Heat exchanger and air conditioner

Abstract

The utility model discloses a heat exchanger and air conditioner, this heat exchanger includes: fin, heat exchange pipe, a plurality of bridge piece area, every bridge piece area includes the interval distribution of a plurality of bridge piece row along the width direction of fin strip, and every bridge piece row includes the interval distribution of at least three bridge pieces along the length direction of fin strip, wherein, in every bridge piece area, at least three bridge pieces of at least one bridge piece row and at least three bridge pieces of another bridge piece row are partially staggered in the width direction of fin strip. Thus, every bridge piece row includes the interval distribution of at least three bridge pieces along the length direction of fin strip, can improve the contact area with air, also can increase the quantity of the edge of bridge piece, thereby can strengthen secondary turbulence, because at least three bridge pieces of at least one bridge piece row and at least three bridge pieces of another bridge piece row are partially staggered in the width direction of fin strip, can form periodic disturbance in the air flow direction, thereby help to destroy thermal boundary layer.

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 types 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 types. The bridging direction is perpendicular to the airflow direction, and each bridge fin almost runs through the fin surface. However, its airflow turbulence capability is relatively weak, and it also suffers from low heat exchange efficiency. 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 in which each fin row includes at least three fins spaced apart along the length of the fin strip, which can increase the contact area with air and increase the number of edges of the fins, thereby enhancing secondary turbulence. Since at least three fins in at least one fin row are partially staggered with at least three fins in another fin row in the width direction of the fin strip, periodic turbulence can be formed in the airflow direction, thereby helping to break the thermal boundary layer.

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

[0007] According to a first aspect embodiment of the present invention, the 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 along the circumference of the tube holes; a plurality of bridge regions, the plurality of bridge regions being arranged along the circumference of the plurality of flat regions. The fin strips are staggered along their length direction. Each bridge area includes multiple bridge strip rows spaced apart along the width direction of the fin strip. Each bridge strip row includes at least three bridge strips spaced apart along the length direction of the fin strip. The bridge strips protrude from the side of the fin strip facing the thickness direction of the fin. The bridge area has through holes at the positions corresponding to the bridge strips. In each bridge area, the at least three bridge strips of at least one bridge strip row are partially staggered with the at least three bridge strips of another bridge strip row in the width direction of the fin strip.

[0008] Therefore, each bridge row in the heat exchanger includes at least three bridges spaced apart along the length of the fin strip, which can increase the contact area with air and increase the number of bridge edges, thereby enhancing secondary turbulence. Since at least three bridges in at least one bridge row and at least three bridges in another bridge row are partially staggered in the width direction of the fin strip, periodic disturbances can be formed in the airflow direction, thereby helping to break the thermal boundary layer.

[0009] According to some embodiments of the present invention, the plurality of bridge plate rows include: an end bridge plate row, the end bridge plate rows being located at both ends of the fin strip in the width direction; and a middle bridge plate row, the middle bridge plate row being located between the end bridge plate rows at both ends, wherein the at least three bridge plates of the middle bridge plate row and the at least three bridge plates of the end bridge plate rows are at least partially staggered in the width direction of the fin strip.

[0010] According to some embodiments of the present invention, there are at least two central bridge plates, and the at least three bridge plates of two adjacent central bridge plates are arranged opposite each other in the width direction of the fin strip.

[0011] According to some embodiments of the present invention, the number of bridge pieces in the end bridge piece row is greater than the number of bridge pieces in the middle bridge piece row.

[0012] According to some embodiments of the present invention, the end bridge strips at both ends are symmetrical about the centerline extending along the length direction of the fin strip.

[0013] According to some embodiments of the present invention, in each bridge plate row, the distance between two adjacent bridge plates is S, and S satisfies the relationship: 0.2mm≤S≤2mm.

[0014] According to some embodiments of the present invention, in each bridge plate area, the spacing between two adjacent bridge plate rows is M, and M satisfies the relationship: 0.8mm≤M≤2mm.

[0015] According to some embodiments of the present invention, the bridge plate includes: a first sidewall, which is obliquely disposed on one side of the through hole; a second sidewall, which is obliquely disposed on the other side of the through hole and is spaced apart from the first sidewall in the length direction of the fin strip; and a top wall, which is connected to the top of the first sidewall and the second sidewall.

[0016] According to some embodiments of this utility model, the height of the first sidewall and the second sidewall is H, where H satisfies the relationship: 0.3mm≤H≤1mm; and / or the angle between the first sidewall and the fin strip and the angle between the second sidewall and the fin strip are both α, where α satisfies the relationship: 30°≤α≤60°; and / or the width of the first sidewall and the second sidewall is W, where W satisfies the relationship: 0.8mm≤W≤1.5mm; and / or the distance between the bottom ends of the first sidewall and the second sidewall is L1, and the length of the top wall is L2, where L1 and L2 satisfy the relationship: 1mm≤L2≤L1≤10mm.

[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 fins along the airflow direction according to an embodiment of the present invention;

[0025] Figure 6 This is a partial schematic diagram of the side of the fin along the airflow direction according to an embodiment of the present invention;

[0026] Figure 7 This is a side view of the fin according to an embodiment of the present utility model;

[0027] Figure 8 This is an isometric view of the fin according to an embodiment of the present invention;

[0028] Figure 9 yes Figure 8 A magnified view of region B in the middle;

[0029] Figure 10 (a) is a schematic diagram of the flow field of a conventional fin;

[0030] Figure 10 (b) is a schematic diagram of the flow field of the fins according to an embodiment of the present invention;

[0031] Figure 11 (c) is a schematic diagram of the temperature field of a conventional fin;

[0032] Figure 11 (d) is a schematic diagram of the temperature field of the fins according to an embodiment of the present invention.

[0033] Figure label:

[0034] 100. Heat exchanger;

[0035] 1. Fin; 11. Fin strip; 111. Tube hole;

[0036] 2. Heat exchanger tubes;

[0037] 3. Flat area;

[0038] 4. Bridge section area; 41. Bridge section row; 42. Bridge section; 421. First side wall; 422. Second side wall; 423. Top wall;

[0039] 43. Through hole;

[0040] 5. End bridge plate row; 6. Middle bridge plate row. Detailed Implementation

[0041] 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.

[0042] The following is for reference. Figures 1-11 A heat exchanger 100 according to an embodiment of the present utility model is described.

[0043] 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.

[0044] The fin 1 includes multiple fin strips 11, which are distributed and connected in the width direction of the fin 1. Each fin strip 11 is provided with multiple holes 111 spaced apart along the length direction of the fin strip 11, and the holes 111 in two adjacent fin strips 11 are staggered. Figure 1 and Figure 2 As shown, the heat exchanger 100 includes several heat exchange tubes 2 and several fins 1. The fins 1 are arranged side by side in parallel, with a certain distance between adjacent fins 1. Several heat exchange tubes 2 extend through each fin 1. Each heat exchange tube 2 is connected to an adjacent heat exchange tube 2 through a bend, thereby forming a fluid channel for the heat exchange tube 2. Fluid (e.g., coolant) can flow through the fluid channel of the heat exchange tube 2, and the fluid in the fluid channel of the heat exchange tube 2 can exchange heat with the airflow flowing in the fluid channel of the fins 1 and the heat exchange tube 2.

[0045] The heat exchange tubes 2 can have any suitable size. The number of heat exchange tubes 2 can be arbitrary. The heat exchange tubes 2 can be made of any suitable material with good heat transfer properties, 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. The length and width of the fins 1 can be adjusted according to the size of the heat exchanger 100.

[0046] Each finned strip 11 includes multiple tube holes 111 distributed along the length of the finned strip 11. The heat exchange tube 2 passes through the tube holes 111 and a refrigerant flows through the heat exchange tube 2. In other words, each finned strip 11 can be connected to the heat exchange tube 2 through the tube holes 111, thereby achieving the heat exchange effect between the fins 1 and the heat exchange tube 2 and improving the heat exchange efficiency.

[0047] 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.

[0048] 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.

[0049] 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.

[0050] Specifically, 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 three bridges 42 spaced apart along the length direction of the fin strip 11. This significantly increases the contact area between the fluid and the fin 1, thereby improving the heat exchange efficiency of the fin 1. Moreover, the at least three bridges 42 spaced apart along the length direction of the fin strip 11 can generate additional disturbances in the fluid flow path, which can disrupt the thermal boundary layer, promote turbulence, and thus improve heat transfer efficiency. It can also help to more uniformly distribute mechanical stress and avoid deformation and damage to the fin strip 11 due to stress concentration.

[0051] Furthermore, the bridge plate 42 protrudes from 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 plate 42, further disrupting the thermal boundary layer and improving the local heat transfer coefficient. The bridge plate region 4 has through holes 43 formed at the positions corresponding to the bridge plate 42. Thus, the multiple through holes 43 corresponding to the multiple bridge plate regions 4 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 43 provides additional heat exchange paths and allows the fluid to undergo secondary heat exchange through these through holes 43, thereby further improving the heat transfer efficiency of the fin 1.

[0052] In each bridge zone 4, at least three bridge plates 42 of at least one bridge plate row 41 and at least three bridge plates 42 of another bridge plate row 41 are partially staggered in the width direction of the fin strip 11, which can form periodic disturbances in the airflow direction. This can more effectively break the thermal boundary layer, promote more turbulence in the fluid, thereby increasing the turbulence intensity of the airflow and enhancing the heat transfer effect, thus improving the heat exchange performance of the heat exchanger 100.

[0053] Furthermore, within each bridge section 4, each bridge row 41 is provided with at least three bridges 42, and the at least three bridges 42 correspondingly form at least three through holes 43. Each through hole 43 of each bridge 42 allows partial fluid passage, thereby generating additional disturbance in the fluid flow path, further breaking the thermal boundary layer, promoting turbulence, and thus increasing the contact area between the fluid and the surface of the fins 1, thereby enhancing the heat transfer capacity. Compared with conventional fins, the number of fins 1 can be reduced to achieve the same heat transfer capacity, thereby reducing the cost of the heat exchanger 100. The at least three bridges 42 also provide more support points for the fins 1, thereby enhancing the overall bending resistance of the fin strips 11.

[0054] Moreover, at least three bridge plates 42 of at least one bridge plate row 41 and at least three bridge plates of another bridge plate row are partially staggered in the width direction of the fin strip 11, which can form periodic disturbances in the airflow direction, thereby helping to break the thermal boundary layer and making the fluid more evenly distributed between the fins 1, thus avoiding the situation where the flow velocity in a local area is too high or too low.

[0055] Furthermore, the partial staggered arrangement of at least three bridge plates 42 in one bridge plate row 41 with at least three bridge plates in another bridge plate row in the width direction of the fin strip 11 not only enhances the heat exchange effect but also increases the overall structural strength of the fin 1, thereby preventing deformation or damage to the fin 1 during manufacturing, transportation, or use. Moreover, the partial staggered arrangement of at least three bridge plates 42 in one bridge plate row 41 with at least three bridge plates in another bridge plate row in the width direction of the fin strip 1 further improves the rigidity and vibration resistance of the fin 1, making it particularly suitable for applications requiring long-term stable operation.

[0056] Therefore, each fin row 41 of the heat exchanger 100 includes at least three fins 42 spaced apart along the length of the fin strip 11, which can increase the contact area with air and increase the number of edges of the fins 42, thereby enhancing secondary turbulence. Since at least three fins 42 of at least one fin row 41 and at least three fins 42 of another fin row 41 are partially staggered in the width direction of the fin strip 11, periodic turbulence can be formed in the airflow direction, thereby helping to break the thermal boundary layer.

[0057] According to some embodiments of this utility model, such as Figure 4 As shown, the multiple bridge fin rows 41 include: end bridge fin rows 5 and middle bridge fin rows 6. For example, the end bridge fin rows 5 and the middle bridge fin rows 6 can be arranged in a total of five rows. The end bridge fin rows 5 are located at both ends of the width direction of the fin strip 11. The end bridge fin rows 5 include a head end and a tail end along the width direction (i.e., the airflow direction) of the fin strip 11. The head end is the airflow inlet and the tail end is the airflow outlet. In this way, the turbulence and eddies of the fluid at the inlet and outlet can be reduced, thereby reducing the flow resistance and improving the overall heat exchange efficiency.

[0058] Furthermore, the middle bridge plate row 6 is located between the end bridge plate rows 5 at both ends. Since both the end bridge plate row 5 and the middle bridge plate row 6 are provided with at least three bridge plates 42, the airflow passing through the end bridge plate row 5 is divided into multiple airflow channels by the middle bridge plate row 6.

[0059] Furthermore, at least three bridge plates 42 of the middle bridge plate row 6 and at least three bridge plates 42 of the end bridge plate row 5 are at least partially staggered in the width direction of the fin strip 11. When the airflow passes through the end bridge plate row 5 and then flows through the middle bridge plate row 6, the at least three bridge plates 42 of the middle bridge plate row 6 and at least three bridge plates 42 of the end bridge plate row 5 are at least partially staggered in the width direction of the fin strip 11, which further increases the turbulence intensity of the incoming flow. Compared with conventional bridge plates, the heat transfer area of ​​the fin 1 is increased by 5%, the external heat transfer coefficient is increased by 1.5%, and the heat transfer capacity is increased by 1.9%.

[0060] According to some embodiments of this utility model, such as Figure 4 As shown, there are at least two central bridge plates 6, and at least three bridge plates 42 of two adjacent central bridge plate rows 6 are arranged opposite each other in the width direction of the fin strip 11. In this way, a more regular and orderly airflow channel can be formed, thereby ensuring the uniform distribution of airflow in the area of ​​the central bridge plate row 6, and reducing the phenomenon of excessively high or low local flow velocity.

[0061] According to some embodiments of this utility model, such as Figure 4As shown, the number of bridge plates 42 in the end bridge plate row 5 is greater than the number of bridge plates 42 in the middle bridge plate row 6. Since the end bridge plate row 5 is located at both ends of the fin strip 11 (i.e., the inlet and outlet regions), these regions typically bear greater mechanical stress and fluid impact force. Setting the number of bridge plates 42 in the end bridge plate row 5 to be greater than the number of bridge plates 42 in the middle bridge plate row 6 can increase the number of bridge plates 42 and significantly enhance the structural strength at both ends of the fin strip 11, thereby preventing bending or deformation at both ends of the fin strip 11.

[0062] Furthermore, the number of end bridge plates 5 at the airflow inlet is relatively greater than the number of middle bridge plates 6, which can evenly divide the airflow into multiple airflow channels and distribute them to the middle bridge plates 6, thereby reducing flow resistance.

[0063] Furthermore, the number of end bridge plates 5 at the airflow outlet is relatively greater than the number of middle bridge plates 6, which can better guide the fluid to flow smoothly out of the fins 1, thereby ensuring that the fluid can be discharged smoothly and reducing energy loss.

[0064] According to some embodiments of this utility model, such as Figure 4 As shown, the end bridge fins 5 at both ends are symmetrical about the centerline of the fin strip 11 extending along its length. This ensures that the fluid is evenly distributed in each airflow channel when entering and leaving the fin 1.

[0065] The symmetrical design allows for a more balanced flow resistance at the inlet and outlet, thereby improving the fluid throughput efficiency of the heat exchanger 100 and reducing energy loss.

[0066] According to some embodiments of this utility model, such as Figure 4 As shown, in each bridge plate row 41, the distance between two adjacent bridge plates 42 is S, and S satisfies the relationship: 0.2mm≤S≤2mm.

[0067] Specifically, the distance S between two adjacent bridge plates 42 is set to be no less than the first parameter value. If the distance S between two adjacent bridge plates 42 is less than the first parameter value, it will affect the airflow channel, causing the airflow channel to narrow and increasing the resistance when the fluid passes through. Therefore, in each bridge plate row 41, the distance S between two adjacent bridge plates 42 is set to be no less than the first parameter value.

[0068] The first parameter value can be 0.1mm-0.2mm. Preferably, the first parameter value can be 0.2mm. When the distance S between two adjacent bridge plates 42 is 0.2mm, it can just meet the requirement that the airflow can pass smoothly through the distance S between the two adjacent bridge plates 42.

[0069] The spacing S between two adjacent bridge plates 42 can range from 0.2 mm to 0.5 mm. Preferably, when the spacing S between two adjacent bridge plates 42 is 0.5 mm, the turbulence of the incoming flow can be increased when the fluid passes through the channel between the two adjacent bridge plates 42, thereby enhancing heat transfer.

[0070] Furthermore, the spacing S between two adjacent bridge plates 42 is set to be no greater than the second parameter value. If the spacing S between two adjacent bridge plates 42 is greater than the second parameter value, the contact area between the fluid and the fin 1 will be reduced, resulting in a decrease in the overall heat exchange area of ​​the fin 1 and a reduction in heat exchange efficiency.

[0071] The second parameter value can be 2mm to 3mm. Preferably, the second parameter value can be set to 2mm. When the distance S between two adjacent bridge plates 42 is 2mm, the turbulence intensity of the airflow channel between the two adjacent bridge plates 42 is the lowest.

[0072] The spacing S between two adjacent bridge plates 42 can range from 0.5 mm to 2 mm. For example, the spacing S between two adjacent bridge plates 42 can be set to 0.5 mm, 0.6 mm and 1 mm. Preferably, if the spacing S between two adjacent bridge plates 42 is 1 mm, the spacing between the two adjacent bridge plates 42 is moderate, which can further improve the turbulence intensity of the incoming flow, thereby further improving the heat exchange performance of the heat exchanger 100.

[0073] According to some embodiments of this utility model, such as Figure 4 and Figure 7 As shown, in each bridge section area 4, the distance between two adjacent bridge section rows 41 is M, and M satisfies the relationship: 0.8mm≤M≤2mm.

[0074] Specifically, the spacing M between two adjacent bridge plate rows 41 is set to be no less than the third parameter value. If the spacing M between two adjacent bridge plate rows 41 is less than the third parameter value, it will increase the resistance to fluid flow and increase the loss of fluid energy. Therefore, the spacing M between two adjacent bridge plate rows 41 is set to be no less than the third parameter value.

[0075] The third parameter value can be set to 0.5mm to 0.8mm. Preferably, the third parameter value can be set to 0.8mm. When the spacing M between two adjacent bridge plate rows 41 is 0.8mm, the occlusion between the two adjacent bridge plate rows 41 can be avoided, thereby reducing the loss of fluid energy.

[0076] The spacing M between two adjacent bridge plate rows 41 ranges from 0.8 mm to 1 mm. Preferably, when the spacing M between two adjacent bridge plate rows 41 is 1 mm, the fluid flow between the two adjacent bridge plate rows 41 can be smoother, thereby further reducing the energy loss of the fluid.

[0077] Furthermore, the spacing M between two adjacent bridge fin rows 41 is set to be no greater than the fourth parameter value. If the spacing M between two adjacent bridge fin rows 41 is greater than the fourth parameter value, the contact area between the fluid and the fins 1 will be reduced, which is not conducive to heat exchange and will lead to a decrease in the heat exchange efficiency of the heat exchanger 100.

[0078] The fourth parameter value can be 2mm to 2.5mm. Preferably, the fourth parameter value can be 2mm. When the distance M between two adjacent bridge fin rows 41 is 2mm, the contact area between the fluid and the fin 1 is large, which facilitates heat exchange in the heat exchanger 100.

[0079] The spacing M between two adjacent bridge fin rows 41 can range from 1 mm to 2 mm. For example, the spacing M between two adjacent bridge fin rows 41 can be set to 1 mm, 1.2 mm and 1.4 mm. Preferably, if the spacing M between two adjacent bridge fin rows 41 is 1 mm, the fluid can be in full contact with the fins 1 and the obstruction of the fluid can be avoided, thereby increasing the heat exchange area of ​​the heat exchanger 100.

[0080] According to some embodiments of this utility model, such as Figure 6 As shown, the bridge plate 42 includes a first sidewall 421, a second sidewall 422, and a top wall 423. The first sidewall 421 is inclinedly disposed on one side of the through hole 43, and the second sidewall 422 is inclinedly disposed on the other side of the through hole 43. The second sidewall 422 is disposed at intervals from the first sidewall 421 in the length direction of the fin strip 11. The top wall 423 is connected to the top of the first sidewall 421 and the second sidewall 422.

[0081] The first sidewall 421, the second sidewall 422, and the top wall 423 can form through holes 43 on the fin strip 11. This creates multiple through holes 43 around the heat exchange tube 2, allowing heat from the heat exchange tube 2 to dissipate through these holes, thereby improving heat dissipation efficiency. The through holes 43 can also disrupt the flow boundary layer, thus increasing heat transfer.

[0082] According to some embodiments of this utility model, such as Figure 7 As shown, the height of the first sidewall 421 and the second sidewall 422 is H, and H satisfies the relationship: 0.3mm≤H≤1mm.

[0083] Specifically, the height H of the first sidewall 421 and the second sidewall 422 is set to be no less than the fifth parameter value. If the height H of the first sidewall 421 and the second sidewall 422 is less than the fifth parameter value, the height of the through hole 43 will be lower, failing to disrupt the flow boundary layer and reducing heat transfer efficiency. Therefore, the height of the first sidewall 421 and the second sidewall 422 is set to be no less than the fifth parameter value.

[0084] The fifth parameter value can be set to 0.1mm-0.3mm. Preferably, the fifth parameter value can be set to 0.3mm. When the height H of the first sidewall 421 and the second sidewall 422 is 0.3mm, it can just break the flow boundary layer and allow the heat exchange tube 2 to dissipate heat, thereby ensuring the heat dissipation efficiency of the heat exchange tube 2.

[0085] The height H of the first sidewall 421 and the second sidewall 422 ranges from 0.3 mm to 0.8 mm. Preferably, when the height H of the first sidewall 421 and the second sidewall 422 is 0.8 mm, the heat exchange tube 2 can dissipate heat fully through the through hole 43, thereby further increasing the heat transfer rate.

[0086] Furthermore, the height H of the first sidewall 421 and the second sidewall 422 is set not to be greater than the sixth parameter value. If the height H of the first sidewall 421 and the second sidewall 422 is greater than the sixth parameter value, it will reduce the disturbance to the fluid, which is not conducive to breaking the boundary layer effect, thereby reducing the heat transfer efficiency. Therefore, the height of the first sidewall 421 and the second sidewall 422 is set not to be greater than the sixth parameter value.

[0087] The sixth parameter value can be 1mm to 2mm. Preferably, the sixth parameter value can be 1mm. When the height H of the first sidewall 421 and the second sidewall 422 is 1mm, the boundary layer effect can be destroyed, thereby ensuring the heat transfer effect of the heat exchanger 100.

[0088] The height H of the first sidewall 421 and the second sidewall 422 ranges from 0.8 mm to 1 mm. Preferably, if the height H of the first sidewall 421 and the second sidewall 422 is 0.9 mm, the fluid can be disturbed, the turbulence intensity can be increased, and the heat exchange efficiency can be further improved.

[0089] Furthermore, such as Figure 6 As shown, the angle between the first sidewall 421 and the fin strip 11 and the angle between the second sidewall 422 and the fin strip 11 are both α, and α satisfies the relationship: 30°≤α≤60°.

[0090] Specifically, the angle α between the first sidewall 421 and the fin 11 and the second sidewall 422 and the fin 11 is set to be no less than the seventh parameter value. If the angle α between the first sidewall 421 and the fin 11 and the second sidewall 422 and the fin 11 is less than the seventh parameter value, the flow boundary layer cannot be broken, resulting in reduced heat transfer efficiency. Therefore, the angle between the first sidewall 421 and the fin 11 and the second sidewall 422 and the fin 11 must not be less than the seventh parameter value.

[0091] The seventh parameter value can be set to 10°-30°. Preferably, the seventh parameter value can be set to 30°mm. When the angle between the first sidewall 421 and the fin strip 11 and the angle α between the second sidewall 422 and the fin strip 11 is 30°, the flow boundary layer can be broken and the heat exchange tube 2 can dissipate heat, thereby ensuring the heat dissipation efficiency of the heat exchange tube 2.

[0092] The angle between the first sidewall 421 and the fin strip 11 and the angle α between the second sidewall 422 and the fin strip 11 are in the range of 30°-45°. Preferably, when the angle between the first sidewall 421 and the fin strip 11 and the angle between the second sidewall 422 and the fin strip 11 are 45°, the heat exchange tube 2 can dissipate heat fully through the through hole 43, thereby further increasing the heat transfer rate.

[0093] Furthermore, the angle between the first sidewall 421 and the fin strip 11 and the angle α between the second sidewall 422 and the fin strip 11 should not be greater than the value of the eighth parameter. If the angle between the first sidewall 421 and the fin strip 11 and the angle between the second sidewall 422 and the fin strip 11 are greater than the value of the eighth parameter, it will reduce the disturbance to the fluid and will not be conducive to breaking the boundary layer effect, thereby reducing the heat transfer efficiency. Therefore, the angle between the first sidewall 421 and the fin strip 11 and the angle between the second sidewall 422 and the fin strip 11 should not be greater than the value of the eighth parameter.

[0094] The value of the eighth parameter can be 60° to 70°. Preferably, the value of the eighth parameter can be 60°. When the angle between the first sidewall 421 and the fin strip 11 and the angle α between the second sidewall 422 and the fin strip 11 is 60°, the boundary layer effect can be destroyed, thereby ensuring the heat transfer effect of the heat exchanger 100.

[0095] The angle between the first sidewall 421 and the fin strip 11 and the angle α between the second sidewall 422 and the fin strip 11 are in the range of 50° to 60°. Preferably, if the angle between the first sidewall 421 and the fin strip 11 and the angle α between the second sidewall 422 and the fin strip 11 are 50°, the fluid can be disturbed, the turbulence intensity can be increased, and the heat exchange efficiency can be further improved.

[0096] Also, such as Figure 7 As shown, the width of the first sidewall 421 and the second sidewall 422 is W, and W satisfies the relationship: 0.8mm≤W≤1.5mm.

[0097] The width W of the first sidewall 421 and the second sidewall 422 can be set to 0.8mm, 1mm and 1.5mm respectively. This can be set according to the width of the fin 1, which can increase the contact area between the fluid and the fin 1, thereby increasing the heat dissipation effect.

[0098] When the width W of the first sidewall 421 and the second sidewall 422 is less than 0.8mm, the width of the through hole 43 is small, which is not conducive to heat dissipation. Therefore, the width W of the first sidewall 421 and the second sidewall 422 should not be less than 0.8mm.

[0099] Furthermore, when the width W of the first sidewall 421 and the second sidewall 422 is greater than 1.5mm, the width W of the first sidewall 421 and the second sidewall 422 is relatively large, occupying a large area in the width direction of the fin 1, which makes it inconvenient to set other bridge pieces 42.

[0100] Also, such as Figure 4 As shown, the distance between the bottom ends of the first sidewall 421 and the second sidewall 422 is L1, and the length of the top wall 423 is L2. L1 and L2 satisfy the relationship: 1mm≤L2≤L1≤10mm.

[0101] The length L2 of the top wall 423 is less than the distance L1 between the bottom ends of the first side wall 421 and the second side wall 422. The distance L1 between the bottom ends of the first side wall 421 and the second side wall 422 can be set to 1.8mm, 4mm and 8mm. Correspondingly, the length L2 of the top wall 423 can be set to 0.6mm, 2mm and 5mm. In this way, the heat dissipation area can be increased, thereby accelerating heat transfer.

[0102] When the length L2 of the top wall 423 is less than 1 mm, it is not convenient to form the through hole 43. Therefore, the length L2 of the top wall 423 should not be less than 1 mm. When the distance L1 between the bottom ends of the first side wall 421 and the second side wall 422 is greater than 10 mm, it will lead to a decrease in fluid resistance and make heat dissipation difficult. Therefore, the distance L1 between the bottom ends of the first side wall 421 and the second side wall 422 should not be greater than 10 mm.

[0103] Among them, the flow field comparison between fin 1 in heat exchanger 100 and conventional fins is as follows: Figure 10 It can be clearly seen that the high-speed zone of the fin 1 of this utility model is more widely distributed, and the heat transfer coefficient outside the tube is increased by 1.5% compared with conventional fins.

[0104] like Figure 11 As shown, a comparison of the temperature fields of the fin 1 of this invention and conventional fins clearly shows that the low-temperature zone of the fin 1 of this invention is wider. This indicates that under the same inlet flow rate, due to the better heat exchange effect of the fin 1 of this invention, more heat can be removed, resulting in a lower temperature of the fin body. Ultimately, this leads to a 1.9% increase in heat exchange capacity of the fin 1 of this invention compared to conventional fins.

[0105] An air conditioner according to a second aspect of the present invention includes: the heat exchanger 100 described in the above embodiment.

[0106] 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.

[0107] 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.

[0108] In some embodiments, the outdoor heat exchanger further includes heat exchange 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.

[0109] 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.

[0110] 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.

[0111] 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.

[0112] 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.

[0113] In some embodiments, the indoor heat exchanger further includes heat exchange 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.

[0114] The indoor fan is configured to draw indoor air into the indoor unit through the third air inlet and discharge the air, after heat exchange with the indoor heat exchanger, through the fourth air outlet. The indoor fan provides power for the airflow. In the description of this utility model, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential," indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing this utility model and simplifying the description. They 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.

[0115] 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.

[0116] 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 three bridge plates spaced apart along the length direction of the fin strip. The bridge plates protrude from the side of the fin strip facing the thickness direction of the fin. The bridge plate area has through holes formed at the positions corresponding to the bridge plates. In each bridge section, at least three bridge pieces of at least one bridge piece row are partially staggered with at least three bridge pieces of another bridge piece row in the width direction of the fin strip.

2. The heat exchanger according to claim 1, characterized in that, The plurality of bridge plate rows include: End bridge strips, wherein the end bridge strips are located at both ends of the fin strip in the width direction; A middle bridge plate row, located between the end bridge plate rows at both ends, wherein at least three bridge plates of the middle bridge plate row are at least partially staggered from the at least three bridge plates of the end bridge plate rows in the width direction of the fin strip.

3. The heat exchanger according to claim 2, characterized in that, The central bridge plate row consists of at least two sections, and the at least three bridge plates of two adjacent central bridge plate rows are arranged opposite each other in the width direction of the fin strip.

4. The heat exchanger according to claim 2, characterized in that, The number of bridge pieces in the end bridge piece row is greater than the number of bridge pieces in the middle bridge piece row.

5. The heat exchanger according to claim 2, characterized in that, The end bridge strips at both ends are symmetrical about the centerline of the fin strip extending along its length.

6. The heat exchanger according to claim 1, characterized in that, In each of the bridge plates, the spacing between two adjacent bridge plates is S, and S satisfies the relationship: 0.2mm≤S≤2mm.

7. The heat exchanger according to claim 1, characterized in that, Within each bridge section area, the spacing between two adjacent bridge sections is M, where M satisfies the following relationship: 0.8mm ≤ M ≤ 2mm.

8. The heat exchanger according to claim 1, characterized in that, The bridge plate includes: A first sidewall is inclinedly disposed on one side of the through hole; The second sidewall is inclinedly disposed on the other side of the through hole and is spaced apart from the first sidewall in the length direction of the fin strip; A top wall, which is connected to the top of the first side wall and the second side wall.

9. The heat exchanger according to claim 8, characterized in that, The height of both the first sidewall and the second sidewall is H, where H satisfies the following relationship: 0.3mm ≤ H ≤ 1mm; and / or The angle between the first sidewall and the fin strip and the angle between the second sidewall and the fin strip are both α, where α satisfies the relationship: 30°≤α≤60°; and / or The widths of the first sidewall and the second sidewall are W, where W satisfies the following relationship: 0.8mm ≤ W ≤ 1.5mm; and / or The distance between the bottom ends of the first sidewall and the second sidewall is L1, and the length of the top wall is L2. L1 and L2 satisfy the relationship: 1mm≤L2≤L1≤10mm.

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

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