Heat exchanger and air conditioner

Abstract

The utility model discloses a heat exchanger and air conditioner, this heat exchanger includes: fin, fin includes a plurality of fin strips, a plurality of fin strips distribute and be connected in the width direction of fin, and each fin strip is provided with a plurality of tube holes that interval distribution along the length direction of fin strip, heat exchange pipe, heat exchange pipe is worn in the tube hole, fin strip includes: a plurality of flat area, and the flat area is along the circumference of tube hole and is arranged, a plurality of bridge piece area, a plurality of bridge piece area and a plurality of flat area staggered distribution along the length direction of fin strip, and each bridge piece area includes a plurality of bridge piece row that interval distribution along the width direction of fin strip, wherein, a plurality of bridge piece row includes end bridge piece row and middle bridge piece row, along the width direction of fin strip, middle bridge piece row is located between the end bridge piece row of both ends, and the width of the bridge piece of middle bridge piece row is less than the width of the bridge piece of end bridge piece row of both ends. Therefore, can reduce the pressure drop, can also improve the heat exchange amount simultaneously to can improve the heat exchange efficiency of heat exchanger.

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 one of the core components of an air conditioning system, the heat exchanger's heat exchange capacity directly affects the air conditioner's cooling and heating performance. Simultaneously, the heat exchanger's capacity directly impacts the air conditioning system's energy efficiency ratio; improving the heat exchanger's performance can reduce the air conditioner's energy consumption.

[0003] With stricter national energy efficiency standards for air conditioners and rising raw material prices, cost pressures are increasing further. Small-diameter heat exchangers are one of the most effective ways to reduce costs. Furthermore, after the Kigali Amendment came into effect, air conditioning systems are required to reduce refrigerant charge or the proportion of HCs-type refrigerants; small-diameter heat exchangers can reduce the refrigerant charge. However, both small-diameter and aluminum tube heat exchangers have certain disadvantages compared to traditional heat exchangers. The former has a relatively smaller heat exchange area, and the latter's aluminum tubes have a lower thermal conductivity than copper tubes.

[0004] In existing technologies, the main forms of heat exchanger fins for air conditioners are corrugated fins and slotted fins (window fins, bridge fins, etc.). Slotted fins have a higher external convective heat transfer coefficient than corrugated fins due to their stronger ability to turbulent airflow. Therefore, for indoor units and outdoor units of single-cooling units, most manufacturers mainly use slotted fins. Bridge fins are one of the main application forms, with multiple rows of bridge fins arranged on the fin surface. Each row of bridge fins has the same width and height, which leads to a decrease in heat transfer capacity when airflow passes through multiple rows of bridge fins. At the same time, it also increases pressure drop, causing pressure loss. Utility Model Content

[0005] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes a heat exchanger that can reduce pressure drop while increasing heat exchange capacity, thereby improving the heat exchanger's heat exchange efficiency.

[0006] This utility model also proposes an air conditioner.

[0007] According to a first aspect of the present invention, a heat exchanger includes: fins, each fin comprising a plurality of fin strips distributed and connected in the width direction of the fins, each fin strip having a plurality of tube holes spaced apart along the length direction of the fin strip, the tube holes in adjacent fin strips being staggered; heat exchange tubes passing through the tube holes, the heat exchange tubes containing refrigerant; each fin strip comprising: a plurality of flat regions arranged circumferentially along the tube holes; and a plurality of bridge regions, the plurality of bridge regions and the plurality of flat regions being arranged along the fins. The fins are staggered along their length, and each fin area includes multiple rows of fins spaced apart along the width direction of the fin strip. Each row of fins includes at least one fin. The fins protrude from the side of the fin strip facing the thickness direction of the fin. The fin area has through holes at the positions corresponding to the fins. The multiple rows of fins include end rows and middle rows. Along the width direction of the fin strip, the middle rows of fins are located between the end rows of fins at both ends. The width of the fins in the middle rows of fins is smaller than the width of the fins in the end rows of fins at both ends.

[0008] Therefore, this heat exchanger can reduce pressure drop and increase heat exchange capacity, thereby improving the heat exchanger's heat exchange efficiency.

[0009] According to some embodiments of the present invention, the number of the middle bridge plate rows is multiple, and the width of the bridge plates of the end bridge plate rows at both ends and the width of the bridge plates of the multiple middle bridge plate rows first decrease and then increase in the direction extending from one end to the other in the width direction of the fin strip.

[0010] According to some embodiments of the present invention, the plurality of central bridge plate rows include: a first central bridge plate row, the first central bridge plate row being located between the end bridge plate rows at both ends; and a second central bridge plate row, the second central bridge plate row being located on both sides of the first central bridge plate row, wherein the width of the bridge plate in the second central bridge plate row is smaller than the width of the bridge plate in the end bridge plate row and larger than the width of the bridge plate in the first central bridge plate row.

[0011] According to some embodiments of the present invention, the width of the bridge pieces in the end bridge piece rows at both ends is the same, and the width of the bridge pieces in the second middle bridge piece rows located on both sides of the first middle bridge piece row is the same.

[0012] According to some embodiments of the present invention, the orthographic projection of the center line of the bridge piece of the first middle bridge piece row extending along the length direction of the fin strip in the bridge piece area coincides with the center line of the fin strip extending along the length direction. The end bridge piece rows at both ends are symmetrically arranged with respect to the first middle bridge piece row, and the second middle bridge piece rows located on both sides of the first middle bridge piece row are symmetrically arranged with respect to the first middle bridge piece row.

[0013] According to some embodiments of the present invention, the width of the bridge piece in the end bridge piece row is M1, the width of the bridge piece in the first middle bridge piece row is M2, and the width of the bridge piece in the second middle bridge piece row is M3. M1, M2, and M3 satisfy the relationship: 0.6mm≤M2<M3<M1≤1.8mm.

[0014] According to some embodiments of the present invention, each bridge piece includes: a sidewall connected to one end of the through hole along its length; and a top wall connected between the two sidewalls, wherein the top wall and the through hole are spaced apart along the thickness direction of the fin strip; wherein, at least one of the bridge pieces in the bridge piece row has an included angle greater than 0° and less than 90° with respect to the width direction of the fin strip.

[0015] According to some embodiments of the present invention, the top wall of the bridge piece in the first middle bridge piece row is parallel to the width direction of the fin strip; the top wall of the bridge piece in the end bridge piece row has the included angle with the width direction of the fin strip, and the side of the top wall of the bridge piece in the end bridge piece row away from the first middle bridge piece row is higher than the other side of the bridge piece row near the first middle bridge piece row; the top wall of the bridge piece in the second middle bridge piece row has the included angle with the width direction of the fin strip, and the side of the top wall of the bridge piece in the second middle bridge piece row away from the first middle bridge piece row is higher than the other side of the bridge piece row near the first middle bridge piece row.

[0016] According to some embodiments of the present invention, the height of the top wall of the bridge piece in the first middle bridge piece row is H1, the height of the top wall of the bridge piece in the second middle bridge piece row near the first middle bridge piece row is H2, and the height of the top wall of the bridge piece in the second middle bridge piece row away from the first middle bridge piece row is H3. H1, H2 and H3 satisfy the relationship: 0.3mm≤H1≤H2<H3≤1mm.

[0017] An air conditioner according to a second aspect of the present invention includes: the heat exchanger described above.

[0018] 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

[0019] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0020] Figure 1 This is a schematic diagram of the structure of a heat exchanger according to an embodiment of the present utility model;

[0021] Figure 2 This is a schematic diagram of the fin structure according to an embodiment of the present utility model;

[0022] Figure 3 yes Figure 2 A magnified view of region A in the middle;

[0023] Figure 4 This is a partial schematic diagram of the fins according to an embodiment of the present utility model;

[0024] Figure 5 This is a side view of the fin according to an embodiment of the present utility model;

[0025] Figure 6 This is a schematic diagram showing the height of the bridge plates in the middle bridge plate row of the fins according to an embodiment of the present utility model;

[0026] Figure 7 This is an isometric view of the fin according to an embodiment of the present invention;

[0027] Figure 8 yes Figure 7 A magnified view of region B in the middle;

[0028] Figure 9 This is a schematic diagram comparing the flow field of an embodiment of the present invention with that of a conventional fin;

[0029] Figure 10 This is a schematic diagram comparing the temperature field of an embodiment of the present invention with that of a conventional fin.

[0030] Figure label:

[0031] 100. Heat exchanger;

[0032] 1. Fin; 11. Fin strip; 111. Tube hole;

[0033] 2. Heat exchanger tubes;

[0034] 3. Flat area;

[0035] 4. Bridge area; 41. Bridge row;

[0036] 5. End bridge plate array;

[0037] 6. Middle bridge section; 61. First middle bridge section; 62. Second middle bridge section;

[0038] 7. Bridge plate; 71. Side wall; 72. Top wall; 73. Through hole; 74. First side wall; 75. Second side wall. Detailed Implementation

[0039] The embodiments of the present invention are described in detail below. The embodiments described with reference to the accompanying drawings are exemplary. The embodiments of the present invention are described in detail below.

[0040] The following is for reference. Figures 1-10 A heat exchanger 100 according to an embodiment of the present utility model is described.

[0041] Reference Figures 1-5 As shown, the heat exchanger 100 of the first aspect embodiment of the present invention includes: fins 1 and heat exchange tubes 2, wherein the heat exchange tubes 2 can serve as a medium for heat exchange between the refrigerant and the outside air, and 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 usually tightly attached to the outer surface of the heat exchange tubes 2, which can effectively increase the heat exchange contact area between the air and the heat exchange tubes 2, thereby accelerating the heat transfer speed and improving the heat exchange efficiency.

[0042] The fin 1 includes multiple fin strips 11, which are distributed and connected along the width direction of the fin 1. Each fin strip 11 has multiple tube holes 111 spaced apart along the length direction of the fin strip 11, with the tube holes 111 in adjacent fin strips 11 staggered. The heat exchanger 100 includes several heat exchange tubes 2 and several fins 1. The several fins 1 are arranged parallel to each other, with a certain distance between adjacent fins 1. Several heat exchange tubes 2 extend through each fin 1, and each heat exchange tube 2 is connected to an adjacent heat exchange tube 2 via 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 in the fluid channel of the heat exchange tube 2 can exchange heat with the airflow flowing in the fin fluid channel through the heat exchange tube 2 and the fins 1.

[0043] The heat exchange tubes 2 can have any suitable size, and 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, 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 properties, and the length and width of the fins 1 can be adjusted according to the size of the heat exchanger 100.

[0044] Each finned strip 11 includes multiple tube holes 111 distributed along the length of the finned strip 11. A heat exchange tube 2 is inserted into the tube hole 111. The heat exchange tube 2 can be a copper tube, and a refrigerant flows inside the heat exchange tube 2. In other words, each finned strip 11 can be connected to the heat exchange tube 2 through the tube hole 111, thereby achieving the heat exchange effect between the fins 1 and the heat exchange tube 2, and thus improving the heat exchange efficiency.

[0045] Furthermore, the tube holes 111 in two adjacent fin strips 11 are staggered. That is, the tube holes 111 in one fin strip 11 and the tube holes 111 in the adjacent fin strip 11 are staggered, so that the heat exchange tubes 2 passing through the corresponding tube holes 111 on the fin 1 are staggered accordingly, which can further improve the heat exchange efficiency of the heat exchanger 100.

[0046] Furthermore, the fin strip 11 includes multiple flat regions 3 and multiple bridge regions 4, with the multiple flat regions 3 arranged circumferentially along the tube hole 111. Specifically, the flat regions 3 surround the outer periphery of the tube hole 111 circumferentially, and are flat in shape. This arrangement increases the contact area between the fins 1 and the tube hole 111, thereby facilitating better heat conduction. It also reduces the flow resistance of the fluid in the flat regions 3 (i.e., reduces turbulence between the fins 1), thus improving fluid flowability. Additionally, it provides a smoother flow channel, reducing fluid friction loss and thereby increasing flow velocity.

[0047] Furthermore, multiple bridge zones 4 and multiple flat zones 3 are staggered along the length of the fin strip 11, which can reduce the flow resistance of the fluid between different regions and reduce the turbulence of the fluid between different regions, thereby improving the smoothness of fluid flow.

[0048] Furthermore, each bridge region 4 includes multiple bridge rows 41 spaced apart along the width direction of the fin strip 11, and each bridge row 41 includes at least one bridge 7. This significantly increases the contact area between the fluid and the bridge row 41, thereby improving the heat exchange efficiency of the fin 1. Moreover, the bridge 7 is convex relative to the side of the fin strip 11 facing the thickness direction of the fin 1, which increases the effective contact area between the fluid and the surface of the bridge 7, further disrupting the thermal boundary layer and improving the local heat transfer coefficient.

[0049] Furthermore, the bridge section 4 has through holes 73 at the positions corresponding to the bridge section 7. These through holes 73 on the fin strip 11 can divide the airflow into multiple airflow channels, thereby increasing the heat exchange surface area of ​​the fin 1. The presence of the through holes 73 provides additional heat exchange paths and allows the fluid to undergo secondary heat exchange through these through holes 73, further improving the heat transfer efficiency of the fin 1.

[0050] Among them, the multiple bridge plate rows 41 include end bridge plate rows 5 and middle bridge plate rows 6. Along the width direction of the fin strip 11, the middle bridge plate row 6 is located between the end bridge plate rows 5 at both ends, and the width of the bridge plate 7 of the middle bridge plate row 6 is smaller than the width of the bridge plate 7 of the end bridge plate rows 5 at both ends.

[0051] Specifically, the end bridge fin rows 5 at both ends are located on both sides of the middle bridge fin row 6. The middle bridge fin row 6 is positioned close to the heat exchange tube 2. Since the width of the bridge fins 7 in the middle bridge fin row 6 is smaller than the width of the bridge fins 7 in the end bridge fin rows 5, along the width direction of the fin strips 11, i.e., the airflow direction, when the airflow enters from the bridge fins 7 of the end bridge fin row 5, the larger width of the bridge fins 7 in the end bridge fin row 5 increases the contact area between the airflow and the bridge fins 7 in the end bridge fin row 5, thereby increasing the heat exchange area and improving the heat exchange capacity. Moreover, the narrower width of the bridge fins 7 in the middle bridge fin row 6 provides a relatively spacious channel, allowing for smoother fluid flow and reducing obstruction to fluid flow. This reduces pressure drop, allows for more uniform airflow distribution, avoids excessively high or low local flow velocities, reduces pressure loss, and thus lowers the pressure drop of the heat exchanger 100 while also increasing the heat exchange capacity.

[0052] Therefore, the heat exchanger 100 can reduce the pressure drop and increase the heat exchange capacity, thereby improving the heat exchange efficiency of the heat exchanger 100.

[0053] According to specific embodiments of this utility model, such as Figure 3 and Figure 4 As shown, there are multiple middle bridge plate rows 6. In the direction extending from one end to the other in the width direction of the fin strip 11, the width of the bridge plate 7 of the end bridge plate rows 5 and the width of the bridge plate 7 of the multiple middle bridge plate rows 6 first decrease and then increase.

[0054] Specifically, the width of the bridge plates 7 in each middle bridge plate row 6 is the same, and the width of the bridge plates 7 in each end bridge plate row 5 is also the same. This ensures more uniform fluid flow, thus facilitating fluid movement. Furthermore, the width of the bridge plates 7 in the end bridge plate rows 5 and the multiple middle bridge plate rows 6 decreases first and then increases along the width direction of the fin strips 11. In the area of ​​the end bridge plate rows 5, where the fluid velocity is higher or the turbulence is greater, using wider bridge plates 7 can guide and rectify the flow, preventing local vortices or backflow. It also increases the contact area between the airflow and the bridge plates 7 of the end bridge plate rows 5, further increasing heat exchange efficiency.

[0055] Furthermore, the width of the bridge plates 7 of the multiple middle bridge plates 6 facing the area close to the heat exchange tube 2 gradually decreases along the width direction of the fin strips 11 in the end bridge plates 5 and the middle bridge plates 6. This can avoid resistance concentration, further reduce pressure loss, accelerate the fluid, enhance turbulence, and thus improve the local heat transfer coefficient.

[0056] Furthermore, the width of the bridge plates 7 in the middle bridge plate row 6 and the end bridge plate row 5 gradually increases along the width direction of the fin strips 11. This can balance the pressure distribution at both ends of the end bridge plate row 5, making it more stable, and can further increase the heat exchange area and improve the heat exchange capacity, thereby further improving the heat exchange efficiency of the heat exchanger 100.

[0057] According to some embodiments of this utility model, such as Figure 4 As shown, the multiple middle bridge plate rows 6 include: a first middle bridge plate row 61 and a second middle bridge plate row 62. The first middle bridge plate row 61 is located between the end bridge plate rows 5 at both ends, and the second middle bridge plate rows 62 are located on both sides of the first middle bridge plate row 61. Thus, the first middle bridge plate row 61 is located at the center position in the width direction of the fin strip 11. The width of the bridge plate 7 of the second middle bridge plate row 62 is smaller than the width of the bridge plate 7 of the end bridge plate row 5, and the width of the bridge plate 7 of the second middle bridge plate row 62 is larger than the width of the bridge plate 7 of the first middle bridge plate row 61.

[0058] Thus, the width of the bridge plates 7 in the end bridge plate row 5, the second middle bridge plate row 62, and the first middle bridge plate row 61 gradually decreases along the width direction of the fin strip 11. In this way, the airflow flows sequentially from the end bridge plate row 5 and the second middle bridge plate row 62 to the first middle bridge plate row 61, which can gradually reduce the airflow resistance and thus reduce the pressure loss between the end bridge plate row 5, the second middle bridge plate row 62, and the first middle bridge plate row 61.

[0059] Similarly, the width of the bridge plates 7 in the first middle bridge plate row 61, the second middle bridge plate row 62, and the end bridge plate row 5 gradually increases along the width direction of the fin strip 11. In this way, the contact area between the first middle bridge plate row 61, the second middle bridge plate row 62, and the end bridge plate row 5 and the airflow can be further increased, thereby further improving the heat exchange effect and also increasing the disturbance to the airflow.

[0060] According to some embodiments of this utility model, the width of the bridge plates 7 in the end bridge plate rows 5 at both ends is the same. This ensures that the airflow encounters the same resistance distribution when entering and leaving the fins 1, thereby achieving a more uniform fluid distribution. The equal width of the bridge plates 7 in the end bridge plate rows 5 at both ends provides more balanced support and stability, thus reducing the occurrence of overall structural instability due to weakness at one end.

[0061] Furthermore, the width of the bridge plates 7 in the second middle bridge plate rows 62 located on both sides of the first middle bridge plate row 61 is the same. This can further balance the forces on both sides of the first middle bridge plate row 61, thus avoiding the overall structural instability caused by the weakness of one side, and also enhancing the durability and reliability of the fin 1, thereby making the fin 1 more stable.

[0062] According to some embodiments of this utility model, such as Figure 2 and Figure 4 As shown, the orthographic projection of the center line of the bridge plate 7 of the first middle bridge plate row 61 extending along the length direction of the fin strip 11 in the bridge plate area 4 coincides with the center line of the fin strip 11 extending along the length direction. In this way, the airflow can be guided to the area of ​​the center line extending along the length direction of the fin strip 11, which can increase the heat exchange area between the airflow and the heat exchange tube 2, thereby further improving the heat exchange capacity.

[0063] Furthermore, the end bridge plate rows 5 at both ends are symmetrically arranged about the first middle bridge plate row 61. This symmetrical arrangement can balance the forces at both ends of the fin 1 and reduce the risk of deformation or damage caused by uneven force on one side, thereby improving the overall structural strength and stability of the fin 1 and extending its service life.

[0064] Furthermore, the second middle bridge plate rows 62 located on both sides of the first middle bridge plate row 61 are symmetrically arranged with respect to the first middle bridge plate row 61. This makes the force on the second middle bridge plate rows 62 on both sides of the first middle bridge plate row 61 more balanced, and also makes the fluid flow on the second middle bridge plate rows 62 on both sides of the first middle bridge plate row 61 more uniform. This can avoid the fluid velocity being too fast or too slow, thereby reducing the occurrence of turbulence.

[0065] According to some embodiments of this utility model, such as Figure 4 As shown, the width of bridge piece 7 in end bridge piece row 5 is M1, the width of bridge piece 7 in first middle bridge piece row 61 is M2, and the width of bridge piece 7 in second middle bridge piece row 62 is M3. M1, M2, and M3 satisfy the relationship: 0.6mm≤M2<M3<M1≤1.8mm.

[0066] In this configuration, the width M2 of the bridge piece 7 in the first middle bridge piece row 61 is smaller than the width M3 of the bridge piece 7 in the second middle bridge piece row 62, and the width M3 of the bridge piece 7 in the second middle bridge piece row 62 is smaller than the width M1 of the bridge piece 7 in the end bridge piece row 5. This allows the widths of the bridge pieces 7 in the end bridge piece row 5, the second middle bridge piece row 62, and the first middle bridge piece row 61 to decrease sequentially, or the widths of the bridge pieces 7 in the first middle bridge piece row 61, the second middle bridge piece row 62, and the end bridge piece row 5 to increase sequentially.

[0067] Furthermore, the width M2 of the bridge plate 7 in the first middle bridge plate row 61 should not be less than the first parameter value. If the width M2 of the bridge plate 7 in the first middle bridge plate row 61 is less than the first parameter value, the width of the bridge plate 7 in the first middle bridge plate row 61 will be too small, which will reduce the contact area between the bridge plate 7 and the fluid and reduce the heat exchange efficiency of the heat exchanger 100. Moreover, a smaller width of the bridge plate 7 in the first middle bridge plate row 61 will result in lower strength of the bridge plate 7, making it more susceptible to damage from external forces, vibrations, or changes in internal pressure. Therefore, it is necessary to ensure that the width M2 of the bridge plate 7 in the first middle bridge plate row 61 is not less than the first parameter value.

[0068] The first parameter value can be 0.5mm-0.6mm. Preferably, when the first parameter value is 0.6mm, the width M2 of the bridge piece 7 of the first middle bridge piece row 61 is 0.6mm, which can just make the bridge piece 7 of the first middle bridge piece row 61 have sufficient strength, thereby preventing it from deforming.

[0069] The width M2 of the bridge plate 7 in the first middle bridge plate row 61 can be in the range of 0.6mm to 1mm. Preferably, when the width M2 of the bridge plate 7 in the first middle bridge plate row 61 is 1mm, the airflow passing through the bridge plate 7 in the first middle bridge plate row 61 can increase the heat exchange area between the airflow and the bridge plate 7 in the first middle bridge plate row 61, and can also make the bridge plate 7 in the first middle bridge plate row 61 have sufficient strength.

[0070] Furthermore, the width M1 of the bridge plate 7 in the end bridge plate row 5 is set not to be greater than the second parameter value. If the width M1 of the bridge plate 7 in the end bridge plate row 5 is set to be greater than the second parameter value, the width of the bridge plate 7 in the end bridge plate row 5 will be larger, which will result in a larger pressure difference between the fluid entering and leaving the heat exchanger 100, i.e., an increase in pressure drop.

[0071] The second parameter value can be 1.8 to 2 mm. Preferably, the second parameter value can be 1.8 mm. When the width M1 of the bridge piece 7 of the end bridge piece row 5 is 1.8 mm, the pressure drop of the bridge piece 7 passing through the end bridge piece row 5 can be made smaller.

[0072] The width M1 of the bridge piece 7 in the end bridge piece row 5 can range from 1mm to 1.8mm. For example, the width M1 of the bridge piece 7 in the end bridge piece row 5 can be set to 1mm, 1.5mm and 1.8mm. Preferably, when the width M1 of the bridge piece 7 in the end bridge piece row 5 is 1.5mm, the pressure drop of the bridge piece 7 in the end bridge piece row 5 can be moderate, and it can also have sufficient strength, thereby extending the service life of the bridge piece 7 in the end bridge piece row 5.

[0073] According to some embodiments of this utility model, such as Figure 7 and Figure 8 As shown, each bridge piece 7 includes a side wall 71 and a top wall 72. The side wall 71 is connected to one end of the through hole 73 along its length direction, and the top wall 72 is connected between the two side walls 71. The top wall 72 and the through hole 73 are spaced apart along the thickness direction of the fin strip 11.

[0074] Specifically, the sidewall 71 has a first sidewall 74, a second sidewall 75, and a top wall 72 that can form through holes 73 on the fin strip 11. The first sidewall 74 is obliquely connected to one end of the through hole 73 along its length, and the second sidewall 75 is obliquely connected to the other end of the through hole 73 along its length. In this way, multiple through holes 73 are formed around the heat exchange tube 2, and the heat from the heat exchange tube 2 can be dissipated through the multiple through holes 73, thereby improving heat dissipation efficiency. The through holes 73 can also disrupt the flow boundary layer, thereby increasing heat transfer.

[0075] In this configuration, the top wall 72 of at least one bridge plate 7 in the bridge plate row 41 has an angle greater than 0° and less than 90° with respect to the width direction of the fin strip 11. This can change the direction and path of fluid flow, enhance airflow turbulence, improve heat transfer capacity, and increase fluid turbulence. Higher turbulence helps to break the boundary layer, thereby further improving heat transfer efficiency.

[0076] According to some embodiments of this utility model, such as Figure 6 As shown, the top wall 72 of the bridge plate 7 in the first middle bridge plate row 61 is parallel to the width direction of the fin strip 11. This facilitates smooth fluid flow and reduces obstruction, thereby reducing pressure loss. The top wall 72 of the bridge plate 7 in the end bridge plate row 5 forms an angle with the width direction of the fin strip 11. This enhances airflow turbulence, improves heat transfer capacity, and increases turbulence. Higher turbulence can break the boundary layer effect, thus improving overall heat transfer efficiency.

[0077] Furthermore, the side of the top wall 72 of the bridge plate 7 in the end bridge plate row 5 that is away from the first middle bridge plate row 61 is higher than the side that is close to the first middle bridge plate row 61. This makes the top wall 72 of the bridge plate 7 in the end bridge plate row 5 an inclined surface. Along the airflow direction, the height of the top wall 72 of the bridge plate 7 in the end bridge plate row 5 gradually decreases, which can play a role in turbulence, increasing heat exchange, and also guiding the airflow to the second middle bridge plate row 62. Moreover, the inclined surface of the top wall 72 of the bridge plate 7 in the end bridge plate row 5 can also reduce obstruction to the airflow, thereby allowing the airflow to pass through more quickly.

[0078] Furthermore, the top wall 72 of the bridge plate 7 in the second middle bridge plate row 62 has an angle with the width direction of the fin strip 11. This can enhance airflow turbulence, improve heat transfer capacity, and increase turbulence. Higher turbulence can break the boundary layer effect, thereby improving the overall heat transfer efficiency.

[0079] Furthermore, the side of the top wall 72 of the bridge plate 7 in the second middle bridge plate row 62 that is farther from the first middle bridge plate row 61 is higher than the side that is closer to the first middle bridge plate row 61. This makes the top wall 72 of the bridge plate 7 in the second middle bridge plate row 62 an inclined surface. Along the airflow direction, the height of the top wall 72 of the bridge plate 7 in the second middle bridge plate row 62 gradually decreases, which can further turbulent the airflow, increase heat exchange, and guide the airflow towards the first middle bridge plate row 61. Moreover, the inclined surface of the top wall 72 of the bridge plate 7 in the second middle bridge plate row 62 also reduces obstruction to the airflow, thereby allowing the airflow to pass through more quickly.

[0080] According to some embodiments of this utility model, such as Figure 6 As shown, the height of the top wall 72 of the bridge piece 7 of the first middle bridge piece row 61 is H1, the height of the top wall 72 of the bridge piece 7 of the second middle bridge piece row 62 on the side closer to the first middle bridge piece row 61 is H2, and the height of the top wall 72 of the bridge piece 7 of the second middle bridge piece row 62 on the side farther away from the first middle bridge piece row 61 is H3. H1, H2 and H3 satisfy the relationship: 0.3mm≤H1≤H2<H3≤1mm.

[0081] In this configuration, the height H1 of the top wall 72 of the bridge plate 7 of the first middle bridge plate row 61 is not greater than the height H2 of the top wall 72 of the bridge plate 7 of the second middle bridge plate row 62 on the side closest to the first middle bridge plate row 61. This can change the flow path of the airflow, increase the disturbance, facilitate the smooth flow of the airflow through the top wall 72 of the bridge plate 7 of the second middle bridge plate row 62 over the first middle bridge plate row 61, and reduce the obstruction of the airflow through the bridge plate 7 of the first middle bridge plate row 61 over the bridge plate 7 of the second middle bridge plate row 62, thereby accelerating the flow rate of the fluid.

[0082] Furthermore, the height H2 of the top wall 72 of the bridge piece 7 of the second middle bridge piece row 62 on the side closer to the first middle bridge piece row 61 is less than the height H3 of the top wall 72 of the bridge piece 7 of the second middle bridge piece row 62 on the side farther from the first middle bridge piece row 61. In this way, the top wall 72 of the bridge piece 7 of the second middle bridge piece row 62 can be an inclined surface that faces the first middle bridge piece row 61, thereby changing the flow path of the airflow, increasing the disturbance, guiding the airflow passing through the top wall 72 of the bridge piece 7 of the second middle bridge piece row 62 towards the first middle bridge piece row 61, and accelerating the flow velocity of the airflow.

[0083] Furthermore, the height H1 of the top wall 72 of the bridge plate 7 in the first middle bridge plate row 61 is not less than the third parameter value. If the height H1 of the top wall 72 of the bridge plate 7 in the first middle bridge plate row 61 is less than the third parameter value, the effective surface area for heat exchange between the bridge plate 7 and the fluid will be reduced, which can decrease the overall heat exchange capacity of the heat exchanger 100. Therefore, the height H1 of the top wall 72 of the bridge plate 7 in the first middle bridge plate row 61 is not less than the third parameter value.

[0084] The third parameter value can be 0.2mm-0.3mm. Preferably, the third parameter value can be 0.3mm. When the height H1 of the top wall 72 of the bridge plate 7 of the first middle bridge plate row 61 is 0.3mm, the airflow can just come into contact with the bridge plate 7 of the first middle bridge plate row 61, thereby enhancing heat exchange.

[0085] The height H1 of the top wall 72 of the bridge plate 7 in the first middle bridge plate row 61 can be in the range of 0.3mm to 0.5mm. Preferably, when the height H1 of the top wall 72 of the bridge plate 7 in the first middle bridge plate row 61 is 0.5mm, the airflow can fully contact the bridge plate 7 in the first middle bridge plate row 61, thereby increasing the heat exchange capacity and reducing pressure loss.

[0086] Furthermore, the height H3 of the top wall 72 of the bridge plate 7 of the second middle bridge plate row 62 on the side away from the first middle bridge plate row 61 should not be greater than the fourth parameter value. If the height H3 of the top wall 72 of the bridge plate 7 of the second middle bridge plate row 62 on the side away from the first middle bridge plate row 61 is greater than the fourth parameter value, it will cause the fluid to encounter greater resistance when passing through, and the fluid will need a longer path to bypass it. This will lead to an increase in pressure drop in the system, and thus require more energy to push the fluid through the heat exchanger 100, increasing energy loss. Therefore, the height H3 of the top wall 72 of the bridge plate 7 of the second middle bridge plate row 62 on the side away from the first middle bridge plate row 61 should not be greater than the fourth parameter value.

[0087] The fourth parameter value can be 1mm-1.5mm. Preferably, the fourth parameter value can be 1mm, 1.2mm and 1.3mm. When the height H3 of the top wall 72 of the bridge plate 7 of the second middle bridge plate row 62 away from the first middle bridge plate row 61 is 1mm, the resistance to the fluid can be reduced, the pressure drop can be reduced, and the heat exchange can be increased.

[0088] Furthermore, to illustrate the advantages of this utility model, the specific structural parameters are as follows: the height H1 of the bridge piece 7 in the first middle bridge piece row 61 is 0.8mm; the height H2 of the top wall 72 of the bridge piece 7 in the second middle bridge piece row 62 on the side closest to the first middle bridge piece row 61 is 0.85mm; and the height H3 of the top wall 72 of the bridge piece 7 in the second middle bridge piece row 62 on the side furthest from the first middle bridge piece row 61 is 0.75mm. The spacing W between adjacent bridge piece rows 41 is 1.0mm; the width M1 of the bridge piece 7 in the end bridge piece row 5 is 1.2mm; the width M2 of the bridge piece 7 in the first middle bridge piece row 61 is 1.0mm; and the width M3 of the bridge piece 7 in the second middle bridge piece row 62 is 1.1mm.

[0089] Compared to conventional bridge plates with equal bridge height and width, the fin 1 of this invention utilizes the high airflow velocity at the narrow cross-section to set a narrow bridge plate to reduce resistance, while designing a wide bridge plate and a sloping bridge at the wide cross-section. This fully utilizes the large temperature difference between the front airflow and the fin 1 to increase the bridge area and the turbulence of the incoming flow, ensuring low pressure loss, while also increasing the heat exchange capacity, thus achieving the purpose of synergistic heat exchange.

[0090] like Figure 9 As shown, a comparison of the flow field of the fin 1 of this invention and that of conventional fins clearly shows that the wide bridge fin 7 at the front end of the fin 1 of this invention, combined with its inclined top wall 72, has a more pronounced turbulence effect, and the external heat transfer coefficient is increased by 2.8% compared to conventional fin 1. Figure 10 As shown, the temperature field of fin 1 of this utility model is compared with that of conventional fins. It can be clearly seen that the low temperature zone of fin 1 of this utility model is wider. This means that under the same inlet flow rate, due to the better heat exchange effect of this utility model, more heat can be removed. Therefore, the temperature of fin 1 is lower, which ultimately leads to a 0.6% increase in heat exchange capacity of this utility model compared with conventional fins.

[0091] Furthermore, designing a wide bridge fin 7 at a narrow cross-section, i.e., a wider bridge fin 7, fully utilizes the enhanced heat transfer capacity of high-speed airflow. However, this increases the pressure drop. When pursuing high heat transfer, a wide bridge fin 7 at a narrow cross-section can be selected, resulting in a 0.4% improvement in heat transfer compared to conventional fins with uniform bridge width. Alternatively, designing a narrow bridge fin 7 at a narrow cross-section, i.e., a narrower bridge fin 7, while appropriately reducing heat transfer capacity, also significantly reduces pressure loss. When pursuing low pressure loss or low noise, a narrow bridge fin 7 at a narrow cross-section can be selected, resulting in a 1.4% reduction in pressure drop compared to conventional fins with uniform bridge width.

[0092] Furthermore, this utility model utilizes the advantage of low pressure loss of narrow bridge fins 7 at narrow cross sections, and designs the top wall 72 of bridge fins 7 as an inclined surface to enhance airflow turbulence and improve heat exchange capacity. Compared with a uniform bridge width, the heat exchange capacity is increased by 0.5% under the condition of comparable comprehensive heat exchange factor. Therefore, by using the fin structure provided by this utility model, the number of fins 1 can be reduced while achieving the same heat exchange capacity, and the cost of heat exchanger 100 can also be reduced.

[0093] An air conditioner according to a second aspect of the present invention includes: the heat exchanger 100 described in the above embodiment.

[0094] An air conditioner includes an indoor unit and an outdoor unit, which are connected by pipes to transfer 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, outdoor heat exchanger, expansion valve, and indoor heat exchanger, connected in sequence, form a refrigerant circuit. The refrigerant circulates in the refrigerant circuit and exchanges heat with the air through the outdoor and indoor heat exchangers to achieve the cooling or heating mode of the cabinet air conditioner. The compressor is configured to compress the refrigerant, so that the low-pressure refrigerant is compressed into high-pressure refrigerant.

[0095] The outdoor heat exchanger is configured to exchange heat between outdoor air and refrigerant transported within it. For example, in the cooling mode of a cabinet air conditioner, the outdoor heat exchanger functions as a condenser, causing the refrigerant compressed by the compressor to dissipate heat to the outdoor air and condense. In the heating mode of the cabinet air conditioner, the outdoor heat exchanger functions as an evaporator, causing the depressurized refrigerant to absorb heat from the outdoor air and evaporate.

[0096] In some embodiments, the outdoor heat exchanger further includes fins 1 to increase the contact area between the outdoor air and the refrigerant transported in the outdoor heat exchanger, thereby improving the heat exchange efficiency between the outdoor air and the refrigerant.

[0097] The outdoor fan is configured to draw outdoor air into the outdoor unit through the outdoor air inlet and expel the outdoor air, after it has been heated by the outdoor heat exchanger, through the outdoor air outlet. The outdoor fan provides power for the flow of outdoor air.

[0098] An expansion valve connects the outdoor and indoor heat exchangers. The opening degree of the expansion valve regulates the refrigerant pressure flowing through both heat exchangers, thereby regulating the refrigerant flow rate between them. The flow rate and pressure of the refrigerant flowing between the outdoor and indoor heat exchangers affect their heat exchange performance. The expansion valve can be an electronic valve, and its opening degree is adjustable to control the refrigerant flow rate and pressure.

[0099] The four-way valve is connected to 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 perform cooling mode or heating mode.

[0100] The indoor heat exchanger is configured to exchange heat between indoor air and refrigerant transported within it. For example, in the cooling mode of a cabinet air conditioner, the indoor heat exchanger operates as an evaporator, causing the refrigerant, after dissipating heat from the outdoor heat exchanger, to absorb heat from the indoor air and evaporate. In the heating mode of the cabinet air conditioner, the indoor heat exchanger operates as a condenser, causing the refrigerant, after absorbing heat from the outdoor heat exchanger, to dissipate heat to the indoor air and condense.

[0101] In some embodiments, the indoor heat exchanger further includes fins 1 to increase the contact area between indoor air and the refrigerant transported in the indoor heat exchanger, thereby improving the heat exchange efficiency between indoor air and the refrigerant.

[0102] The indoor fan is configured to draw indoor air into the indoor unit through the third air inlet and discharge the indoor air, after heat exchange with the indoor heat exchanger, through the fourth air outlet. The indoor fan provides power for the airflow.

[0103] 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", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this utility model and simplifying the description, and do not 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.

[0104] 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.

[0105] 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 a plurality of fin strips, which are distributed and connected in the width direction of the fin. Each fin strip is provided with a plurality of tube holes that are spaced apart along the length direction of the fin strip, and the tube holes in two adjacent fin strips 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 strip includes: Multiple flat zones are provided along the circumference of the pipe hole; Multiple bridge plate areas are staggered with multiple flat areas along the length direction of the fin strip. Each bridge plate area includes multiple bridge plate rows spaced apart along the width direction of the fin strip. Each bridge plate row includes at least one bridge plate. The bridge plate protrudes from the side of the fin strip facing the thickness direction of the fin. The bridge plate area has through holes at the positions corresponding to the bridge plates. The plurality of bridge strip rows include end bridge strip rows and middle bridge strip rows. Along the width direction of the fin strip, the middle bridge strip row is located between the end bridge strip rows at both ends, and the width of the bridge strips in the middle bridge strip row is smaller than the width of the bridge strips in the end bridge strip rows at both ends.

2. The heat exchanger according to claim 1, characterized in that, The number of the middle bridge plate rows is multiple. In the direction extending from one end to the other in the width direction of the fin strip, the width of the bridge plate in the end bridge plate rows at both ends and the width of the bridge plate in the multiple middle bridge plate rows first decreases and then increases.

3. The heat exchanger according to claim 2, characterized in that, The plurality of said central bridge segments include: The first middle bridge section is located between the end bridge sections at both ends; The second middle bridge plate row is located on both sides of the first middle bridge plate row. The width of the bridge plate in the second middle bridge plate row is smaller than the width of the bridge plate in the end bridge plate row but larger than the width of the bridge plate in the first middle bridge plate row.

4. The heat exchanger according to claim 3, characterized in that, The bridge plates in the end bridge plate rows at both ends have the same width, and the bridge plates in the second middle bridge plate rows located on both sides of the first middle bridge plate row have the same width.

5. The heat exchanger according to claim 4, characterized in that, The orthographic projection of the center line of the bridge plate of the first middle bridge plate row extending along the length direction of the fin strip in the bridge plate area coincides with the center line of the fin strip extending along the length direction. The end bridge plate rows at both ends are symmetrically arranged with respect to the first middle bridge plate row. The second middle bridge plate rows located on both sides of the first middle bridge plate row are symmetrically arranged with respect to the first middle bridge plate row.

6. The heat exchanger according to claim 4, characterized in that, The width of the bridge piece in the end bridge piece row is M1, the width of the bridge piece in the first middle bridge piece row is M2, and the width of the bridge piece in the second middle bridge piece row is M3. M1, M2, and M3 satisfy the relationship: 0.6mm≤M2<M3<M1≤1.8mm.

7. The heat exchanger according to claim 3, characterized in that, Each of the bridge pieces includes: Sidewall, the sidewall being connected to one end of the through hole along its length; A top wall, which is connected between the two side walls, and the top wall and the through hole are spaced apart along the thickness direction of the fin strip; Wherein, at least one of the bridge plates in the bridge plate row has an angle greater than 0° and less than 90° between the top wall of the bridge plate and the width direction of the fin strip.

8. The heat exchanger according to claim 7, characterized in that, The top wall of the bridge plate in the first middle bridge plate row is parallel to the width direction of the fin strip; The top wall of the bridge piece in the end bridge piece row has the included angle with the width direction of the fin strip, and the side of the top wall of the bridge piece in the end bridge piece row away from the first middle bridge piece row is higher than the other side of the top wall of the bridge piece row near the first middle bridge piece row. The top wall of the bridge piece in the second middle bridge piece row has the included angle with the width direction of the fin strip, and the side of the top wall of the bridge piece in the second middle bridge piece row away from the first middle bridge piece row is higher than the other side of the top wall of the bridge piece row near the first middle bridge piece row.

9. The heat exchanger according to claim 8, characterized in that, The height of the top wall of the bridge piece in the first middle bridge piece row is H1, the height of the top wall of the bridge piece in the second middle bridge piece row near the first middle bridge piece row is H2, and the height of the top wall of the bridge piece in the second middle bridge piece row away from the first middle bridge piece row is H3. H1, H2, and H3 satisfy the relationship: 0.3mm≤H1≤H2<H3≤1mm.

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

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