece 71 is located in front of the heat exchange tube 2, that is, in the direction of the inflow of the air flow, when the air flow passes through the third bridge piece 71, the cross-sectional area of the inlet of the third bridge piece 71 is larger than the cross-sectional area of the outlet. When the air flow flows in from the inlet of the third bridge piece 71 and flows out from the outlet, since the cross-sectional area of the through hole 511 of the third bridge piece 71 gradually decreases, the air flow speed at the outlet of the third bridge piece 71 can be increased, and it can be directly blown against the windward surface of the heat exchange tube 2 through diversion, thereby improving the convective heat transfer intensity outside the heat exchange tube 2 and also improving the heat exchange efficiency.

[0092] In addition, when the third bridge piece 71 is also provided behind the heat exchange tube 2, that is, in the direction of the outflow of the air flow, when the air flow passes through the heat exchange tube 2, a wake vortex is likely to be formed at the tail of the heat exchange tube 2, resulting in an increase in pressure drop. By arranging the third bridge piece 71 at the position behind the heat exchange tube 2, the air flow can be quickly separated from the heat exchange tube 2, and the air flow can be prevented from gathering at the tail of the heat exchange tube 2 to form a wake vortex, thereby reducing the pressure loss.

[0093] According to some embodiments of the present invention, as Figure 2 and Figure 4 shown, along the length direction of the fin strip 11, the distance between the centers of two adjacent tube holes 111 is L1, and the maximum distance from the end of the third bridge piece 71 far from the third central line 43 to the third central line 43 is L2. L1 and L2 satisfy the relational expression: L2 ≥ 0.25L1.

[0094] Among them, along the length direction of the fin strip 11, the maximum distance L2 from the end of the third bridge piece 71 away from the third center line 43 to the third center line 43 is greater than or equal to 0.25 times the distance L1 between the centers of two adjacent tube holes 111 along the length direction of the fin strip 11. In this way, the range of disturbance to the air flow can be expanded. This kind of disturbance can destroy the boundary layer effect, thereby increasing the air flow disturbance ability and also increasing the contact area between the air flow and the surface of the fin 1, so as to improve the convective heat transfer coefficient.

[0095] Moreover, by setting the maximum distance L2 from the end of the third bridge piece 71 away from the third center line 43 to the third center line 43 to be relatively large, the outer region of the fin strip 11 can be effectively covered, thereby reducing the occurrence of uneven air flow and further improving the heat transfer efficiency.

[0096] Also, as Figure 4 shown, the minimum distance from the end of the third bridge piece 71 close to the third center line 43 to the third center line 43 is L3, the width of the bridge piece 51 is W, and the outer diameter of the heat exchange tube 2 is D1. L3, W and D1 satisfy the relationship: W ≤ L3 < 0.5D1.

[0097] Among them, the minimum distance L3 from the end of the third bridge piece 71 close to the third center line 43 to the third center line 43 is greater than or equal to the width W of the bridge piece 51. In this way, the end of the third bridge piece 71 close to the third center line 43 will not overly occupy the fluid passage near the heat exchange tube 2, thereby avoiding the obstruction to the air flow, ensuring the smooth flow of the fluid, and reducing the local resistance. Moreover, the minimum distance L3 from the end of the third bridge piece 71 close to the third center line 43 to the third center line 43 is greater than or equal to the width W of the bridge piece 51, which can avoid the situation that the distance between the third bridge piece 71 and the second center line 42 is too small and also avoid the air flow not covering the outer region of the fin strip 11.

[0098] Furthermore, the minimum distance L3 from the end of the third bridge piece 71 close to the third center line 43 to the third center line 43 is less than half of the outer diameter D1 of the heat exchange tube 2. In this way, the air flow can be better guided to flow around the heat exchange tube 2 and directly blow the windward surface of the heat exchange tube 2, thereby improving the convective heat transfer intensity outside the heat exchange tube 2. Moreover, the minimum distance L3 from the end of the third bridge piece 71 close to the third center line 43 to the third center line 43 is less than half of the outer diameter D1 of the heat exchange tube 2. In this way, the distance between the third bridge piece 71 and the third center line 43 is relatively close, which can increase the strength of the third center line 43 region, thereby improving the bending strength of the fin 1.

[0099] According to some embodiments of the present invention, as Figure 4As shown, the bridge fin sub-regions 5 located on both sides of the first center line 41 are symmetrically arranged with respect to the first center line 41, and the bridge fin sub-regions 5 located on both sides of the second center line 42 are symmetrically arranged with respect to the second center line 42. In this way, the shapes and angles of the bridge fins 51 in the bridge fin sub-regions 5 can be made the same, so that the air flow can flow into each bridge fin sub-region 5 more evenly. Moreover, the bridge fin sub-regions 5 are symmetrically arranged with respect to the first center line 41 and the second center line 42, which can also reduce the phenomenon of too high or too low local flow velocity and evenly distribute the stress, thus preventing the fins 1 from deforming or being damaged.

[0100] Furthermore, compared with conventional fins, for the fin 1 of the present invention, along the width direction of the fin 1, the air flow is cut by the mutually staggered bridge fins 51 along the way and changes direction under the guidance of the mutually staggered bridge fins 51. The effect of cutting the air flow is obvious. Figure 10 It can be clearly seen from the comparison of the flow fields that the high-speed air flow distribution of the present invention is wider, thus increasing the turbulence intensity of the air flow.

[0101] As Figure 11 shown by the comparison of the temperature fields of the fin 1 body, the low-temperature region of the fin 1 body of the present invention is wider, indicating that under the same inlet flow rate, because the fin 1 of the present invention has a better heat exchange effect and can take away more heat, the temperature of the fin 1 body is lower. The heat exchange capacity of the fin 1 of the present invention is increased by 2.5% compared with that of the conventional fin. In addition, due to the surface structure of the staggered bridge fins 51, the stiffness of the fin 1 can be increased, and the maximum deformation amount is reduced from 40.1 mm to 31.1 mm, thus reducing the risk of difficult blanking during the processing of the fin 1.

[0102] The air conditioner according to the second aspect embodiment of the present invention includes: the heat exchanger 100 of the above embodiment.

[0103] The air conditioner includes an indoor unit and an outdoor unit. The indoor unit and the outdoor unit are connected by pipelines to transmit the refrigerant. The indoor unit includes an indoor heat exchanger and an indoor fan. The outdoor unit includes a compressor, a four-way valve, an outdoor heat exchanger, an outdoor fan, and an expansion valve. The compressor, the outdoor heat exchanger, the expansion valve, and the indoor heat exchanger connected in sequence form a refrigerant circuit. The refrigerant circulates in the refrigerant circuit and exchanges heat with air through the outdoor heat exchanger and the indoor heat exchanger respectively to achieve the refrigeration mode or the heating mode of the cabinet air conditioner. The compressor is configured to compress the refrigerant so that the low-pressure refrigerant is compressed to form a high-pressure refrigerant.

[0104] The outdoor heat exchanger is configured to exchange heat between outdoor air and the refrigerant flowing through the outdoor heat exchanger. For example, in the cooling mode of the cabinet air conditioner, the outdoor heat exchanger operates as a condenser, enabling the refrigerant compressed by the compressor to dissipate heat to the outdoor air through the outdoor heat exchanger and condense. In the heating mode of the cabinet air conditioner, the outdoor heat exchanger operates as an evaporator, enabling the decompressed refrigerant to absorb heat from the outdoor air through the outdoor heat exchanger and evaporate.

[0105] In some embodiments, the outdoor heat exchanger further includes fin 1 to increase the contact area between the outdoor air and the refrigerant flowing through the outdoor heat exchanger, thereby improving the heat exchange efficiency between the outdoor air and the refrigerant.

[0106] The outdoor fan is configured to suck outdoor air into the outdoor unit through the outdoor air inlet of the outdoor unit and send the outdoor air that has exchanged heat with the outdoor heat exchanger out through the outdoor air outlet of the outdoor unit. The outdoor fan provides power for the flow of outdoor air.

[0107] The expansion valve is connected between the outdoor heat exchanger and the indoor heat exchanger. The opening degree of the expansion valve adjusts the refrigerant pressure flowing through the outdoor heat exchanger and the indoor heat exchanger to regulate the refrigerant flow rate between the outdoor heat exchanger and the indoor heat exchanger. The flow rate and pressure of the refrigerant flowing between the outdoor heat exchanger and the indoor heat exchanger will affect the heat exchange performance of the outdoor heat exchanger and the indoor heat exchanger. The expansion valve can be an electronic valve, and the opening degree of the expansion valve is adjustable to control the flow rate and pressure of the refrigerant flowing through the expansion valve.

[0108] The four-way valve is connected within the refrigerant circuit and is configured to switch the flow direction of the refrigerant in the refrigerant circuit so that the cabinet air conditioner can execute the cooling mode or the heating mode.

[0109] The indoor heat exchanger is configured to exchange heat between indoor air and the refrigerant flowing through the indoor heat exchanger. For example, in the cooling mode of the cabinet air conditioner, the indoor heat exchanger operates as an evaporator, enabling the refrigerant that has dissipated heat through the outdoor heat exchanger to absorb heat from the indoor air through the indoor heat exchanger and evaporate. In the heating mode of the cabinet air conditioner, the indoor heat exchanger operates as a condenser, enabling the refrigerant that has absorbed heat through the outdoor heat exchanger to dissipate heat to the indoor air through the indoor heat exchanger and condense.

[0110] In some embodiments, the indoor heat exchanger further includes fin 1 to increase the contact area between the indoor air and the refrigerant flowing through the indoor heat exchanger, thereby improving the heat exchange efficiency between the indoor air and the refrigerant.

[0111] The indoor fan is configured to suck indoor air into the indoor unit through the third air inlet of the indoor unit and send the indoor air that has exchanged heat with the indoor heat exchanger out through the fourth air outlet of the indoor unit. The indoor fan provides power for the flow of indoor air.

[0112] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. are based on the orientation or positional relationship 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.

[0113] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "schematic embodiments", "examples", "specific examples", or "some examples", etc. 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.

[0114] 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: Fins, the fins comprising a plurality of fin strips, the plurality of fin strips being distributed and connected in the width direction of the fins, each fin strip being provided with a plurality of tube holes spaced apart in the length direction of the fin strip, and the tube holes in two adjacent fin strips being staggered; Heat exchange tubes, the heat exchange tubes being inserted into the tube holes, and a refrigerant flowing through the heat exchange tubes; Characterized in that The fin strip comprises: A plurality of flat areas, the flat areas being arranged along the circumference of the tube hole; A plurality of bridge areas, the plurality of bridge areas and the plurality of flat areas being alternately distributed in the length direction of the fin strip, each bridge area having a first center line extending in the length direction of the fin strip and a second center line extending in the width direction of the fin strip, the bridge area being separated into a plurality of bridge sub-areas by the intersecting first center line and second center line, each bridge sub-area including a plurality of bridge pieces spaced apart in the width direction of the fin strip, the bridge pieces protruding from one side of the fin strip towards the thickness direction of the fin, and through holes being formed in the bridge area at positions corresponding to the bridge pieces; Wherein, in each bridge sub-area, the plurality of bridge pieces include: End bridge pieces, the end bridge pieces extending in the length direction of the fin strip; Middle bridge pieces, the middle bridge pieces being located between the end bridge pieces, and the length direction of the middle bridge pieces having an angle greater than 0° and less than 90° with the width direction of the fin strip.

2. The heat exchanger according to claim 1, characterized in that There are at least two middle bridge pieces and they include: A first bridge piece; A second bridge piece, the second bridge piece being located on the side of the first bridge piece close to the first center line, and the angle between the length direction of the first bridge piece and the width direction of the fin strip being different from the angle between the length direction of the second bridge piece and the width direction of the fin strip.

3. The heat exchanger according to claim 2, wherein, The angle formed by the length direction of the first bridge piece and the width direction of the fin strip is α, and α satisfies the relational expression: 45° ≤ α < 90°; and / or The angle formed by the length direction of the second bridge piece and the width direction of the fin strip is β, and β satisfies the relational expression: 68° ≤ β < 90°.

4. The heat exchanger according to claim 2, wherein, The distance from the edge of one end of the second bridge piece close to the tube hole to the center of the tube hole is d, along the length direction of the fin strip, the distance between the centers of two adjacent tube holes is L1, the outer diameter of the heat exchange tube is D1, and the diameter of the flat area is D2. Wherein, the relational expression satisfied by d, L1, D1 and D2 is: D2 + 0.4×(L1 - D2) ≤ d ≤ D2 + 0.6×(L1 - D2).

5. The heat exchanger according to claim 2, wherein The end bridge piece includes: A third bridge piece, the third bridge piece being located on the side of the first bridge piece away from the first center line; A fourth bridge piece, the fourth bridge piece being located on the side of the second bridge piece close to the first center line, the first center line passing through the fourth bridge piece, and a plurality of bridge areas sharing one fourth bridge piece.

6. The heat exchanger according to claim 5, characterized in that, The included angle formed by the length direction of the first bridge piece and the width direction of the fin strip is α, the included angle formed by the length direction of the second bridge piece and the width direction of the fin strip is β, and the included angle formed by the length direction of the fourth bridge piece and the width direction of the fin strip is δ. The relationship satisfied by β is: β = (α + δ) / 2.

7. The heat exchanger according to claim 5, characterized in that, The tube hole has a third center line, which passes through the center of the tube hole and extends along the width direction of the fin strip. The intersection point of the extension line of the edge of the third bridge piece far from the third center line and the outer diameter of the heat exchange tube is A. The included angle formed by the connection line between A and the center of the tube hole and the width direction of the fin strip is γ; The intersection point of the extension line of the edge of the third bridge piece close to the third center line and the outer diameter of the heat exchange tube is B. The included angle formed by the connection line between B and the center of the tube hole and the width direction of the fin strip is θ. The relationship satisfied by γ and θ is: 90° ≤ γ ≤ θ ≤ 180°.

8. The heat exchanger according to claim 7, characterized in that, Along the length direction of the fin strip, the distance between the centers of two adjacent tube holes is L1, and the maximum distance from the end of the third bridge piece far from the third center line to the third center line is L2. The relationship satisfied by L1 and L2 is: L2 ≥ 0.25L1; and / or The minimum distance from the end of the third bridge piece close to the third center line to the third center line is L3, the width of the bridge piece is W, and the outer diameter of the heat exchange tube is D1. The relationship satisfied by L3, W and D1 is: W ≤ L3 < 0.5D1.

9. The heat exchanger according to claim 1, wherein The bridge piece sub-regions on both sides of the first center line are symmetrically arranged with respect to the first center line, and the bridge piece sub-regions on both sides of the second center line are symmetrically arranged with respect to the second center line.

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

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