Heat exchanger of duct type air conditioner and duct type air conditioner

Abstract

The heat exchanger is provided with a windward side and a leeward side, the heat exchanger comprises a heat exchange tube, the heat exchanger comprises a first part and a second part, the first part is located above the second part, the first part comprises an inclined part, and the inclined part is located above the first part. The inclined part obliquely extends towards the leeward side from top to bottom, and the second part obliquely extends towards the windward side from top to bottom; the inclination angle of the inclined part is A, the inclination angle of the second part is B, and the heat exchanger meets the condition that A is larger than B. Therefore, the inclination angle A of the inclination part is larger than the inclination angle B of the second part, so that the opening area of the opening, jointly defined by the first part and the second part, of the heat exchanger is large, it is guaranteed that the flow speed of airflow capable of flowing into the heat exchanger is large, and the heat exchange efficiency of the airflow and the heat exchanger is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of air duct machines, and in particular to a heat exchanger of an air duct machine and an air duct machine. Background Art

[0002] The air duct machine is installed on the roof of a room. In order to improve the versatility of the air duct machine to match various situations such as different storey heights and different house types, for example, in the related art, it is required that the expansion height of the heat exchanger be reduced from 1135 mm to 935 mm. However, since the reduction of the expansion height of the heat exchanger will affect the heat exchange capacity of the heat exchanger, resulting in a decrease in the heat exchange capacity of the heat exchanger and a low heat exchange efficiency of the heat exchanger, the cooling / heating effect of the air duct machine cannot well meet the user's needs. Summary of the Invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a heat exchanger of an air duct machine, and the heat exchanger has a large open area and a high flow velocity of the air flow flowing into the heat exchanger, thereby improving the heat exchange effect between the air flow and the heat exchanger.

[0004] A heat exchanger of an air duct machine, the heat exchanger has a windward side and a leeward side, the heat exchanger includes heat exchange tubes, the heat exchanger includes a first part and a second part, the first part is located above the second part, the first part includes an inclined part, the inclined part extends obliquely towards the leeward side in the direction from top to bottom, and the second part extends obliquely towards the windward side in the direction from top to bottom; the inclination angle of the inclined part is A, and the inclination angle of the second part is B, wherein the heat exchanger satisfies: A > B.

[0005] According to the heat exchanger of the air duct machine of the present invention, by making the inclination angle A of the inclined part greater than the inclination angle B of the second part, the opening area of the opening of the heat exchanger jointly defined by the first part and the second part is large, ensuring that the flow velocity of the air flow that can flow into the heat exchanger is high, thereby facilitating the improvement of the heat exchange efficiency between the air flow and the heat exchanger.

[0006] According to some embodiments of the present invention, the heat exchanger satisfies: 1.02 ≤ A / B ≤ 1.31.

[0007] According to some embodiments of the present invention, in the direction from the windward side to the leeward side, the width of the inclined part is P1, and the width of the second part is P2, wherein P1 > P2.

[0008] According to some embodiments of the present invention, the heat exchanger satisfies: 1.02 ≤ P1 / P2 ≤ 1.45.

[0009] According to some embodiments of the present invention, the first part further includes a transition part, which is formed in an arc shape. The upper end of the transition part is connected to the inclined part, and the lower end of the transition part is connected to the second part.

[0010] According to some embodiments of the present invention, both the first part and the second part are provided with multiple rows of heat exchange tubes. The number of rows of the heat exchange tubes in the first part is greater than that in the second part; in the same vertical plane, the number of the heat exchange tubes in the first part is N1, and the number of the heat exchange tubes in the second part is N2. The heat exchanger satisfies the following relationship: 1.5 ≤ N1 / N2 ≤ 1.9.

[0011] According to some embodiments of the present invention, the heat exchanger satisfies: 1.6 ≤ N1 / N2 ≤ 1.8.

[0012] According to some embodiments of the present invention, the heat exchanger further includes heat exchange fins, and the heat exchange tubes pass through the heat exchange fins; in the first part or the second part, the distance between the center of the heat exchange tube on the windward side and the edge of the heat exchange fin is L1; the distance between the center of the heat exchange tube on the leeward side and the edge of the heat exchange fin is L2, where L1 is greater than L2.

[0013] According to some embodiments of the present invention, the heat exchanger satisfies the following relationship: 1.2 ≤ L1 / L2 ≤ 1.45.

[0014] According to some embodiments of the present invention, adjacent heat exchange fins are provided with an air flow space, and at least a part of the heat exchange fins are provided with air flow channels penetrating through them in the thickness direction. The air flow channels are communicated with the air flow space; the heat exchange tube closest to the windward side is defined as the first row of heat exchange tubes, and the heat exchange tube closest to the leeward side is defined as the last row of heat exchange tubes. The number of the air flow channels corresponding to the first row of heat exchange tubes is greater than the number of the air flow channels corresponding to the last row of heat exchange tubes.

[0015] According to some embodiments of the present invention, the number of the air flow channels corresponding to the first row of heat exchange tubes in the first part is greater than the number of the air flow channels corresponding to the first row of heat exchange tubes in the second part.

[0016] According to some embodiments of the present invention, the air flow channel includes a first air flow channel, and the heat exchange fin includes: a body part, the body part includes a plurality of through holes for passing through the heat exchange tubes; the body part includes at least one group of first spoiler groups, each group of first spoiler groups includes a plurality of louvers, each louver is connected to the body part, and the adjacent louvers define the first air flow channel.

[0017] According to some embodiments of the present invention, the air flow channel further includes a second air flow channel, and the heat exchange fins further include at least one group of second flow disturbing groups. Each group of the second flow disturbing groups includes a plurality of spaced bridge pieces, and each bridge piece defines the second air flow channel with the body portion.

[0018] According to some embodiments of the present invention, the number of the first flow disturbing groups in the first row of heat exchange tubes is greater than the number of the first flow disturbing groups in the last row of heat exchange tubes, or the number of the first flow disturbing groups in the first row of heat exchange tubes located in the first part is greater than the number of the first flow disturbing groups in the first row of heat exchange tubes located in the second part.

[0019] Another object of the present invention is to provide an air duct machine.

[0020] An air duct machine includes: a heat exchanger, which is the above-mentioned heat exchanger; a driving fan, and the air outlet of the driving fan is arranged towards the windward side of the heat exchanger.

[0021] The air duct machine has the same advantages as the above-mentioned heat exchanger, which will not be elaborated herein one by one.

[0022] According to some embodiments of the present invention, the driving fan is a centrifugal fan.

[0023] According to some embodiments of the present invention, the bottom wall of the air outlet extends obliquely downward towards the heat exchanger, and the extension line of the bottom wall of the air outlet passes through the second part.

[0024] The additional aspects and advantages of the present invention will be partially given in the following description, partially become obvious from the following description, or be understood through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The above and / or additional aspects and advantages of the present invention will become obvious and easy to understand from the description of the embodiments in conjunction with the following drawings, in which:

[0026] Figure 1 is a schematic structural diagram of the heat exchanger according to the embodiment of the present invention Figure 1 ;

[0027] Figure 2 is a schematic structural diagram of the heat exchanger according to the embodiment of the present invention Figure 2 ;

[0028] Figure 3 is a schematic structural diagram of the heat exchanger according to the embodiment of the present invention Figure 3 ;

[0029] Figure 4 is a schematic diagram of the air flow distribution when the air flow flows towards the heat exchanger according to the embodiment of the present invention;

[0030] Figure 5 Schematic diagram of the relationship between the ratio of the width P1 of the first part to the width P2 of the second part described in the embodiments of the present invention and the heat exchange amount of the heat exchanger;

[0031] Figure 6 Schematic diagram of the relationship between the ratio of the inclination angle A of the inclined part to the inclination angle B of the second part described in the embodiments of the present invention and the heat exchange amount of the heat exchanger;

[0032] Figure 7 Schematic diagram of the relationship between the ratio of L1 to L2 described in the embodiments of the present invention and the heat exchange amount of the heat exchanger;

[0033] Figure 8 Schematic diagram of the relationship between the ratio of the number N1 of heat exchange tubes in the first part to the number N2 of heat exchange tubes in the second part described in the embodiments of the present invention and the heat exchange amount of the heat exchanger;

[0034] Figure 9 Schematic diagram of the structure of the heat exchanger described in the embodiments of the present invention Figure 4 ;

[0035] Figure 10 Schematic diagram of the structure of the heat exchanger described in the embodiments of the present invention Figure 5 ;

[0036] Figure 11 Schematic diagram of the structure of the heat exchanger described in the embodiments of the present invention Figure 6 ;

[0037] Figure 12 Schematic diagram of the structure of the heat exchanger described in the embodiments of the present invention Figure 7 ;

[0038] Figure 13 Schematic diagram of the structure of the heat exchanger described in the embodiments of the present invention Figure 8 ;

[0039] Figure 14 Schematic diagram of the structure of the heat exchanger described in the embodiments of the present invention Figure 9 ;

[0040] Figure 15 Schematic diagram of the structure of the heat exchanger described in the embodiments of the present invention Figure 10 ;

[0041] Figure 16 Cross-sectional view of the main body part in the thickness direction at the first spoiler group described in the embodiments of the present invention;

[0042] Figure 17 Cross-sectional view of the main body part in the thickness direction at the second spoiler group described in the embodiments of the present invention;

[0043] Figure 18 Structural schematic of the air duct machine according to the embodiment of the present invention Figure 1 ;

[0044] Figure 19 Structural schematic of the air duct machine according to the embodiment of the present invention Figure 2 。

[0045] Reference numerals:

[0046] Heat exchanger 100, windward side 101, leeward side 102,

[0047] First part 103, inclined part 1031, transition part 1032, second part 104,

[0048] Heat exchange tubes 110, first row of heat exchange tubes 111, last row of heat exchange tubes 112, second row of heat exchange tubes 113,

[0049] Heat exchange fins 120, main body part 121,

[0050] Air flow channels 122, first air flow channel 1221, second air flow channel 1222,

[0051] First surface 123, upper surface 1231, lower surface 1232,

[0052] First region 131, second region 132, third region 133, fourth region 134, fifth region 135,

[0053] First spoiler group 140, louvers 141, end louvers 1411, intermediate louvers 1412,

[0054] Second spoiler group 150, bridge pieces 151,

[0055] Air duct machine 1000, driving fan 200, air outlet 210, bottom wall 211, top wall 212,

[0056] Air outlet opening 300, lower wall surface 400, upper wall surface 500, partition 600. Detailed implementation manners

[0057] The embodiments of the present invention will be described in detail below. Examples of the embodiments are shown in the accompanying drawings, where the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described by referring to the accompanying drawings are exemplary and are only used to explain the present invention and should not be construed as a limitation to the present invention.

[0058] In the description of the present invention, it should be understood that the orientation or positional relationships indicated by terms such as "length", "width", "thickness", "vertical", "horizontal", "circumferential", etc. are based on the orientation or positional relationships shown in the drawings. These are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation to the present invention. In addition, features defined as "first", "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise stated, the meaning of "a plurality" is two or more.

[0059] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "mounted", "connected", "coupled" shall be construed in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0060] The following refers to Figures 1 - 19 Describe the heat exchanger 100 and the air duct unit 1000 according to an embodiment of the present invention.

[0061] Combined with Figures 1 to 3 , for the heat exchanger 100 of the air duct unit 1000 according to an embodiment of the present invention, the heat exchanger 100 has a windward side 101 and a leeward side 102. The heat exchanger 100 includes heat exchange tubes 110. The heat exchanger 100 includes a first part 103 and a second part 104. The first part 103 is located above the second part 104. The first part 103 includes an inclined part 1031. The inclined part 1031 extends obliquely towards the leeward side 102 in the direction from top to bottom. The second part 104 extends obliquely towards the windward side 101 in the direction from top to bottom; the inclination angle of the inclined part 1031 is A, and the inclination angle of the second part 104 is B, where the heat exchanger 100 satisfies: A > B.

[0062] Specifically, the air flow enters the heat exchanger 100 from the windward side 101 and exchanges heat with the heat exchange tubes 110. After heat exchange, the air flow flows out of the heat exchanger 100 from the leeward side 102. The heat exchanger 100 includes a first part 103 and a second part 104. The first part 103 is connected to the second part 104, and the first part 103 is located above the second part 104. The first part 103 includes an inclined part 1031. In the direction from top to bottom, the inclined part 1031 extends obliquely from the windward side 101 towards the leeward side 102. The second part 104 extends obliquely from the leeward side 102 towards the windward side 101. The inclined part 1031 and the second part 104 are arranged at an angle. The first part 103 and the second part 104 together define an opening that is open towards the windward side 101, and the air flow can enter the heat exchanger 100 through the opening.

[0063] Furthermore, the inclined part 1031 is arranged at an angle with respect to the horizontal line, and this angle is defined as the inclination angle A of the inclined part 1031. The second part 104 is arranged at an angle with respect to the horizontal line, and this angle is defined as the inclination angle B of the second part 104. By making A > B, the opening area of the opening jointly defined by the first part 103 and the second part 104 is large, ensuring that the flow rate of the air flow that can enter the heat exchanger 100 is large, and being able to match the air flow velocity distribution of the air flow flowing towards the heat exchanger 100 in the air duct machine 1000, thereby being beneficial to improving the heat exchange efficiency between the air flow and the heat exchanger 100.

[0064] For the heat exchanger 100 of the air duct machine 1000 according to the present invention, by making the inclination angle A of the inclined part 1031 greater than the inclination angle B of the second part 104, the opening area of the opening of the heat exchanger 100 jointly defined by the first part 103 and the second part 104 is large, ensuring that the flow rate of the air flow that can enter the heat exchanger 100 is large, thereby being beneficial to improving the heat exchange efficiency between the air flow and the heat exchanger 100.

[0065] Combined Figure 2 、 Figure 3 and Figure 6 In some embodiments of the present invention, the heat exchanger 100 satisfies: 1.02 ≤ A / B ≤ 1.31.

[0066] Specifically, by making the inclination angle A of the inclined part 1031 and the inclination angle B of the second part 104 satisfy 1.02 ≤ A / B ≤ 1.31, through testing, it is known that when the heat exchanger 100 satisfies 1.02 ≤ A / B ≤ 1.31, the heat exchange amount of the heat exchanger 100 is within the optimal range, that is, the heat exchange performance of the heat exchanger 100 is in the optimal interval, effectively ensuring the heat exchange capacity of the heat exchanger 100 and enabling the heat exchanger 100 to achieve efficient heat exchange.

[0067] It can be understood that when A / B < 1.02 or A / B > 1.31, the heat transfer amount of the heat exchanger 100 is less than that when 1.02 ≤ A / B ≤ 1.31 for the heat exchanger 100, and the heat transfer capacity is poor. In some embodiments of the present invention, 1.1 ≤ A / B ≤ 1.3 can further improve the heat transfer efficiency of the heat exchanger 100.

[0068] Combined with Figures 1 to 3 , in some embodiments of the present invention, in the direction from the windward side 101 to the leeward side 102, the width of the inclined portion 1031 is P1, and the width of the second portion 104 is P2, where P1 > P2.

[0069] Specifically, the dimension of the inclined portion 1031 in the direction extending from the windward side 101 to the leeward side 102 is defined as the width dimension P1 of the inclined portion 1031, and the dimension of the second portion 104 in the direction extending from the windward side 101 to the leeward side 102 is defined as the width dimension P2 of the second portion 104. P1 and P2 satisfy P1 = P2 * Sin(B) / Sin(A). Preferably, the width dimension of the inclined portion 1031 is greater than the width dimension of the second portion 104, which is beneficial to making the number of rows of the heat exchange tubes 110 in the inclined portion 1031 greater than the number of rows of the heat exchange tubes 110 in the second portion 104, increasing the heat exchange area, improving the heat transfer capacity of the inclined portion 1031, and thus improving the heat transfer capacity of the first portion 103.

[0070] Combined with Figures 1 to 3 and Figure 5 , in some embodiments of the present invention, the heat exchanger 100 satisfies: 1.02 ≤ P1 / P2 ≤ 1.45.

[0071] Specifically, the width dimension P1 of the inclined portion 1031 and the width dimension P2 of the second portion 104 satisfy 1.02 ≤ P1 / P2 ≤ 1.45. Through testing, it is known that when the heat exchanger 100 satisfies 1.02 ≤ P1 / P2 ≤ 1.45, the heat transfer amount of the heat exchanger 100 is within the optimal range, that is, the heat transfer performance of the heat exchanger 100 is within the optimal interval, effectively improving the heat transfer capacity of the heat exchanger 100 and enabling the heat exchanger 100 to achieve efficient heat transfer.

[0072] When P1 / P2 < 1.02 or P1 / P2 > 1.45, the heat transfer amount of the heat exchanger 100 is small and the heat transfer capacity is poor. In some embodiments of the present invention, 1.1 ≤ P1 / P2 ≤ 1.3 can further improve the heat transfer efficiency of the heat exchanger 100.

[0073] Such as Figure 1As shown, in some embodiments of the present invention, the first part 103 further includes a transition part 1032. The transition part 1032 is formed in an arc shape. The upper end of the transition part 1032 is connected to the inclined part 1031, and the lower end of the transition part 1032 is connected to the second part 104.

[0074] Specifically, one end of the transition part 1032 is connected to the end of the inclined part 1031 relatively close to the leeward side 102, and the other end of the transition part 1032 is connected to the end of the second part 104 relatively close to the leeward side 102. In the direction extending from the leeward side 102 to the windward side 101, the spacing between the inclined part 1031 and the second part 104 in the vertical direction gradually increases. When the air flow flows to the heat exchanger 100 and impacts the windward end of the heat exchanger 100, the windward ends of the inclined part 1031 and the second part 104 located on the windward side 101 can guide the air flow, preventing the air flow from diverging outward after hitting the heat exchanger 100, that is, reducing the air flow escaping from the end of the heat exchanger 100, improving the effect of the air flow flowing to the heat exchanger 100, thereby ensuring the heat exchange effect of the air flow and improving the working efficiency of the heat exchanger 100.

[0075] In addition, constructing the transition part 1032 as an arc shape can effectively reduce the resistance generated by the heat exchanger 100 to the air flow and reduce turbulence.

[0076] As Figure 1 shown, in some embodiments of the present invention, both the first part 103 and the second part 104 are provided with multiple rows of heat exchange tubes 110. The number of rows of the heat exchange tubes 110 in the first part 103 is greater than the number of rows of the heat exchange tubes 110 in the second part 104; in the same vertical plane, the number of the heat exchange tubes 110 in the first part 103 is N1, and the number of the heat exchange tubes 110 in the second part 104 is N2. The heat exchanger 100 satisfies the following relationship: 1.5 ≤ N1 / N2 ≤ 1.9.

[0077] Specifically, in the cross-section in the width direction of the first part 103, the first part 103 is provided with multiple rows of heat exchange tubes 110. In the cross-section in the width direction of the second part 104, the second part 104 is provided with multiple rows of heat exchange tubes 110, and the number of rows of the heat exchange tubes 110 in the first part 103 is greater than the number of rows of the heat exchange tubes 110 in the second part 104, so that the heat exchange efficiency of the first part 103 is greater than the heat exchange efficiency of the second part 104.

[0078] Further, in the same vertical plane, the number of heat exchange tubes 110 in the first part 103 is greater than the number of heat exchange tubes 110 in the second part 104, that is, the density of the heat exchange tubes 110 in the first part 103 is greater than the density of the heat exchange tubes 110 in the second part 104, so as to effectively improve the heat exchange efficiency of the first part 103. Since the air flow flowing into the first part 103 has a higher flow rate than the air flow flowing into the second part 104, by making the density of the heat exchange tubes 110 in the first part 103 greater than the density of the heat exchange tubes 110 in the second part 104, it can be effectively ensured that the first part 103 can fully exchange heat with the air flow flowing into it, so that the heat exchange capacity of the first part 103 can match the flow rate of the air flow flowing into the first part 103, ensuring the heat exchange effect of the first part 103 on the air flow, and thus ensuring the heat exchange effect of the heat exchanger 100.

[0079] Among them, the number N1 of the heat exchange tubes 110 in the first part 103 and the number N2 of the heat exchange tubes 110 in the second part 104 in the same vertical plane satisfy 1.5 ≤ N1 / N2 ≤ 1.9, so as to ensure the heat exchange effect of the first part 103 on the air flow while effectively increasing the overall heat exchange amount of the heat exchanger 100, improving the heat exchange effect of the heat exchanger 100, and enabling the heat exchanger 100 to achieve efficient heat exchange.

[0080] When N1 / N2 < 1.5, the overall heat exchange amount of the heat exchanger 100 is small, resulting in a poor heat exchange effect of the heat exchanger 100, and the heat exchange capacities of the first part 103 and the second part 104 are relatively close, which easily leads to the mismatch between the heat exchange capacities of the first part 103 and the second part 104 and the flow rates of the air flows flowing into them respectively, so that the first part 103 cannot fully exchange heat with the air flow flowing into it, or the heat exchange capacity of the second part 104 is too large, increasing the energy consumption of the heat exchanger 100.

[0081] When N1 / N2 > 1.9, the overall heat exchange amount of the heat exchanger 100 decreases, resulting in a poor heat exchange effect of the heat exchanger 100, and the difference in the number of the heat exchange tubes 110 between the first part 103 and the second part 104 is too large, and the heat exchange capacities of the first part 103 and the second part 104 are mismatched with the flow rates of the air flows flowing into them respectively, which easily leads to too large a heat exchange capacity of the first part 103, increasing the energy consumption of the heat exchanger 100, and the air resistance of the first part 103 is too large, affecting the heat exchange effect of the first part 103; the second part 104 cannot fully exchange heat with the air flow flowing into it, affecting the heat exchange effect of the heat exchanger 100.

[0082] As Figure 8 shown, in some embodiments of the present invention, the heat exchanger 100 satisfies: 1.6 ≤ N1 / N2 ≤ 1.8.

[0083] Specifically, the number N1 of the heat exchange tubes 110 in the first part 103 and the number N2 of the heat exchange tubes 110 in the second part 104 on the same vertical plane satisfy 1.6 ≤ N1 / N2 ≤ 1.8. Through testing, it is known that when the heat exchanger 100 satisfies 1.6 ≤ N1 / N2 ≤ 1.8, the heat exchange capacity of the heat exchanger 100 is within the optimal range, that is, the heat exchange performance of the heat exchanger 100 is in the optimal interval, effectively ensuring the heat exchange capacity of the heat exchanger 100 and enabling the heat exchanger 100 to achieve efficient heat exchange.

[0084] Combined with Figure 1 and Figure 3 , in some embodiments of the present invention, the hole pitch between adjacent heat exchange tubes 110 in the same row of the first part 103 is C1, and the hole pitch between adjacent heat exchange tubes 110 in the same row of the second part 104 is C2, where C2 may be equal to C1.

[0085] Specifically, by making the hole pitch C1 between adjacent heat exchange tubes 110 in the same row of the first part 103 equal to the hole pitch C2 between adjacent heat exchange tubes 110 in the same row of the second part 104, at least some adjacent heat exchange tubes 110 can be connected by connecting tubes of the same specification (such as U-shaped tubes), which is convenient for the assembly of the heat exchanger 100; at the same time, it also makes the air resistance of the first part 103 and the second part 104 relatively uniform.

[0086] It should be noted that "the same row" refers to a plurality of heat exchange tubes 110 arranged in sequence along the extension direction of the heat exchanger 100.

[0087] As Figure 1 shown, in some embodiments of the present invention, the number of rows of the heat exchange tubes 110 in the inclined part 1031 is the same as the number of rows of the heat exchange tubes 110 in the transition part 1032.

[0088] Specifically, the number of heat exchange tubes 110 arranged in sequence along the width direction of the inclined part 1031 is defined as the number of rows of the heat exchange tubes 110 in the inclined part 1031. Similarly, the number of heat exchange tubes 110 arranged in sequence along the width direction of the transition part 1032 is defined as the number of rows of the heat exchange tubes 110 in the transition part 1032. The number of rows of the heat exchange tubes 110 in the inclined part 1031 is the same as the number of rows of the heat exchange tubes 110 in the transition part 1032, so that the heat exchange capacity of the inclined part 1031 is the same as the heat exchange capacity of the transition part 1032, which is beneficial to ensuring the uniform heat exchange effect of the first part 103 on the air flow.

[0089] Combined with Figure 1 and Figure 2, in some embodiments of the present invention, the heat exchanger 100 further includes heat exchange fins 120, and the heat exchange tubes 110 are disposed through the heat exchange fins 120; in the first part 103 or the second part 104, the distance between the center of the heat exchange tube 110 on the windward side 101 and the edge of the heat exchange fin 120 is L1; the distance between the center of the heat exchange tube 110 on the leeward side 101 and the edge of the heat exchange fin 120 is L2, where L1 is greater than L2.

[0090] Specifically, a plurality of heat exchange fins 120 are provided. Along the direction extending from the leeward side 102 to the windward side 101, the distance between the heat exchange fins 120 of the inclined part 1031 and the heat exchange fins 120 of the second part 104 gradually increases in the vertical direction, and the heat exchange fins 120 located in the transition part 1032 are connected between the heat exchange fins 120 of the inclined part 1031 and the heat exchange fins 120 of the second part 104.

[0091] Meanwhile, a plurality of heat exchange fins 120 are arranged at intervals in the first direction. An air flow space is provided between adjacent heat exchange fins 120. Each heat exchange tube 110 is disposed through a plurality of heat exchange fins 120 in the first direction and is spaced from the outer edge of the heat exchange fin 120. The heat exchange tube 110 can dissipate heat through the heat exchange fin 120. After the air flow enters the heat exchanger 100, it flows into the air flow space and contacts the heat exchange fin 120, so that the air flow can exchange heat with the heat exchange fin 120, and the heat-exchanged air flow flows out of the heat exchanger 100 from the leeward side 102. Among them, a plurality of heat exchange fins 120 can increase the heat exchange area of the heat exchange tube 110 and improve the heat exchange effect of the heat exchange tube 110 on the air flow.

[0092] It should be noted that the "first direction" is the thickness direction of the heat exchange fin 120.

[0093] Further, in the first part 103 or the second part 104, the distance between the center of the heat exchange tube 110 closest to the windward side 101 and the edge of the heat exchange fin 120 is L1, and the distance between the center of the heat exchange tube 110 closest to the leeward side 102 and the edge of the heat exchange fin 120 is L2. L1 is greater than L2, so that the area of the heat exchange fin 120 near the windward side 101 (i.e., the area between the center of the heat exchange tube 110 arranged near the windward side 101 and the edge of the heat exchange fin 120) is larger than the area of the heat exchange fin 120 near the leeward side 102 (i.e., the area between the center of the heat exchange tube 110 arranged near the leeward side 102 and the edge of the heat exchange fin 120). Since the temperature difference between the air flow and the heat exchanger 100 is large when the air flow flows in from the windward side 101, and the temperature difference between the air flow and the heat exchanger 100 gradually decreases when the air flow gradually flows to the leeward side 102, it is necessary to make the heat exchange efficiency of the heat exchanger 100 near the windward side higher than that of the heat exchanger 100 near the leeward side 102 to meet the heat exchange requirements of the air flow. By making the heat exchange area of the heat exchange fin 120 near the windward side 101 larger than the heat exchange area of the heat exchange fin 120 near the leeward side 102, the heat exchange effect of the heat exchanger 100 is ensured to meet the different heat exchange requirements of the air flow.

[0094] Optionally, the heat exchange fins 120 of the first part 103 and the heat exchange fins 120 of the second part 104 can be integrally formed and then bent into the above shape through subsequent processing for the processing and assembly of the heat exchanger 100; the heat exchange fins 120 of the inclined part 1031, the heat exchange fins 120 of the transition part 1032 and the heat exchange fins 120 of the second part 104 can also be separately arranged and then processed and assembled by splicing, which is beneficial to the disassembly, installation and maintenance of the heat exchanger 100; of course, it can be understood that the specific processing method of the heat exchanger 100 can be determined according to actual production and assembly and will not be specifically limited herein.

[0095] Combined with Figure 1 、 Figure 2 and Figure 7 In some embodiments of the present invention, the heat exchanger 100 satisfies the following relational expression: 1.2 ≤ L1 / L2 ≤ 1.45.

[0096] Specifically, in the first part 103 or the second part 104, the distance L1 between the center of the heat exchange tube 110 arranged near the windward side 101 and the edge of the heat exchange fin 120, and the distance L2 between the center of the heat exchange tube 110 arranged near the windward side 101 and the edge of the heat exchange fin 120 satisfy 1.2 ≤ L1 / L2 ≤ 1.45. Through testing, it is known that when L1 / L2 < 1.2 and L1 / L2 > 1.45, the heat exchange capacity of the heat exchanger 100 is smaller and the heat exchange ability is poorer compared to when the heat exchanger 100 satisfies 1.2 ≤ L1 / L2 ≤ 1.45. Therefore, when the heat exchanger 100 satisfies 1.2 ≤ L1 / L2 ≤ 1.45, the heat exchange capacity of the heat exchanger 100 is within the optimal range, that is, the heat exchange performance of the heat exchanger 100 is in the optimal interval, effectively improving the heat exchange ability of the heat exchanger 100 and enabling the heat exchanger 100 to achieve efficient heat exchange.

[0097] Combined with Figure 1 and Figure 15 As shown, in some embodiments of the present invention, an air flow space is provided between adjacent heat exchange fins 120, and at least a part of the heat exchange fins 120 are provided with air flow channels 122 penetrating through them in the thickness direction, and the air flow channels 122 communicate with the air flow space.

[0098] Specifically, a flow space is provided between every two adjacent heat exchange fins 120. After the air flow enters the air flow space, it comes into contact with the heat exchange fins 120, so that the air flow can exchange heat with the heat exchange fins 120.

[0099] Furthermore, the air flow channels 122 communicate with the air flow space. The air flow can flow from the air flow space on one side of the heat exchange fin 120 to the air flow space on the other side of the heat exchange fin 120 through the air flow channels 122. Compared with the air flow directly flowing through from one side air flow space, by providing the air flow channels 122, the length of the air flow path can be increased to improve the heat exchange effect between the air flow and the heat exchange fins 120.

[0100] Optionally, the air flow channels 122 can be provided on a part of the heat exchange fins 120 among multiple heat exchange fins 120 to facilitate the processing of the heat exchanger 100; or the air flow channels 122 can be provided on all the heat exchange fins 120 to improve the heat exchange ability of the heat exchanger 100. Of course, it can be understood that the number of heat exchange fins 120 provided with the air flow channels 122 can be determined according to the heat exchange requirements of the heat exchanger 100, and no specific limitation is made here.

[0101] Combined with Figure 1 and Figure 15, in some embodiments of the present invention, in the direction from the windward side 101 to the leeward side 102, the heat exchanger 100 is provided with multiple rows of heat exchange tubes 110, and multiple air flow channels 122 are correspondingly arranged for each row of heat exchange tubes 110; the heat exchange tube 110 closest to the windward side 101 is defined as the first row of heat exchange tubes 111, and the heat exchanger 100 closest to the leeward side 102 is defined as the last row of heat exchange tubes 112, and the number of air flow channels 122 corresponding to the first row of heat exchange tubes 111 is greater than the number of air flow channels 122 corresponding to the last row of heat exchange tubes 112.

[0102] Specifically, air flow channels 122 are provided on the heat exchange fins 120. The air flow channels 122 may include a first air flow channel 1221 and a second air flow channel 1222. At the same time, air flow spaces are provided on both sides of the heat exchange fins 120 in the first direction, and the air flow in the air flow spaces can flow through the first air flow channel 1221 and the second air flow channel 1222. The first air flow channel 1221 and the second air flow channel 1222 respectively form a first flow disturbance group 140 and a second flow disturbance group 150. The first flow disturbance group 140 and the second flow disturbance group 150 respectively play a role in disturbing the flow, increasing the flow time of the air flow in the heat exchanger 100, ensuring that the air flow can perform sufficient heat exchange, and improving the heat exchange effect of the heat exchanger 100 on the air flow.

[0103] The flow disturbance effect of the first flow disturbance group 140 may be better than that of the second flow disturbance group 150. For example, the number of air flow channels 122 in the first flow disturbance group 140 may be greater than the number of air flow channels 122 in the second flow disturbance group 150, or the opening manner of the air flow channels 122 in the first flow disturbance group 140 can interfere with the air flow direction more than the opening manner of the air flow channels 122 in the second flow disturbance group 150.

[0104] It should be noted that the "first direction" can be understood as the thickness direction of the heat exchange fins 120.

[0105] Furthermore, the heat exchanger 100 is provided with multiple rows of heat exchange tubes 110, and each row of heat exchange tubes 110 includes multiple heat exchange tubes 110 arranged at intervals along the extending direction of the heat exchange fins 120. Multiple air flow channels 122 are correspondingly arranged for each row of heat exchange tubes 110. The air flow channels 122 can be the first air flow channel 1221 or the second air flow channel 1222. Among them, multiple heat exchange tubes 110 arranged at intervals along the extending direction of the heat exchange fins 120 and closest to the windward side 101 are defined as the first row of heat exchange tubes 111, and multiple heat exchange tubes 110 arranged at intervals along the extending direction of the heat exchange fins 120 and closest to the windward side 101 are defined as the last row of heat exchange tubes 112.

[0106] After the air flow enters the heat exchanger 100, it preferentially flows through the first row of heat exchange tubes 111 for heat exchange. The temperature difference between the air flow and the first row of heat exchange tubes 111 is the largest. After the air flow exchanges heat with multiple rows of heat exchange tubes 110 in sequence, it flows towards the last row of heat exchange tubes 112, and the temperature difference between the air flow and the last row of heat exchange tubes 112 is the smallest. Since the flow disturbance effect of the first flow disturbance group 140 is better than that of the second flow disturbance group 150, the first flow disturbance group 140 can be correspondingly arranged for the first row of heat exchange tubes 111, and the second flow disturbance group 150 can be correspondingly arranged for the last row of heat exchange tubes 112, so as to improve the flow disturbance effect of the air flow channel 122 arranged corresponding to the first row of heat exchange tubes 111, increase the heat exchange time between the air flow and the first row of heat exchange tubes 111, improve the heat exchange effect of the first row of heat exchange tubes 111 on the air flow, and thus contribute to improving the heat exchange effect of the heat exchanger 100 on the air flow.

[0107] Combined with Figure 1 and Figure 15 , in some embodiments of the present invention, an air flow channel 122 is provided between any two adjacent heat exchange tubes 110 in each row of heat exchange tubes 110.

[0108] Specifically, each row of heat exchange tubes 110 includes a plurality of heat exchange tubes 110 arranged at intervals along the extending direction of the heat exchange fins 120. An air flow channel 122 is provided between two adjacent heat exchange tubes 110 arranged in each row of heat exchange tubes 110, so as to increase the number of air flow channels 122 corresponding to each row of heat exchange tubes 110, improve the flow disturbance effect of the air flow channels 122, and a flow disturbance is performed by providing an air flow channel 122 between any two adjacent heat exchange tubes 110, further increasing the heat exchange time between the air flow and each heat exchange tube 110, and enabling the air flow to fully exchange heat with each heat exchange tube 110 and the heat exchange fins 120, thereby improving the heat exchange effect of the heat exchanger 100 on the air flow.

[0109] Combined with Figure 1 and Figure 15 , in some embodiments of the present invention, multiple rows of air flow channels 122 are provided between any two adjacent heat exchange tubes 110 in the same row.

[0110] Specifically, each row of heat exchange tubes 110 includes a plurality of heat exchange tubes 110 arranged at intervals along the extending direction of the heat exchange fins 120. Multiple rows of air flow channels 122 are provided between any two adjacent heat exchange tubes 110 arranged in each row of heat exchange tubes 110, that is, at least one group of the first flow disturbance group 140 or the second flow disturbance group 150 is provided between any two adjacent heat exchange tubes 110, so as to further increase the number of air flow channels 122, improve the flow disturbance effect exerted by the air flow channels 122, further increase the time required for the air flow to flow through the heat exchange tubes 110 and the heat exchange fins 120, and improve the heat exchange effect of the heat exchanger 100 on the air flow.

[0111] In some embodiments of the present invention, the number of air flow channels 122 corresponding to the first row of heat exchange tubes 111 in the first part 103 is greater than the number of air flow channels 122 corresponding to the first row of heat exchange tubes 111 in the second part 104.

[0112] Specifically, since the air flow velocity flowing into the first part 103 in the air duct unit 1000 is greater than the air flow velocity flowing into the second part 104, by making the number of air flow channels 122 corresponding to the first row of heat exchange tubes 111 in the first part 103 greater than the number of air flow channels 122 corresponding to the first row of heat exchange tubes 111 in the second part 104, the turbulence effect of the air flow channels 122 provided corresponding to the first row of heat exchange tubes 111 in the first part 103 is improved, the heat exchange time between the air flow and the first row of heat exchange tubes 111 in the first part 103 is increased, so that the heat exchange effect between the first row of heat exchange tubes 111 in the first part 103 and the air flow is greater than the heat exchange effect between the first row of heat exchange tubes 111 in the second part 103 and the air flow, ensuring that the heat exchange capacity at different positions of the heat exchanger 100 is adapted to the characteristics of the air flow velocity.

[0113] As Figure 1 and Figure 15 shown, in some embodiments of the present invention, at least a part of the heat exchange tubes 110 are arranged in a staggered manner in the direction from the windward side 101 to the leeward side 102.

[0114] Specifically, a row of heat exchange tubes 110 between the first row of heat exchange tubes 111 and the last row of heat exchange tubes 112 is defined as the second row of heat exchange tubes 113. At least some of the heat exchange tubes 110 in two adjacent rows of heat exchange tubes 110 are arranged in a staggered manner in the direction from the windward side 101 to the leeward side 102. For example, at the position where the first row of heat exchange tubes 111 and the second row of heat exchange tubes 113 are adjacent in the extending direction from the windward side 101 to the leeward side 102, some of the heat exchange tubes 110 of the first row of heat exchange tubes 111 can be arranged in a staggered manner with some of the heat exchange tubes 110 of the second row of heat exchange tubes 113, so as to prevent the heat exchange tubes 110 behind the first row of heat exchange tubes 111 from being blocked in the direction from the windward side 101 to the leeward side 102, ensuring that the air flow can flow through the second row of heat exchange tubes 113 or the last row of heat exchange tubes 112 after flowing through the first row of heat exchange tubes 111, ensuring the heat exchange efficiency between the air flow and the heat exchange tubes 110, and improving the heat exchange effect of the heat exchanger 100 on the air flow.

[0115] It can be understood that in the direction from the windward side 101 to the leeward side 102, all the heat exchange tubes 110 can be arranged in a staggered manner to further ensure that the air flow can pass through all the heat exchange tubes 110, improving the heat exchange effect of the heat exchanger 100 on the air flow; in the direction from the windward side 101 to the leeward side 102, the heat exchange tubes 110 at both ends in the length direction of the heat exchange fins 120 can be arranged in a staggered manner. The specific arrangement manner of the heat exchange tubes 110 can be determined according to the air flow characteristics of the air flowing into the heat exchanger 100 and the heat exchange requirements of the heat exchanger 100, and no specific limitation is made here, as long as the heat exchange effect of the heat exchanger 100 on the air flow is ensured.

[0116] As Figure 1 and Figure 15 shown, in some embodiments of the present invention, at least a part of the heat exchange tubes 110 in each row of heat exchange tubes 110 are arranged opposite to the air flow channel 122 in the direction from the windward side 101 to the leeward side 102. The air flow channel 122 can cause turbulence to the air flow, increasing the time for the air flow to pass through the heat exchange fins 120 and the heat exchange tubes 110, and improving the heat exchange effect of this part of the air flow.

[0117] Furthermore, another part of the air flow passes through the air flow channel 122 and flows to the heat exchange tubes 110 in another row arranged opposite to the air flow channel 122, and this part of the air flow exchanges heat with the heat exchange tubes 110, enabling this part of the air flow to be fully heat-exchanged. Thus, the heat exchange effect of the heat exchanger 100 on the air flow can be effectively ensured, and the heat exchange amount of the heat exchanger 100 for the air flow can be increased.

[0118] Combined with Figure 15 and Figure 16 , in some embodiments of the present invention, the air flow channel 122 includes a first air flow channel 1221, and the heat exchange fins 120 include: a body portion 121, the body portion 121 includes a plurality of through holes for passing through the heat exchange tubes 110; the body portion 121 includes at least one group of first turbulence groups 140, each group of first turbulence groups 140 includes a plurality of louvers 141, each louver 141 is connected to the body portion 121, and a first air flow channel 1221 is defined between adjacent louvers 141.

[0119] Specifically, a plurality of spaced-apart through holes are provided on the body portion 121, and a plurality of heat exchange tubes 110 are arranged in one-to-one correspondence with the plurality of through holes. Each heat exchange tube 110 can pass through the heat exchange fins 120 through the through holes, and the heat exchange tubes 110 can exchange heat through the heat exchange fins 120. The heat exchange fins 120 can increase the heat exchange area of the heat exchange tubes 110, which is beneficial to improving the heat exchange effect of the heat exchange tubes 110.

[0120] Further, a first flow disturbing group 140 is provided on the body portion 121. The first flow disturbing group 140 includes a plurality of louvers 141 for disturbing the air flow. The louvers 141 are connected to the body portion 121 to ensure the stability of the louvers 141 and prevent the poor flow disturbing effect of the louvers 141 on the air flow due to the shaking of the louvers 141 when the air flow passes through the louvers 141.

[0121] A plurality of air flow channels 122 are formed on the body portion 121. The plurality of air flow channels 122 include a first air flow channel 1221 defined by the adjacent louvers 141. Each first air flow channel 1221 is arranged at intervals. When the air flow passes through the heat exchange fins 120, it can flow into the first air flow channel 1221 on one side of the heat exchange fins 120. The first air flow channel 1221 can increase the time for the air flow to pass through the heat exchange fins 120, so that the air flow can fully exchange heat with the heat exchange fins 120, which is beneficial to improving the heat exchange effect of the heat exchange tube 110 on the air flow, thereby improving the heat exchange performance of the heat exchanger 100.

[0122] Optionally, multiple groups of the first flow disturbing group 140 can be provided. For example, 2 groups, 3 groups or 4 groups of the first flow disturbing group 140 can be provided. The multiple groups of the first flow disturbing group 140 are arranged at intervals on the body portion 121, which is beneficial to further improving the heat exchange effect between the heat exchange fins 120 and the air flow, thereby further improving the heat exchange performance of the heat exchanger 100. It can be understood that the number of the first flow disturbing group 140 can be determined according to the heat exchange requirements of the heat exchanger 100, and no specific limitation is made here.

[0123] In the related art, the heat exchange time between the air flow and the fins is short, and the air flow cannot fully exchange heat, resulting in poor heat exchange effect of the fins on the air flow and low heat utilization rate of the heat exchange tube, reducing the heat exchange performance of the heat exchanger.

[0124] In this application, by providing the first flow disturbing group 140 on the heat exchange fins 120, the time for the air flow to pass through the heat exchange fins 120 and the heat exchange tube 110 is increased, the heat utilization rate of the heat exchange tube 110 is improved, and the air flow can fully exchange heat, improving the heat exchange performance of the heat exchanger 100. Moreover, the first flow disturbing group 140 also has the effect of reducing noise.

[0125] In some embodiments of the present invention, the number of the first flow disturbing group 140 in the first row of heat exchange tubes 111 is greater than the number of the first flow disturbing group 140 in the last row of heat exchange tubes 112, or the number of the first flow disturbing group 140 in the first row of heat exchange tubes 111 in the first part 103 is greater than the number of the first flow disturbing group 140 in the first row of heat exchange tubes 111 in the second part 104.

[0126] Specifically, after the air flow enters the heat exchanger 100, it preferentially flows through the first row of heat exchange tubes 111 for heat exchange. The temperature difference between the air flow and the first row of heat exchange tubes 111 is the largest. After the air flow exchanges heat with multiple rows of heat exchange tubes 110 in sequence, it flows to the last row of heat exchange tubes 112, and the temperature difference between the air flow and the last row of heat exchange tubes 112 is the smallest. By making the number of the first spoiler groups 140 in the first row of heat exchange tubes 111 greater than the number of the first spoiler groups 140 in the last row of heat exchange tubes 112, the turbulence effect of the air flow channel 122 corresponding to the first row of heat exchange tubes 111 is improved, the heat exchange time between the air flow and the first row of heat exchange tubes 111 is increased, and the heat exchange effect of the first row of heat exchange tubes 111 on the air flow is improved, thereby facilitating the improvement of the heat exchange effect of the heat exchanger 100 on the air flow.

[0127] Optionally, since the air flow velocity of the air flow flowing to the first part 103 in the air duct machine 1000 is greater than the air flow velocity of the air flow flowing to the second part 104, by making the number of the first spoiler groups 140 in the first row of heat exchange tubes 111 located in the first part 103 greater than the number of the first spoiler groups 140 in the first row of heat exchange tubes 111 located in the second part 104, so that the number of the air flow channels 122 in the first row of heat exchange tubes 111 located in the first part 103 is greater than the number of the corresponding air flow channels 122 of the first row of heat exchange tubes 111 located in the second part 104, to improve the turbulence effect of the air flow channel 122 corresponding to the first row of heat exchange tubes 111 located in the first part 103, and make the heat exchange effect between the first row of heat exchange tubes 111 located in the first part 103 and the air flow greater than the heat exchange effect between the first row of heat exchange tubes 111 located in the second part 103 and the air flow, ensuring that the heat exchange capacity at different positions of the heat exchanger 100 is adapted to the characteristics of the air flow velocity.

[0128] Refer to Figure 16 , in some embodiments of the present invention, adjacent louvers 141 are arranged in parallel.

[0129] Specifically, the louver 141 and one side surface of the body portion 121 in the thickness direction (i.e., the first direction) are arranged at an angle, and adjacent louvers 141 are arranged parallel to each other, so that the first air flow channel 1221 defined by adjacent louvers 141 and one side surface of the body portion 121 in the thickness direction are arranged at an angle, facilitating the air flow to flow into the first air flow channel 1221, and being beneficial to improving the turbulence effect of the louver 141 on the air flow.

[0130] At the same time, the parallel arrangement of adjacent louvers 141 can facilitate the processing of the louvers 141, thereby being beneficial to improving the processing and production efficiency of the heat exchange fins 120.

[0131] Such as Figure 16As shown, in some embodiments of the present invention, in the thickness direction of the heat exchange fin 120, the heat exchange fin 120 includes a first surface 123 disposed opposite to each other, and both sides of at least one louver 141 extend beyond the first surface 123 respectively.

[0132] Specifically, in the thickness direction of the heat exchange fin 120, the heat exchange fin 120 includes a first surface 123 disposed opposite to and spaced apart from each other, a through hole penetrates the first surface 123, and both sides of at least one louver 141 extend out of the first surface 123 in the thickness direction of the heat exchange fin 120, so that there is a height difference between the louver 141 and the first surface 123, enabling the louver 141 to play a role in disturbing the air flow when the air flow passes through the heat exchange fin 120, increasing the heat exchange time between the air flow and the heat exchange fin 120, and improving the heat exchange effect of the air flow.

[0133] Among them, the number of louvers 141 that extend out of the first surface 123 on both sides can be 1, 2, 3, etc. The specific number setting can be determined according to the heat exchange requirements of the heat exchanger 100 and the influence of the louver 141 disturbing the flow on the heat exchange effect, and no specific limitation is made here.

[0134] Referring to Figure 16 , in some embodiments of the present invention, each group of first flow disturbance groups 140 includes an end louver 1411 and an intermediate louver 1412. End louvers 1411 are provided on both sides of the intermediate louver 1412, and the protruding directions of the end louvers 1411 on both sides with respect to the body portion 121 are opposite, and both ends of the intermediate louver 1412 extend beyond the first surface 123.

[0135] It should be noted that the multiple louvers 141 of the first flow disturbance group 140 are arranged in sequence along the width direction of the body portion 121. Among them, in the width direction of the body portion 121, the louvers 141 located on both sides in the width direction are defined as end louvers 1411, and the louvers 141 located between the two end louvers 1411 are defined as intermediate louvers 1412.

[0136] Specifically, one of the two first surfaces 123 is defined as the upper surface 1231, and the other first surface 123 is defined as the lower surface 1232. Both ends of the intermediate louver 1412 protrude from the two opposite first surfaces 123 respectively, that is, one end of the intermediate louver 1412 protrudes from the upper surface 1231 in a direction away from the body portion 121, and the other end of the intermediate louver 1412 protrudes from the lower surface 1232 in a direction away from the body portion 121.

[0137] One end of the end louver 1411 extends out of the first surface 123. One of the two end louvers 1411 protrudes from the upper surface 1231 in a direction away from the body portion 121, and the other of the two end louvers 1411 protrudes from the lower surface 1232 in a direction away from the body portion 121, so that the number of protrusions on both sides of the body portion 121 in the thickness direction is the same, that is, the arrangement of the plurality of first air flow channels 1221 is the same, so that the flow disturbance effects on both sides of the body portion 121 on the air flow are the same, which is beneficial to ensuring the uniformity of heat exchange on both sides of the heat exchange fin 120 and improving the heat exchange performance of the heat exchanger 100.

[0138] Combined Figure 15 with Figure 16 , in some embodiments of the present invention, the heat exchanger 100 is provided with a windward side 101 and a leeward side 102. In the direction from the windward side 101 to the leeward side 102, the body portion 121 is provided with a plurality of first flow disturbance groups 140, and the first air flow channels 1221 of adjacent first flow disturbance groups 140 extend obliquely in a direction facing each other.

[0139] Specifically, the heat exchange fins 120 are provided with multiple rows of heat exchange tubes 110. Each row of heat exchange tubes 110 includes a plurality of heat exchange tubes 110 arranged at intervals along the extending direction of the heat exchange fins 120. Two first flow disturbance groups 140 can be arranged between every two heat exchange tubes 110. The two first flow disturbance groups 140 are arranged adjacent to each other in the direction from the windward side 101 to the leeward side 102. It can also be understood that one of the two first flow disturbance groups 140 is arranged relatively close to the windward side 101 of the heat exchanger 100, and the other of the two first flow disturbance groups 140 is arranged relatively close to the leeward side 102 of the heat exchanger 100.

[0140] Furthermore, the louvers 141 of two adjacent first flow disturbance groups 140 arranged adjacent to each other and opposite to each other are arranged at an angle, that is, in the thickness direction of the heat exchange fins 120, one ends of the two end louvers 1411 of two adjacent first flow disturbance groups 140 arranged adjacent to each other and opposite to each other are close to each other, and the other ends are far from each other. The louvers 141 of each first flow disturbance group 140 are arranged in parallel, so that the first air flow channels 1221 of adjacent first flow disturbance groups 140 extend obliquely in a direction facing each other, and the air flow can flow from one first surface 123 of the heat exchange fins 120 to the other first surface 123 through the first air flow channels 1221 of the first flow disturbance group 140 relatively close to the windward side 101.

[0141] For example, the air flow can flow from the upper surface 1231 of the heat exchange fin 120 to the lower surface 1232 of the air flow through the first air flow channel 1221 of the first spoiler group 140 relatively close to the windward side 101, and then the air flow flows to the first air flow channel 1221 of the first spoiler group 140 relatively close to the leeward side 102 and flows from the lower surface 1232 of the heat exchange fin 120 to the upper surface 1231 of the air flow, increasing the length of the air flow path, enabling the air flow to fully exchange heat with the heat exchange fin 120, and improving the heat exchange effect of the heat exchange fin 120 on the air flow.

[0142] Combined with Figure 15 and Figure 17 , in some embodiments of the present invention, the air flow channel 122 further includes a second air flow channel 1222, the heat exchange fin 120 further includes at least one group of second spoiler groups 150, and each group of second spoiler groups 150 includes a plurality of spaced bridge pieces 151, and a second air flow channel 1222 is defined between each bridge piece 151 and the body portion 121.

[0143] Specifically, the air flow channel 122 further includes a second air flow channel 1222, and the second air flow channel 1222 is defined by the space between each bridge piece 151 and the body portion 121. The second air flow channel 1222 penetrates through the body portion 121 in the thickness direction of the heat exchange fin 120. When the air flow flows through one side of the heat exchange fin 120, the air flow can flow into the other side of the heat exchange fin 120 through the second air flow channel 1222. For example, when the air flow flows on one side of the upper surface 1231 of the heat exchange fin 120, the air flow can flow into the other side of the lower surface 1232 of the air flow through the second air flow channel 1222, so that the second spoiler group 150 can play a role in disturbing the flow, further increasing the time for the air flow to flow through the heat exchange fin 120, ensuring that the air flow can fully exchange heat, and further improving the heat exchange effect of the heat exchanger 100 on the air flow.

[0144] Optionally, one group of the first spoiler groups 140 can be provided, and multiple groups of the second spoiler groups 150 can also be provided. The specific number of the second spoiler groups 150 can be determined according to the heat exchange requirements of the heat exchanger 100, and no specific limitation is made here. It should be noted that the first spoiler group 140 and the second spoiler group 150 are arranged at intervals and uniformly distributed, which is beneficial to ensuring the spoiler effect of the first spoiler part and the second spoiler part, and thus ensuring the heat exchange effect of the air flow.

[0145] Combined with Figure 15 and Figure 17 , in some embodiments of the present invention, each bridge piece 151 is defined by separating and deforming a part of the body portion 121 from the rest.

[0146] Specifically, a part of the main body portion 121 can be separated from the remaining at least part by processing methods such as cutting or trimming and deformed to define the bridge piece 151. For example, a sheet-like structure can be cut out on the main body portion 121, with one side edge connected to the remaining part of the main body portion 121 and the remaining three side edges separated from the remaining part of the main body portion 121, and this sheet-like structure is configured as the bridge piece 151.

[0147] Further, the bridge piece 151 can be made perpendicular to the main body portion 121 by folding, so as to expose the second air flow channel 1222 formed by separating the bridge piece 151 from the remaining part of the main body portion 121, facilitating the flow of air through the second air flow channel 1222. And the perpendicular arrangement of the bridge piece 151 and the main body portion 121 can also disturb the air flow, thereby improving the flow disturbance effect of the second flow disturbance group 150.

[0148] As Figure 15 shown, in some embodiments of the present invention, the number of the first flow disturbance groups 140 is less than the number of the second flow disturbance groups 150.

[0149] Specifically, the flow disturbance effect of the first flow disturbance group 140 is better than that of the second flow disturbance group 150. However, when the number of the first flow disturbance groups 140 is set too large, it will cause a large heat exchange pressure drop of the heat exchanger 100, resulting in an increase in the power consumption of the heat exchanger 100, and will also cause poor heat exchange performance and shortened service life of the heat exchanger 100. By making the number of the first flow disturbance groups 140 less than the number of the second flow disturbance groups 150, it is beneficial to balance the heat exchange pressure drop, ensure the heat exchange performance of the heat exchanger 100, reduce the power consumption of the heat exchanger 100, and at the same time is beneficial to improving the service life of the heat exchanger 100.

[0150] Referring to Figure 15 , in some embodiments of the present invention, the heat exchanger 100 is provided with a windward side 101 and a leeward side 102, and the first flow disturbance group 140 is arranged close to the windward side 101.

[0151] Specifically, the air flow flows into the heat exchanger 100 from the windward side 101. Since the temperature difference between the air flow and the heat exchanger 100 is large when the air flow just flows into the heat exchanger 100 from the windward side 101, and the flow disturbance effect of the first flow disturbance group 140 is good, by arranging the first flow disturbance group 140 close to the windward side 101, so that the air flow can flow through the first flow disturbance group 140 after flowing into the heat exchanger 100, and the first flow disturbance group 140 disturbs the air flow, enabling the air flow to fully exchange heat with the heat exchange fins 120 and reducing the temperature difference between the air flow and the heat exchanger 100.

[0152] Further, the second spoiler group 150 is arranged away from the windward side 101 relative to the first spoiler group 140. When the air flow passes through the first spoiler group 140, the air flow further passes through the second spoiler group 150, and the second spoiler group 150 disturbs the air flow so that the air flow can further exchange heat with the heat exchange fins 120, improving the heat exchange effect of the air flow and being beneficial to improving the heat exchange performance of the heat exchanger 100.

[0153] The following will describe the structure of the heat exchanger 100 according to some embodiments of the present invention in conjunction with the attached Figure 1 to the attached Figure 3 and the attached Figure 9 to the attached Figure 15 description.

[0154] As Figure 1 and Figure 15 shown, in some embodiments of the present invention, the first part 103 includes a first area 131, a second area 132 and a third area 133. Among them, the first area 131 is arranged closest to the windward side 101, the third area 133 is arranged closest to the leeward side 102 on the first part 103, and the second area 132 is clamped between the first area 131 and the third area 133 in the width direction of the heat exchange fins 120. The second part 104 includes a fourth area 134 and a fifth area 135. The fourth area 134 is arranged closest to the windward side 101 on the second part 104, the fifth area 135 is arranged closest to the leeward side 102 on the second part 104, and the fourth area 134 and the fifth area 135 are adjacent. A part of the first row of heat exchange tubes 111 is arranged in the first area 131, another part of the first row of heat exchange tubes 111 is arranged in the fourth area 134, the second row of heat exchange tubes 113 is arranged in the second area 132, a part of the last row of heat exchange tubes 112 is arranged in the third area 133, and another part of the last row of heat exchange tubes 112 is arranged in the fifth area 135.

[0155] Further, according to the flow velocity distribution of the air flow and the temperature gradient change of the heat exchange fins 120, different fin types can be set in different areas, that is, the first spoiler group 140 or the second spoiler group 150 or a combination of the first spoiler group 140 and the second spoiler group 150 can be arranged in the first area 131 to the fifth area 135.

[0156] In some embodiments of the present invention, the second spoiler group 150 is provided on all of the first region 131 to the fifth region 135. The number of bridge pieces 151 of each second spoiler group 150 on the heat exchange fins 120 in the first region 131 is 2 - 6. The number of bridge pieces 151 of each second spoiler group 150 provided on the heat exchange fins 120 in the second region 132 is 2 - 5. The number of bridge pieces 151 of each second spoiler group 150 provided on the heat exchange fins 120 in the third region 133 is 2 - 4. The number of bridge pieces 151 of each second spoiler group 150 provided on the heat exchange fins 120 in the fourth region 134 is 3 - 6. The number of bridge pieces 151 of each second spoiler group 150 provided on the heat exchange fins 120 in the fifth region 135 is 2 - 5.

[0157] Since the flow velocity of the air flow flowing into the first region 131 and the temperature difference between the air flow and the heat exchange tube 110 are greater than the flow velocity of the air flow flowing into the second region 132 and the third region 133 and the temperature difference between the air flow and the heat exchange tube 110. Similarly, the flow velocity of the air flow flowing into the second region 132 and the temperature difference between the air flow and the heat exchange tube 110 are greater than the flow velocity of the air flow flowing into the third region 133 and the temperature difference between the air flow and the heat exchange tube 110. The flow velocity of the air flow flowing into the fourth region 134 and the temperature difference between the air flow and the heat exchange tube 110 are greater than the flow velocity of the air flow flowing into the fifth region 135 and the temperature difference between the air flow and the heat exchange tube 110. Therefore, by adjusting the fin type of the heat exchange fins 120 in different regions (i.e., adjusting the number of bridge pieces 151 of the second spoiler group 150 on the heat exchange fins 120 in different regions), the heat exchange effect of the heat exchange fins 120 is adjusted, thereby regulating the heat exchange capacity of the heat exchange fins 120 to ensure that the heat exchange effects of the heat exchange fins 120 in different regions on the air flow can meet the heat exchange requirements of the air flow. It can be understood that the more the number of bridge pieces 151 of the heat exchange fins 120, the stronger the heat exchange capacity of the heat exchange fins 120.

[0158] For example, as Figure 1 shown, the number of bridge pieces 151 provided in the first region 131 and the fourth region 134 can both be 3, that is, the number of rows of the second air flow channels 1222 between two adjacent heat exchange tubes 110 of the first row of heat exchange tubes 111 can both be three rows. The number of bridge pieces 151 provided in the second region 132, the third region 133 and the fifth region 135 can all be 2, that is, the number of rows of the second air flow channels 1222 between two adjacent heat exchange tubes 110 of the second row of heat exchange tubes 113 can all be two rows. At the same time, the number of rows of the second air flow channels 1222 between two adjacent heat exchange tubes 110 of the last row of heat exchange tubes 112 can all be two rows, so that the number of air flow channels 122 in the first part 103 is greater than the number of air flow channels 122 in the second part 104, ensuring the heat exchange effect of the heat exchanger 100 while facilitating the processing of the heat exchanger 100, which is beneficial to improving the production and processing efficiency of the heat exchanger 100.

[0159] Optionally, on the basis that the number of bridge plates 151 of the second spoiler group 150 provided in the first region 131 and the fourth region 134 can both be 3, and the number of bridge plates 151 of the second spoiler group 150 provided in the second region 132, the third region 133, and the fifth region 135 can both be 2, combined with Figure 4 and Figure 9 , since the air flow velocity is fast when the air flow flows to the positions close to each other on the first region 131 and the fourth region 134, the number of bridge plates 151 of the second spoiler group 150 at the positions close to each other on the first region 131 and the fourth region 134 can be further increased, so that the number of bridge plates 151 of the second spoiler group 150 at the positions close to each other on the first region 131 and the fourth region 134 is 4. Since the air flow velocity is slow when the air flow passes through the end of the fourth region 134 far from the first region 131, the number of bridge plates 151 of the second spoiler group 150 at the end of the fourth region 134 far from the first region 131 can be reduced, so that the number of bridge plates 151 of the second spoiler group 150 at the end of the fourth region 134 far from the first region 131 is 2, so that the number of the second air flow channels 1222 in the first part 103 is greater than the number of the second air flow channels 1222 in the second part 104, ensuring the heat exchange effect of the heat exchanger 100.

[0160] Optionally, combined with Figure 4 and Figure 10 , since the air flow velocity is fast when the air flow flows to the positions close to each other on the first region 131 and the fourth region 134, the number of bridge plates 151 of the second spoiler group 150 at the positions close to each other on the first region 131 and the fourth region 134 can be set to 4, and the number of bridge plates 151 of the second spoiler group 150 at the end of the first region 131 far from the fourth region 134 can be set to 3. Since the air flow velocity is slow when the air flow passes through the end of the fourth region 134 far from the first region 131, the number of bridge plates 151 of the second spoiler group 150 at the end of the fourth region 134 far from the first region 131 can be set to 2, and the number of bridge plates 151 of the second spoiler group 150 at the middle position of the fourth region 134 can be set to 2.

[0161] Furthermore, since the flow velocity of the air flowing into the middle position of the second region 132 is higher than that of the air flowing into the two ends of the second region 132, the number of bridge plates 151 of the second spoiler group 150 at the middle position of the second region 132 can be set to 3, and the number of bridge plates 151 of the second spoiler group 150 at the two ends of the second region 132 can be set to 2. Similarly, since the flow velocities of the air flowing into the third region 133 and the fifth region 135 are relatively low, the number of bridge plates 151 of the second spoiler group 150 in the third region 133 and the fifth region 135 can be set to 2, so that the number of the second air flow channels 1222 in the first part 103 is greater than that in the second part 104, thereby further improving the heat exchange effect of the heat exchanger 100 and facilitating the improvement of the production and processing efficiency of the heat exchanger 100.

[0162] Optionally, in combination with Figure 4 and Figure 11 , the number of bridge plates 151 of the second spoiler group 150 at the positions where the first region 131 and the fourth region 134 are close to each other is set to 4, the number of bridge plates 151 of the second spoiler group 150 at one end of the first region 131 far from the fourth region 134 is set to 3, the number of bridge plates 151 of the second spoiler group 150 at one end of the fourth region 134 far from the first region 131 is set to 2, the number of bridge plates 151 of the second spoiler group 150 at the middle position of the fourth region 134 is set to 2, the number of bridge plates 151 of the second spoiler group 150 at the middle position of the second region 132 is set to 3, and the number of bridge plates 151 of the second spoiler group 150 at the two ends of the second region 132 is set to 2.

[0163] Furthermore, since the flow velocity of the air flowing into the middle position of the third region 133 is higher than that of the air flowing into the two ends of the third region 133 and the air flowing into the fifth region 135, the number of bridge plates 151 of the second spoiler group 150 at the middle position of the third region 133 can be set to 3, and the number of bridge plates 151 of the second spoiler group 150 at the two ends of the third region 133 and the number of bridge plates 151 of the second spoiler group 150 in the fifth region 135 can be set to 2, so that the number of the second air flow channels 1222 in the first part 103 is greater than that in the second part 104, thereby further improving the heat exchange effect of the heat exchanger 100 on the air flow.

[0164] Optionally, in combination with Figure 4 and Figure 12, since the air flow velocity flowing into the first region 131 is greater than that flowing into the second region 132, the air flow velocity flowing into the second region 132 is greater than that flowing into the third region 133, and the air flow velocity at the middle position of the first region 131 is greater than that at both ends of the first region 131. Similarly, the air flow velocity at the middle position of the second region 132 is greater than that at both ends of the second region 132. Therefore, the number of bridge pieces 151 of the second spoiler group 150 at the middle position of the first region 131 can be set to 4, the number of bridge pieces 151 of the second spoiler group 150 at both ends of the first region 131 can be set to 3, the number of bridge pieces 151 of the second spoiler group 150 at the middle position of the second region 132 can be set to 3, the number of bridge pieces 151 of the second spoiler group 150 at both ends of the second region 132 can be set to 2, and the number of bridge pieces 151 of the second spoiler group 150 in the third region 133 can be set to 2.

[0165] Furthermore, the air flow velocity flowing into the fourth region 134 is greater than that flowing into the fifth region 135, and the air flow velocity at the end of the fourth region 134 far from the first region 131 is relatively small. Therefore, the number of bridge pieces 151 of the second spoiler group 150 at the end of the fourth region 134 far from the first region 131 can be set to 2, the number of bridge pieces 151 of the second spoiler group 150 at the remaining positions of the fourth region 134 can be set to 2, and the number of bridge pieces 151 of the second spoiler group 150 in the fifth region 135 can be set to 2, so that the number of the second air flow channels 1222 in the first part 103 is greater than that in the second part 104, which is beneficial to improving the heat exchange effect of the heat exchanger 100.

[0166] Combined with Figure 4 and Figure 13 , optionally, since the inclined part 1031 extends along a straight line and the transition part 1032 extends in an arc, the space on the inclined part 1031 is small and the space of the transition part 1032 is large. The number of bridge pieces 151 of the second spoiler group 150 where the first region 131 is located on the inclined part 1031 can be set to 4, and the number of bridge pieces 151 of the second spoiler group 150 where the first region 131 is located on the transition part 1032 can be set to 7, so as to make full use of the space that can be arranged on the transition part 1032, which is beneficial to further increasing the number of air flow channels 122 on the first part 103. The number of bridge pieces 151 of the second spoiler group 150 at the middle position of the second region 132 can be set to 3, and the number of bridge pieces 151 of the second spoiler group 150 at both ends of the second region 132 can be set to 2. The number of bridge pieces 151 of the second spoiler group 150 where the third region 133 is located on the inclined part 1031 can be set to 3, and the number of bridge pieces 151 of the second spoiler group 150 where the third region 133 is located on the transition part 1032 can be set to 2.

[0167] Further, the number of bridge pieces 151 of the second spoiler group 150 at one end of the fourth region 134 relatively close to the first region 131 can be set to 4, and the number of bridge pieces 151 of the second spoiler group 150 at one end of the fourth region 134 relatively far from the first region 131 can be set to 3. The number of bridge pieces 151 of the second spoiler group 150 at one end of the fifth region 135 relatively close to the third region 133 can be set to 3, and the number of bridge pieces 151 of the second spoiler group 150 at one end of the fifth region 135 relatively far from the third region 133 can be set to 2. Thus, the number of the second air flow channels 1222 provided in the first part 103 is greater than the number of the second air flow channels 1222 provided in the second part 104, so that the heat exchange capacity of the first part 103 is adapted to the heat exchange capacity of the second part 104 and the flow rate of the air flow, ensuring the heat exchange effect of the heat exchanger 100.

[0168] Optionally, in combination with Figure 4 and Figure 14 , since the temperature difference between the air flow flowing into the first row of heat exchange tubes 111 and the first row of heat exchange tubes 111 is greater than the temperature difference between the air flow and the second row of heat exchange tubes 113 when the air flow flows into the second row of heat exchange tubes 113, and the temperature difference between the air flow and the second row of heat exchange tubes 113 is greater than the temperature difference between the air flow and the last row of heat exchange tubes 112, in order to make the heat exchange effect between the first row of heat exchange tubes 111 and the air flow greater than the heat exchange effect between the second row of heat exchange tubes 113 and the air flow, and the heat exchange effect between the second row of heat exchange tubes 113 and the air flow greater than the heat exchange effect between the last row of heat exchange tubes 112 and the air flow, the number of the second air flow channels 1222 provided in the first row of heat exchange tubes 111 can be made greater than the number of the second air flow channels 1222 provided in the second row of heat exchange tubes 113, and the number of the second air flow channels 1222 provided in the second row of heat exchange tubes 113 can be greater than the number of the second air flow channels 1222 provided in the last row of heat exchange tubes 112.

[0169] Furthermore, the number of bridge pieces 151 of the second spoiler group 150 in the first region 131 can be set to 4, the number of bridge pieces 151 of the second spoiler group 150 in the second region 132 located in the inclined portion 1031 can be set to 3; on the second region 132, the number of bridge pieces 151 of the second spoiler group 150 at one end of the transition portion 1032 far from the inclined portion 1031 can be set to 2, and the number of bridge pieces 151 of the second spoiler group 150 at one end of the transition portion 1032 close to the inclined portion 1031 can be set to 3; the number of bridge pieces 151 of the second spoiler group 150 in the third region 133 can be set to 2, the number of bridge pieces 151 of the second spoiler group 150 at one end of the fourth region 134 close to the first region 131 can be set to 4, the number of bridge pieces 151 of the second spoiler group 150 at one end of the fourth region 134 far from the first region 131 can be set to 3, the number of bridge pieces 151 of the second spoiler group 150 at one end of the fifth region 135 close to the third region 133 can be set to 3, and the number of bridge pieces 151 of the second spoiler group 150 at one end of the fifth region 135 far from the third region 133 can be set to 2.

[0170] Of course, it can be understood that the structure of the heat exchange fin 120 described above with reference to Figure 1 to Figure 3 and Figure 9 to Figure 14 is only some embodiments of the present invention. Among them, at least a part of the second spoiler group 150 can be replaced by the first spoiler group 140, and the specific arrangement of the first spoiler group 140 and the second spoiler group 150 can be determined according to the heat exchange requirements of the heat exchanger 100 and the flow velocity characteristics of the air flow, and no specific limitation is made here.

[0171] In some other embodiments of the present invention, the first spoiler group 140 is provided in all of the first region 131 to the fifth region 135. The number of louvers 141 of each group of the first spoiler group 140 on the heat exchange fin 120 in the first region 131 is 4 - 8, the number of louvers 141 of each group of the first spoiler group 140 provided on the heat exchange fin 120 in the second region 132 is 2 - 6, the number of louvers 141 of each group of the first spoiler group 140 provided on the heat exchange fin 120 in the third region 133 is 2 - 4, the number of louvers 141 of each group of the first spoiler group 140 provided on the heat exchange fin 120 in the fourth region 134 is 4 - 8, and the number of louvers 141 of each group of the first spoiler group 140 provided on the heat exchange fin 120 in the fifth region 135 is 2 - 6.

[0172] By adjusting the fin types of the heat exchange fins 120 in different regions (i.e., adjusting the number of louvers 141 of the first spoiler group 140 of the heat exchange fins 120 in different regions), the heat exchange effect of the heat exchange fins 120 is adjusted, thereby regulating the heat exchange capacity of the heat exchange fins 120 to ensure that the heat exchange effects of the heat exchange fins 120 in different regions on the air flow can meet the heat exchange requirements of the air flow.

[0173] In some other embodiments of the present invention, a combination of the first spoiler group 140 and the second spoiler group 150 is provided on the first region 131 to the fifth region 135.

[0174] For example, in combination with Figure 4 and Figure 15 , a second spoiler group 150 can be provided between two adjacent heat exchange tubes 110 in the first region 131 located in the inclined portion 1031 and away from one end of the fourth region 134, and the number of bridge pieces 151 of the second spoiler group 150 can be 3. A first spoiler group 140 can be provided between two adjacent heat exchange tubes 110 in the remaining positions of the first region 131 located in the inclined portion 1031, and the number of louvers 141 of the first spoiler group 140 can be 8. A first spoiler group 140 can be provided between two adjacent heat exchange tubes 110 in the first region 131 located in the transition portion 1032 and relatively away from one end of the fourth region 134, and the number of louvers 141 of the first spoiler group 140 can be 8. A second spoiler group 150 can be provided between two adjacent heat exchange tubes 110 in the first region 131 located in the transition portion 1032 and relatively close to the fourth region 134, and the number of bridge pieces 151 of the second spoiler group 150 can be 4.

[0175] Further, a second spoiler group 150 can be provided between two adjacent heat exchange tubes 110 provided adjacent to each other on the fourth region 134. Among them, the number of bridge pieces 151 of the second spoiler group 150 between two adjacent heat exchange tubes 110 at one end close to the transition portion 1032 can be 4, and the number of bridge pieces 151 of the second spoiler group 150 on the fourth region 134 away from the transition region can be 3.

[0176] Further, second spoiler groups 150 can be provided on the second region 132, the third region 133, and the fifth region 135, and the number of bridge pieces 151 of the second spoiler group 150 can be 2.

[0177] Thus, by partitioning and designing the number of the air flow channels 122 of the heat exchanger 100, the heat exchange efficiency of different regions of the heat exchanger 100 can be adapted to the flow velocity characteristics of the air flow flowing into different regions of the heat exchanger 100, improving the heat exchange effect of the heat exchanger 100.

[0178] In combination with Figure 1 and Figure 15, in a further embodiment of the present invention, the number of air flow channels 122 provided in the first region 131 is greater than the number of air flow channels 122 provided in the second region 132 and the third region 133, and the number of air flow channels 122 provided in the fourth region 134 is greater than the number of air flow channels 122 provided in the fifth region 135, ensuring the turbulence effect of the air flow channels 122 on the windward side 101 of the first part 103 and the second part 104.

[0179] Furthermore, the first region 131 can be connected to the fourth region 134, and the heat exchange tubes 110 in the first region 131 and the heat exchange tubes 110 in the fourth region 134 together form the first row of heat exchange tubes 111. The third region 133 can be connected to the fifth region 135, and the heat exchange tubes 110 in the third region 133 and the heat exchange tubes 110 in the fifth region 135 together form the last row of heat exchange tubes 112, so that the number of air flow channels 122 corresponding to the first row of heat exchange tubes 111 can be greater than the number of air flow channels 122 corresponding to the last row of heat exchange tubes 112.

[0180] Among them, when the combination of the first turbulence group 140 and the second turbulence group 150 is provided on the first region 131 to the fifth region 135, it is preferably to provide the first turbulence group 140 between the heat exchange tubes 110 relatively close to the windward side 101. For example: when the heat exchanger 100 is provided with three rows of heat exchange tubes 110, it is preferably to provide the first turbulence group 140 corresponding to the first row of heat exchange tubes 111, and the second row of heat exchange tubes 113 and the last row of heat exchange tubes 112 are provided with the second turbulence group 150, or the first row of heat exchange tubes 111 and the second row of heat exchange tubes 113 are provided with the first turbulence group 140, and the last row of heat exchange tubes 112 is provided with the second turbulence group 150.

[0181] When the heat exchanger 100 is provided with two rows of heat exchange tubes 110, it is preferably to provide the first turbulence group 140 corresponding to the first row of heat exchange tubes 111, and the second turbulence group 150 corresponding to the last row of heat exchange tubes 112.

[0182] It is beneficial to make the heat exchange effects at different positions of the heat exchanger 100 adaptable to the flow rate of the air flow and the temperature difference between the air flow when flowing into the heat exchanger 100 and the heat exchange tubes 110, ensuring the heat exchange effect of the heat exchanger 100.

[0183] In some embodiments of the present invention, there is no limitation on the refrigerant flow path of the heat exchanger 100. The refrigerant can flow into any one or more heat exchange tubes of the heat exchanger 100 and flow out from any one or more other heat exchange tubes. The heat exchanger 100 of this embodiment is applicable to a variety of different refrigerant flow paths. Through experiments, under the structural and parameter limitations of this embodiment, a variety of different refrigerant flow paths can achieve the technical effect of improving the heat exchange efficiency. In some examples, the refrigerant flows into the first row of heat exchange tubes 111 and flows out from the last row of heat exchange tubes 112. For example, the refrigerant flows into multiple heat exchange tubes of the first row of heat exchange tubes 111 in the first part 103 and the second part 104 and flows out from multiple heat exchange tubes of the last row of heat exchange tubes 112 in the first part 103 and the second part 104. In other examples, the refrigerant can flow into the last row of heat exchange tubes 112 and flow out from the first row of heat exchange tubes 111.

[0184] Combined with Figure 18 and Figure 19 , the air duct machine 1000 according to the present invention includes: a heat exchanger 100 and a driving fan 200. The heat exchanger 100 is the above-mentioned heat exchanger 100, and the air outlet 210 of the driving fan 200 is arranged facing the windward side 101 of the heat exchanger 100.

[0185] Specifically, the air duct machine 1000 can be used to adjust the air flow and temperature. Among them, the air duct machine 1000 is provided with a driving fan 200. An installation space is formed inside the air duct machine 1000. The driving fan 200 and the heat exchanger 100 are arranged at intervals in the installation space. Among them, the driving fan 200 can drive the air to flow to form an air flow. The air flow flows out from the air outlet 210 of the driving fan 200. The air outlet 210 is arranged facing the windward side 101 of the heat exchanger 100. After flowing out from the air outlet 210, the air flow flows to the windward side 101 of the heat exchanger 100.

[0186] Combined with Figure 18 and Figure 19 , the bottom end of the heat exchanger 100 is in abutting cooperation with the lower wall surface 400 of the installation space. A partition plate 600 is arranged at a position where the upper wall surface 500 of the installation space is opposite to the top end of the heat exchanger 100. The partition plate 600 extends in the vertical direction. The bottom of the partition plate 600 is in abutting cooperation with the top end of the heat exchanger 100 to seal the space between the top end of the heat exchanger 100 and the upper wall surface 500 of the installation space. Thus, it can prevent the existence of a gap between the heat exchanger 100 and the wall surface of the installation space, resulting in the air flow directly escaping without participating in heat exchange, and ensure the effect of the air flow flowing to the heat exchanger 100.

[0187] Of course, it can be understood that the top end of the heat exchanger 100 can be directly abutted and cooperated with the upper wall surface 500 of the installation space, so as to reduce the component layout of the air duct machine 1000 and lower the production cost of the air duct machine 1000. Specifically, the cooperation mode between the top end of the heat exchanger 100 and the upper wall surface 500 of the installation space can be determined according to the installation space and the dimensional relationship of the heat exchanger 100 in the vertical direction, and no specific limitation is made here, as long as there is no gap between the heat exchanger 100 and the wall surface of the installation space.

[0188] Furthermore, the wall surface of the heat exchanger 100 located on the windward side 101 can guide the air flow to reduce the escaping air flow and improve the effect of the air flow flowing towards the heat exchanger 100. After the air flow flows towards the heat exchanger 100, it can exchange heat with the heat exchange tubes 110 and the heat exchange fins 120, thereby adjusting the temperature of the air flow. After heat exchange, the air flow flows out of the heat exchanger 100 and out of the air duct machine 1000, realizing the function of the air duct machine 1000 to adjust the air temperature.

[0189] Since the air duct machine 1000 is provided with the above-mentioned heat exchanger 100, by making the inclination angle A of the inclined portion 1031 greater than the inclination angle B of the second portion 104, the opening area of the opening of the heat exchanger 100 jointly defined by the first portion 103 and the second portion 104 is large, ensuring that the flow velocity of the air flow that can flow into the heat exchanger 100 is large, thereby being beneficial to improving the heat exchange efficiency between the air flow and the heat exchanger 100.

[0190] In some embodiments of the present invention, the driving fan 200 is a centrifugal fan.

[0191] Specifically, the centrifugal fan can accelerate the air flow by rotating the centrifugal wheel at a high speed, thereby improving the efficiency of air circulation. Moreover, compared with other types of fans, the centrifugal fan has small energy consumption and low usage cost while ensuring the efficiency of air circulation, so that the air duct machine 1000 can save energy. In addition, compared with other types of fans, the centrifugal fan generates less noise, which is beneficial to reducing the noise generated by the air duct machine 1000 and improving the user experience.

[0192] In a further embodiment of the present invention, multiple centrifugal fans can be provided, and the multiple centrifugal fans are evenly spaced along the rotation axis parallel to the centrifugal fans, so as to further improve the efficiency of driving the air flow of the air duct machine 1000, thereby being beneficial to improving the heat exchange efficiency of the air duct machine 1000 for air.

[0193] Refer to Figure 18 , in some embodiments of the present invention, in the vertical cross-section, the bottom wall 211 of the air outlet 210 extends obliquely downward towards the heat exchanger 100, and the extension line of the bottom wall 211 of the air outlet 210 passes through the second portion 104.

[0194] Specifically, the size of the heat exchanger 100 in the vertical direction is greater than the size of the air outlet 210 in the vertical direction. The positive projection of the air outlet 210 in the air outlet direction coincides with the positive projection of the heat exchanger 100 in the air outlet direction, which is beneficial to improving the effect of the air flow flowing towards the heat exchanger 100. Moreover, the bottom wall 211 of the air outlet 210 extends obliquely downward towards the bottom end of the second part 104, and the extension line of the bottom wall 211 of the air outlet 210 passes through the bottom end of the second part 104. The top wall 212 of the air outlet 210 extends obliquely downward towards the first part 103, and the extension line of the top wall 212 of the air outlet 210 passes through the top end (or the middle position of the first part 103) of the first part 103. The bottom wall 211 and the top wall 212 of the air outlet 210 can guide the air flow, ensuring the effect of the air flow flowing towards the heat exchanger 100, thereby ensuring the effect of the air flow exchanging heat with the heat exchanger 100, and further ensuring the air temperature adjustment effect of the air duct machine 1000.

[0195] In some embodiments of the present invention, the driving fan 200 is configured as a centrifugal fan. Therefore, the driving fan 200 has axial air inlet and radial air outlet. By making the horizontal tangent line at the top end of the driving fan 200 located between the top wall 212 and the bottom wall 211 of the air outlet 210, and the horizontal tangent line at the top end of the driving fan 200 being arranged at an angle with the bottom wall 211 and the top wall 212 of the air outlet 210, and the angle between the horizontal tangent line at the top end of the driving fan 200 and the bottom wall 211 of the air outlet 210 being greater than the angle between it and the top wall 212 of the air outlet 210, it is convenient for the driving fan 200 to blow air towards the air outlet 210, improving the air outlet effect of the driving fan 200.

[0196] Refer to Figure 18 , in some embodiments of the present invention, the air duct machine 1000 is formed with an air outlet opening 300. The air outlet opening 300 is located on the leeward side 102 of the heat exchanger 100. After the air flow flows into the heat exchanger 100 and exchanges heat with the heat exchanger 100, the air flow flows out from the leeward side 102 of the heat exchanger 100 and towards the air outlet opening 300, and the air flow flows through the air outlet opening 300 to the external environment to adjust the temperature of the external environment.

[0197] Furthermore, the size of the air outlet opening 300 in the vertical direction is smaller than the size of the heat exchanger 100 in the vertical direction, which is beneficial to increasing the flow rate of the air flow when it flows out of the air duct machine 1000 and the flow distance of the air flow, improving the heat exchange efficiency of the air duct machine 1000 with the external environment.

[0198] Further, one end of the lower wall surface 400 of the installation space close to the air outlet opening 300 extends in an arc shape. When the air flow flows from the heat exchanger 100 to the air outlet opening 300, the lower wall surface 400 extending in an arc shape can guide the air flow, reduce the wind resistance, ensure that the air flow can flow out of the air duct machine 1000, and prevent the air flow from accumulating in the air duct machine 1000 and being unable to flow out.

[0199] In the description of this specification, the description with reference to terms such as "one embodiment", "some embodiments", "schematic embodiments", "examples", "specific examples", or "some examples", etc. means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0200] Although the embodiments of the present invention have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and spirit of the present invention. The scope of the present invention is defined by the claims and their equivalents.

Claims

1. A heat exchanger of an air duct machine, characterized in that, The heat exchanger has a windward side and a leeward side. The heat exchanger includes heat exchange tubes. The heat exchanger includes a first part and a second part. The first part is located above the second part. The first part includes an inclined part that extends obliquely towards the leeward side in the direction from top to bottom. The second part extends obliquely towards the windward side in the direction from top to bottom; The inclination angle of the inclined part is A, and the inclination angle of the second part is B, where the heat exchanger satisfies: A > B.

2. The heat exchanger of the air duct machine according to claim 1, characterized in that, The heat exchanger satisfies: 1.02 ≤ A / B ≤ 1.

31.

3. The heat exchanger of the air duct machine according to claim 1, characterized in that, In the direction from the windward side to the leeward side, the width of the inclined part is P1, and the width of the second part is P2, where P1 > P2.

4. The heat exchanger of the air duct machine according to claim 3, wherein The heat exchanger satisfies: 1.02 ≤ P1 / P2 ≤ 1.

45.

5. The heat exchanger of the air duct machine according to claim 1, wherein The first part further includes a transition part that is formed in an arc shape. The upper end of the transition part is connected to the inclined part, and the lower end of the transition part is connected to the second part.

6. The heat exchanger of the air duct machine according to claim 1, wherein, Both the first part and the second part are provided with multiple rows of heat exchange tubes, and the number of rows of the heat exchange tubes in the first part is greater than the number of rows of the heat exchange tubes in the second part; In the same vertical plane, the number of the heat exchange tubes in the first part is N1, and the number of the heat exchange tubes in the second part is N2. The heat exchanger satisfies the following relationship: 1.5 ≤ N1 / N2 ≤ 1.

9.

7. The heat exchanger of the air duct machine according to claim 6, wherein, The heat exchanger satisfies: 1.6 ≤ N1 / N2 ≤ 1.

8.

8. The heat exchanger of the air duct machine according to any one of claims 1-7, characterized in that, The heat exchanger further includes heat exchange fins, and the heat exchange tubes are passed through the heat exchange fins; In the first part or the second part, the distance between the center of the heat exchange tube on the windward side and the edge of the heat exchange fin is L1; The distance between the center of the heat exchange tube on the leeward side and the edge of the heat exchange fin is L2, where L1 is greater than L2.

9. The heat exchanger of the air duct machine according to claim 8, characterized in that, The heat exchanger satisfies the following relationship: 1.2 ≤ L1 / L2 ≤ 1.

45.

10. The heat exchanger of the air duct machine according to claim 8, characterized in that, Adjacent heat exchange fins are provided with air flow spaces, and at least a part of the heat exchange fins are provided with air flow channels that penetrate through them in the thickness direction. The air flow channels are communicated with the air flow spaces; The heat exchange tube closest to the windward side is defined as the first row of heat exchange tubes, and the heat exchange tube closest to the leeward side is defined as the last row of heat exchange tubes. The number of the air flow channels corresponding to the first row of heat exchange tubes is greater than the number of the air flow channels corresponding to the last row of heat exchange tubes.

11. The heat exchanger of the air duct machine according to claim 10, characterized in that, The number of the air flow channels corresponding to the first row of heat exchange tubes in the first part is greater than the number of the air flow channels corresponding to the first row of heat exchange tubes in the second part.

12. The heat exchanger of the air duct machine according to claim 10, wherein The air flow channels include first air flow channels, and the heat exchange fins include: A body part that includes a plurality of through holes for passing through the heat exchange tubes; The body part includes at least one group of first spoiler groups. Each group of first spoiler groups includes a plurality of louvers, and each louver is connected to the body part. The adjacent louvers define the first air flow channels.

13. The heat exchanger of the air duct machine according to claim 12, characterized in that, The air flow channel further includes a second air flow channel, and the heat exchange fins further include at least one set of second flow disturbing groups. Each set of the second flow disturbing groups includes a plurality of bridge pieces arranged at intervals, and a second air flow channel is defined between each bridge piece and the body portion.

14. The heat exchanger of the air duct machine according to claim 13, characterized in that, The number of the first flow disturbing groups in the first row of heat exchange tubes is greater than the number of the first flow disturbing groups in the last row of heat exchange tubes, or the number of the first flow disturbing groups in the first row of heat exchange tubes located in the first portion is greater than the number of the first flow disturbing groups in the first row of heat exchange tubes located in the second portion.

15. An air duct machine, characterized in that, Comprising: A heat exchanger, which is the heat exchanger according to any one of claims 1-14; A driving fan, and an air outlet of the driving fan is arranged towards the windward side of the heat exchanger.

16. The air duct machine according to claim 15, characterized in that, The driving fan is a centrifugal fan.

17. The air duct machine according to claim 15, characterized in that, In a vertical section, a bottom wall of the air outlet extends obliquely downward towards the heat exchanger, and an extension line of the bottom wall of the air outlet passes through the second portion.

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