Heat exchange sheet, heat exchanger and gas water heating equipment

Abstract

The utility model belongs to the technical field of water heating equipment, and particularly discloses a heat exchange sheet, a heat exchanger and gas water heating equipment, a first notch is arranged between two adjacent first heat exchange tube holes on the heat exchange sheet, the first notch is opposite to a second heat exchange tube hole, and the second heat exchange tube hole is opposite to the second heat exchange tube hole. The circle centers of the first heat exchange pipe holes are located on a preset center line, the hole walls of the first heat exchange pipe holes are tangent to a preset tangent line, the diameter of the second heat exchange pipe holes is set as B, the width of the first notches on the preset center line is A, A is larger than or equal to B, and the preset center line serves as the boundary. The width of the first notch located on the upstream of the preset center line is increased in the direction away from the preset center line, the width of the first notch located between the downstream of the preset center line and the upstream of the preset tangent line is not smaller than A, on the preset center line, the distance between the side edge of each first notch and the adjacent first heat exchange pipe hole is C, and C is smaller than or equal to 7 mm. By limiting the shape, the width and the distance C of the first notch, the thermal inertia and the heat storage capacity of the local area of the heat exchange piece are reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of hot water equipment, in particular to a heat exchange fin, a heat exchanger and a gas hot water equipment. Background Art

[0002] The gas hot water equipment generates high-temperature flue gas through the operation of a burner, and transfers the heat energy of the high-temperature flue gas to the water side through a heat exchanger, so that the temperature of the water rises. Among them, the heat exchange between the heat exchanger and the high-temperature flue gas is mainly realized through the heat exchange fins on it, and the heat exchange fins play an important role in the heat exchange efficiency of the heat exchanger.

[0003] In order to meet the heat exchange requirements, the heat exchange fins are usually set to be relatively large in size, especially for the heat exchange fins with multiple rows of heat exchange tube holes. For example Figure 1 shown is a heat exchange fin in the related art. The heat exchange fin includes two rows of heat exchange tube holes arranged staggeredly along the gas flow direction ( Figure 1 the arrow direction in Figure 1 ). In one row of heat exchange tube holes located upstream (close to the burner side, that is, the lower row), a flue gas notch concave inward along the gas flow direction is arranged between any two adjacent heat exchange tube holes. The width of the flue gas notch decreases in a gradually decreasing manner along the gas flow direction. Due to the large resistance, the flue gas flow exchanges heat excessively with the left and right sides of the flue gas notch and the upstream-facing area of the heat exchange tube hole in the upstream heat exchange tube hole facing the flue gas notch, forming a high-temperature area ( the area within the dotted line in

[0004] One of the technical problems solved by the utility model is to provide a heat exchange fin that can effectively solve the problem of excessive heat exchange in a local area of the heat exchange fin caused by local resistance to form a high-temperature area.

[0005] Another technical problem solved by the utility model is to provide a heat exchanger that can effectively solve the problems of large heat inertia and heat storage capacity caused by the existence of a high-temperature area in the heat exchange fin.

[0006] The third technical problem solved by the utility model is to provide a gas hot water equipment that can solve the problem of the temperature rise at the stop of the water caused by the large heat inertia and heat storage capacity of the heat exchange fin.

[0007] The above first technical problem is solved by the following technical solutions:

[0008] A heat exchange fin, comprising a substrate, the substrate having an air inlet end and an air outlet end along the air flow direction, a first heat exchange tube hole and a second heat exchange tube hole being arranged at intervals along the air flow direction on the substrate, a plurality of the first heat exchange tube holes and the second heat exchange tube holes being arranged along the length direction of the substrate and the first heat exchange tube holes and the second heat exchange tube holes being arranged staggeredly, a first notch being arranged between two adjacent first heat exchange tube holes at the air inlet end of the substrate, the first notch facing the second heat exchange tube hole, and / or a second notch being arranged at the air outlet end of the substrate, the second notch facing the first heat exchange tube hole, the centers of the first heat exchange tube holes being located on a preset center line and the side hole walls of the first heat exchange tube holes facing the second heat exchange tube holes being tangent to a preset tangent line, assuming the diameter of the second heat exchange tube hole is B, the width of the first notch on the preset center line is A, A≥B, and with the preset center line as the boundary, the width of the first notch upstream of the preset center line increases in the direction away from the preset center line, the width of the first notch between the downstream of the preset center line and the upstream of the preset tangent line is not less than A, on the preset center line, the distance between the side edge of the first notch and the adjacent first heat exchange tube hole is C, C≤7mm.

[0009] The heat exchange fin of the present utility model has the following beneficial effects compared with the background art:

[0010] The above heat exchange fin defines the shape of the side edge of the first notch by changing the width of each part of the first notch, then limits the width range of each part of the first notch by defining A≥B, and at the same time limits the distance between the side edge of the first notch and the adjacent first heat exchange tube hole on the preset center line, effectively reducing the regional resistance on both sides of the first notch along the length direction of the substrate, and further reducing the possibility of overheating in the high-temperature area formed by excessive heat exchange on both sides of the first notch along the length direction of the substrate.

[0011] In one embodiment, A≤5 / 3B.

[0012] In one embodiment, the edge of the first notch corresponding to the second heat exchange tube hole is arranged as a circular arc coaxial with the second heat exchange tube hole; and / or, the minimum distance D between the second heat exchange tube hole and the first notch is D≤7mm.

[0013] In one embodiment, the heat exchange fin further includes a first flow disturbance structure, which is disposed between adjacent first heat exchange tube holes and second heat exchange tube holes and downstream of the preset tangent line. The first flow disturbance structure is arranged around the second heat exchange tube hole along the air flow direction. The first flow disturbance structure cooperates with the first heat exchange tube hole and the second heat exchange tube hole to form a first air flow channel and a second air flow channel; and / or, the heat exchange fin further includes a second notch, which is disposed at the exhaust end of the substrate and is disposed opposite to the first heat exchange tube hole.

[0014] In one embodiment, the width of the second air flow channel decreases along the air flow direction.

[0015] In one embodiment, let the inlet width of the first air flow channel be E, and the inlet width of the second air flow channel be F, where 1 < E / F ≤ 1.6 or 1 < F / E ≤ 1.6.

[0016] In one embodiment, the shortest distance between the first flow disturbance structure and the edge of the first notch is G, where 0.5 mm ≤ G ≤ 2 mm; and / or, the minimum distance H between the side edge of the second notch and the first flow disturbance structure is ≤ 2 mm.

[0017] In one embodiment, the exhaust end of the substrate is turned over and provided with a guiding hem, and an exhaust port is provided on the guiding hem.

[0018] In one embodiment, the heat exchange fin further includes a first flow disturbance structure disposed between the first heat exchange tube hole and the second heat exchange tube hole. The first flow disturbance structure is arranged around the second heat exchange tube hole along the air flow direction. The exhaust port includes a first exhaust port corresponding to the first heat exchange tube hole, a second exhaust port corresponding to the second heat exchange tube hole, and a third exhaust port corresponding to the first flow disturbance structure. The length of the first exhaust port is between 2 mm and 5 mm, the length of the second exhaust port is between 2 mm and 8 mm, and the length of the third exhaust port is between 3 mm and 10 mm.

[0019] The above second technical problem is solved by the following technical solutions:

[0020] A heat exchanger includes heat exchange tubes and the heat exchange fins according to any of the above embodiments. The heat exchange fins are stacked, and a plurality of the heat exchange tubes are penetrated through the first heat exchange tube holes and the second heat exchange tube holes.

[0021] The heat exchanger of the present invention has the following beneficial effects compared with the background art: there are fewer high-temperature areas, and the thermal inertia and heat storage capacity are low.

[0022] The above third technical problem is solved by the following technical solution:

[0023] A gas water heating device includes a burner and the heat exchanger described in the above embodiment, and the burner is arranged at the air inlet end of the heat exchanger.

[0024] Compared with the background art, the gas water heating device of the present utility model has the following beneficial effects:

[0025] The gas water heating device has low thermal inertia and heat storage capacity, which can reduce the possibility of the phenomenon of water temperature rise during the boiling of water by users. Description of the Drawings

[0026] Figure 1 It is a schematic structural diagram of a heat exchange fin provided in the related art;

[0027] Figure 2 It is a schematic structural diagram of a heat exchange fin provided in an embodiment of the present utility model.

[0028] Label Description:

[0029] 1. Substrate; 2. First heat exchange tube hole; 3. Second heat exchange tube hole; 4. First notch; 5. First flow disturbing structure; 6. Second flow disturbing structure; 7. Second notch; 8. Guiding flanging; 9. First exhaust port; 10. Second exhaust port; 11. Third exhaust port; l. Preset center line; m. Preset tangent line. Detailed Embodiments

[0030] Next, the technical solutions in the embodiments of the present application will be clearly and completely described with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present application.

[0031] In the description of the present application, it should be understood that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation to the present application.

[0032] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of this application, unless otherwise specified, the meaning of "a plurality" is two or more.

[0033] In the description of this application, it should be noted that, unless otherwise clearly specified and defined, the terms "installed", "connected", and "joined" should be understood 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 components. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0034] Reference Figure 2 As shown, in an embodiment of the present utility model, a heat exchange fin is provided, including a substrate 1. The substrate 1 has an air inlet end and an air outlet end along the air flow direction (as Figure 2 shown, the X direction in the figure is the gas flow direction, the upstream of the X direction is the air inlet end, and the downstream of the X direction is the air outlet end). Along the air flow direction on the substrate 1, a first heat exchange tube hole 2 and a second heat exchange tube hole 3 are arranged at intervals for installing heat exchange tubes. Both the first heat exchange tube hole 2 and the second heat exchange tube hole 3 are arranged in a plurality along the length direction of the substrate 1 ( Figure 2 the Y direction shown in the figure, the Y direction is perpendicular to the X direction), and the plurality of first heat exchange tube holes 2 and the plurality of second heat exchange tube holes 3 are arranged in an alternating manner. At the air inlet end of the substrate 1, a first notch 4 recessed inward along the air flow direction is provided between two adjacent first heat exchange tube holes 2, and the first notch 4 faces the second heat exchange tube hole 3.

[0035] The centers of the first heat exchange tube holes 2 are all located on a preset center line l, and the side hole walls of the first heat exchange tube holes 2 facing the second heat exchange tube holes 3 are all tangent to a preset tangent line m. To solve the problem that heat is likely to accumulate on both sides of the first notch 4 along the length direction of the substrate 1, let the diameter of the second heat exchange tube hole 3 be B, and the width of the first notch 4 on the preset center line l be A, A≥B. And taking the preset center line l as the boundary, the width of the first notch 4 upstream of the preset center line l increases in the direction away from the preset center line l, the width of the first notch 4 between the downstream of the preset center line l and the upstream of the preset tangent line m is not less than A, and on the preset center line l, the distance between the side edge of the first notch 4 and the adjacent first heat exchange tube hole 2 is C, C≤7mm.

[0036] The heat exchanger plate is defined by changing the width of each part of the first notch 4 to define the side edge shape of the first notch 4, and then by defining A≥B to define the width range of each part of the first notch 4. It can be understood that the larger A is, the smaller the resistance to the flue gas flow is, and the less likely it is that heat will accumulate on both sides of the first notch 4 of the heat exchanger plate along the length direction of the substrate 1. Of course, the accumulation of heat is also related to the size of C. The smaller C is, the less likely it is that heat will accumulate on both sides of the first notch 4 along the length direction of the substrate 1. Therefore, there must be a limit range. When both A and C are within the limit range, it is not easy for high-temperature areas to form on both sides of the first notch 4 along the length direction of the substrate 1.

[0037] In order to verify this limit, the inventors of the present application used simulation software to simulate the heat exchange conditions of the heat exchanger and obtained the following Tables 1 and 2:

[0038] Table 1

[0039]

[0040] Table 2

[0041]

[0042] It can be seen from Table 1 and Table 2 that when A ≥ B and C = 2 mm, the first notch 4 is located on both sides of the substrate 1 along the length direction. Figure 2 The maximum temperature of the middle S zone is 255℃, and the smoke resistance is 17Pa; when A≥B and C=4mm, the maximum temperature of the S zone is 270℃, and the smoke resistance is 21Pa; when A≥B and C=7mm, the maximum temperature of the S zone is 280℃, and the smoke resistance is 23Pa; when A≥B and C=9mm, the maximum temperature of the S zone is 297℃, and the smoke resistance is 27Pa; when A<B, the maximum temperature of the S zone is greater than 285℃, and the smoke resistance is greater than 25Pa. Generally, the temperature is below 290℃, and the resistance is controlled below 25Pa, which is considered to be low in heat storage and thermal inertia. Therefore, when A and C are A≥B, and C≤7mm, the problem of heat easily accumulating on both sides of the first notch 4 along the length direction of the substrate 1 to form a high temperature zone can be solved. It should be noted that the S zone is located between two adjacent first heat exchange tube holes 2 and extends in the upstream direction of the preset tangent l with the preset tangent l as the boundary.

[0043] It can be understood that due to the processing technology problem of the first heat exchange tube hole 2 (the first heat exchange tube hole 2 is usually integrally stamped with the substrate 1), if C is too small, it is easy to have the bad phenomenon of stamping deformation, reducing the yield rate. Therefore, in one embodiment, C≥2mm, that is, C can take values between 2mm and 7mm, such as 2mm, 4mm, 7mm, etc. As for the specific value, it can be determined according to the emphasis between heat exchange efficiency and heat storage capacity. When higher heat exchange efficiency is required, C can take the value of 7mm or a value smaller than the difference between 2mm and 7mm. On the contrary, it can take the value of 2mm or a value smaller than the difference between 7mm and 2mm.

[0044] When A is too large, it will affect the flue gas gathering effect and heat exchange efficiency. In one embodiment, A≤5 / 3B. At this time, through the simulation software to simulate the heat exchange condition of the heat exchange fin, the temperature on both sides of the length of the substrate 1 along the first notch 4≥250°C, that is, when A takes values in B≤A≤5 / 3B, the relative balance between the flue gas passing efficiency (the flue gas passing efficiency is high when the resistance is low) and the heat exchange efficiency can be achieved.

[0045] Reference Figure 2 In an embodiment shown in the reference, the first notch 4 is bounded by a preset center line l, and the side edge of the first notch 4 located upstream of the preset center line l is set as a circular arc coaxial with the first heat exchange tube hole 2, so as to improve the uniformity of heat exchange between the flue gas flow and the heat exchange tubes inserted in the first heat exchange tube hole 2, and at the same time reduce the possibility of forming a high-temperature area in the upstream area of the first heat exchange tube hole 2 facing the flow. In other embodiments, bounded by the preset center line l, the side edge of the first notch 4 located upstream of the preset center line l can also be set as an elliptical arc or a broken line.

[0046] In order to reasonably distribute the flue gas flow so that it can evenly flow through each area of the heat exchange fins, and at the same time, in order to enable the flue gas flow to fully contact the heat exchange tubes in the first heat exchange tube holes 2 and the second heat exchange tube holes 3 to improve the heat exchange efficiency, a first flow disturbing structure 5 is further provided between adjacent first heat exchange tube holes 2 and second heat exchange tube holes 3. The first flow disturbing structure 5 is located downstream of the preset tangent line m. The first flow disturbing structure 5 cooperates with the first heat exchange tube holes 2 and the second heat exchange tube holes 3 to form a first gas flow channel and a second gas flow channel. The flue gas flow is divided into two strands under the action of the first flow disturbing structure 5. One of the flue gas flows enters the first gas flow channel and flows along the outer edge of the first heat exchange tube hole 2 towards the exhaust end of the substrate 1, and the other gas flow enters the second gas flow channel and flows along the outer edge of the second heat exchange tube hole 3 towards the exhaust end of the substrate 1. It should be noted that the first flow disturbing structure 5 is arranged around the second heat exchange tube hole 3 along the gas flow direction, so that the length of the second gas flow channel along the gas flow direction is relatively long, which is beneficial to guiding the flue gas flow to flow around the second heat exchange tube hole 3 and then discharging from the exhaust end of the substrate 1. Specifically, the height of one end of the first flow disturbing structure 5 close to the exhaust end is higher than the height of the second heat exchange tube hole 3, so that the flue gas flow can fully flow around the second heat exchange tube hole 3 and achieve full heat exchange with the heat exchange tube inserted in the second heat exchange tube hole 3.

[0047] In one embodiment, the first flow disturbing structure 5 includes a plurality of flanging holes arranged at intervals along the gas flow direction. The flanging holes can guide the flow direction of the flue gas flow while avoiding the formation of high-temperature areas, and can also reduce the weight of the heat exchange fins, thereby saving costs. The sizes of the plurality of flanging holes can be the same or different, and no specific limitation is made here, but the size of the flanging hole is significantly smaller than the size of the second heat exchange tube hole 3 to avoid affecting the flow direction of the flue gas to the second heat exchange tube hole 3.

[0048] In other embodiments, the first flow disturbing structure 5 can also be a convex bulge protruding from the substrate 1. The convex bulge serving as the first flow disturbing structure 5 can be a strip extending along the gas flow direction or a plurality of convex bulges arranged at intervals along the gas flow direction.

[0049] Optionally, the width of the second gas flow channel shows a decreasing trend along the gas flow direction, so that the flue gas resistance on both sides of the second heat exchange tube hole 3 gradually increases, thereby causing the flue gas to gather around the second heat exchange tube hole 3 and further enhancing the heat exchange effect. For example, when the first flow disturbing structure 5 includes a plurality of flanging holes, the width of the second gas flow channel refers to the minimum distance between one side of any flanging hole close to the second heat exchange tube hole 3 and the second heat exchange tube hole 3.

[0050] Let the inlet width of the first gas flow channel be E, and the inlet width of the second gas flow channel be F. 1 < E / F ≤ 1.6 or 1 < F / E ≤ 1.6 (depending on the actual designed pipeline of the gas water heater, the deviation position of the first spoiler structure 5 is also different), so as to achieve a reasonable flue gas flow distribution, thereby improving the heat exchange efficiency, while avoiding excessive heat exchange in a certain area, which may lead to overheating of the area, effectively reducing the overall temperature of the heat exchange fins, and thus reducing the thermal inertia and heat storage of the heat exchange fins. Taking the first spoiler structure 5 including a plurality of flanging holes arranged at intervals along the gas flow direction as an example, the inlet width of the first gas flow channel refers to the minimum distance between the flanging hole closest to the air inlet end of the substrate 1 and the first heat exchange tube hole 2, and the inlet width of the second gas flow channel refers to the minimum distance between the flanging hole closest to the air inlet end of the substrate 1 and the second heat exchange tube hole 3.

[0051] In one embodiment, the number of the second heat exchange tube holes 3 is less than the number of the first heat exchange tube holes 2. For example, in the embodiment shown as Figure 2 In the embodiment shown, there are three first heat exchange tube holes 2, two second heat exchange tube holes 3, and two first notches 4 are correspondingly arranged. In another embodiment, there may be four first heat exchange tube holes 2 and three second heat exchange tube holes 3, and three first notches 4 are correspondingly arranged. The number of the first heat exchange tube holes 2 being less than the number of the second heat exchange tube holes 3 can make the flue gas converge towards the center of the substrate 1 when flowing towards the exhaust end of the substrate 1, avoiding the flue gas being too concentrated at the two ends of the length of the substrate 1, thereby reducing the temperature of the water heater housing when the heat exchange fins are used for the water heater and preventing scalding of the human body.

[0052] In one embodiment, in order to further reduce the heat accumulation at both ends of the length of the substrate 1, the heat exchange fin further includes a second spoiler structure 6. The second spoiler structure 6 is arranged on the outer periphery of two first heat exchange tube holes 2 located on both sides of the length of the substrate 1, so as to increase the resistance on both sides of the length of the substrate 1 and make the flue gas gather towards the middle position of the substrate 1.

[0053] Specifically, the second spoiler structure 6 includes a plurality of protruding bumps. For example, there are 8 second spoiler structures 6, and 4 bumps are respectively arranged on the outer periphery of two first heat exchange tube holes 2 located on both sides of the length of the substrate 1. Among them, two bumps are arranged on the upstream side of the first heat exchange tube hole 2 and close to the edge on one side of the length of the substrate 1, and the other two bumps are arranged on the side of the first heat exchange tube hole 2 close to the first notch 4.

[0054] On the basis of setting the second spoiler structure 6 and the first spoiler structure 5, one side edge of the first notch 4 corresponding to the second spoiler structure 6 extends in the direction of the preset tangent line m with the preset center line l as the boundary, while one side edge of the first notch 4 not corresponding to the second spoiler structure 6 is set as an arc segment protruding outward toward the adjacent first heat exchange tube hole 2 with the preset center line l as the boundary, so as to be connected to the edge of the first spoiler structure 5 corresponding to the first notch 4. The edges of the first notch 4 corresponding to the parts of the first spoiler structure 5 located on both sides of the second heat exchange tube hole 3 are set in a flared shape to guide the flue gas to flow through the second heat exchange tube hole 3.

[0055] In one embodiment, the shortest distance G between the first spoiler structure 5 and the edge of the first notch 4 satisfies 0.5 mm ≤ G ≤ 2 mm. On the basis of meeting the processing method of integral stamping forming of the first spoiler structure 5, heat accumulation on the side of the first spoiler structure 5 close to the first notch 4 is avoided as much as possible, and the possibility of forming a high-temperature area is further reduced.

[0056] In one embodiment, in order to avoid Figure 1 as shown in the figure, a high-temperature area is formed in the upstream side area of the second heat exchange tube hole 3. The edge of the first notch 4 corresponding to the second heat exchange tube hole 3 is in a circular arc shape coaxial with the second heat exchange tube hole 3. Further, the distance D between the second heat exchange tube hole 3 and the edge of the first notch 4 satisfies D ≤ 7 mm. It can be understood that in order to reduce the processing difficulty of the heat exchange tubes, the first heat exchange tube hole 2 and the second heat exchange tube hole 3 have the same size. Affected by the processing technology of the second heat exchange tube hole 3, D ≥ 2 mm.

[0057] In one embodiment, both the first heat exchange tube hole 2 and the second heat exchange tube hole 3 are also flanged holes, and the protruding direction is the same as the protruding direction of the first spoiler structure 5, so that the flue gas can flow better around the heat exchange tubes. Moreover, setting them as flanged holes can also increase the contact area between the heat exchange tubes and the heat exchange fins, which is beneficial to the welding and fixing between the heat exchange tubes and the substrate 1.

[0058] In one embodiment, a second notch 7 recessed toward the intake end of the substrate 1 is further provided at the exhaust end of the substrate 1 to further reduce the high-temperature area, and at the same time reduce the weight of the heat exchange fins and save materials. Specifically, the second notch 7 is provided directly opposite the first heat exchange tube hole 2.

[0059] In one embodiment, the minimum distance H between the side edge of the second notch 7 and the first spoiler structure 5 satisfies H ≤ 2 mm to further reduce the volume of the heat exchange fins, and reduce the thermal inertia and heat storage capacity of the heat exchange fins. Similarly, limited by the process, 0.5 mm ≤ H.

[0060] In order to enable the flue gas flow to converge around the heat exchange tubes to enhance heat transfer, in one embodiment, a guiding hem 8 extending along the edge of the exhaust end is provided at the exhaust end of the substrate 1. The guiding hem 8 can be integrally formed with the substrate 1 by bending the exhaust end of the substrate 1. The guiding hem 8 can guide the flue gas flow to flow around the heat exchange tubes. It can be understood that in order to enable the flue gas to be smoothly discharged from the exhaust end, an exhaust port is provided on the guiding hem 8.

[0061] Corresponding to the first heat exchange tube hole 2, the second heat exchange tube hole 3, and the first flow disturbing structure 5, the exhaust port includes a first exhaust port 9, a second exhaust port 10, and a third exhaust port 11. Among them, the first exhaust port 9 is located in the second notch 7 and is directly opposite to the first heat exchange tube hole 2. The length of the first exhaust port 9 is between 2 mm and 5 mm. The second exhaust port 10 is directly opposite to the second heat exchange tube hole 3. The length of the second exhaust port 10 is between 2 mm and 8 mm. The third exhaust port 11 is inclined corresponding to the first flow disturbing structure 5. The length of the third exhaust port 11 is between 3 mm and 10 mm.

[0062] In an embodiment of the present invention, a heat exchanger is further proposed, which includes heat exchange tubes and the heat exchange fins in any of the above embodiments. The heat exchange fins are stacked, and a plurality of heat exchange tubes are disposed through the first heat exchange tube hole 2 and the second heat exchange tube hole 3.

[0063] The above heat exchanger adopts the above heat exchange fins, which can effectively reduce the local area resistance of the heat exchange fins, reduce the high temperature area and lower the temperature of the high temperature area, thereby reducing the thermal inertia and heat storage capacity.

[0064] In an embodiment of the present invention, a gas water heating device is further proposed, which includes a burner and the above heat exchanger. The burner is disposed at the intake end of the heat exchanger. Due to the inclusion of the above heat exchanger, the gas water heating device has all the beneficial effects of the heat exchanger. Moreover, due to the low thermal inertia and heat storage capacity of the heat exchanger, when the user uses water for the second time, it is not easy to generate the problem of stop water temperature rise or the problem of stop water temperature rise is not obvious.

[0065] In the specific content of the above specific implementation manner, each technical feature can be combined arbitrarily without contradiction. For the sake of concise description, not all possible combinations of the above technical features are described. However, as long as the combination of these technical features does not exist in contradiction, it should be considered as the scope recorded in this specification.

[0066] The specific content of the above specific embodiments only expresses several embodiments of the present utility model. Its description is relatively specific and detailed, but it should not be construed as a limitation on the scope of the patent of the present utility model. It should be noted that for those of ordinary skill in the art, without departing from the concept of the present utility model, several modifications and improvements can still be made, and these all belong to the protection scope of the present utility model. Therefore, the protection scope of the patent of the present utility model shall be subject to the appended claims.

Claims

1. A heat exchange plate, comprising a substrate (1), wherein the substrate (1) has an air inlet end and an air outlet end along an airflow direction, wherein a first heat exchange tube hole (2) and a second heat exchange tube hole (3) are arranged at intervals along the airflow direction on the substrate (1), wherein a plurality of the first heat exchange tube holes (2) and a plurality of the second heat exchange tube holes (3) are arranged along the length direction of the substrate (1), and the plurality of the first heat exchange tube holes (2) and the plurality of the second heat exchange tube holes (3) are arranged alternately, wherein the air inlet end of the substrate (1) is provided with a first notch (4) between two adjacent first heat exchange tube holes (2), and the first notch (4) is directly opposite to the second heat exchange tube hole (3), and wherein: The centers of the circles of the first heat exchange tube holes (2) are all located on the preset center line (l) and the hole walls of the first heat exchange tube holes (2) facing the second heat exchange tube holes (3) are all tangent to the preset tangent line (m). The diameter of the second heat exchange tube hole (3) is assumed to be B. The width of the first notch (4) on the preset center line (l) is A, A≥B, and with the preset center line (l) as the boundary, the width of the first notch (4) located upstream of the preset center line (l) increases in a direction away from the preset center line (l), and the width of the first notch (4) located between the downstream of the preset center line (l) and the upstream of the preset tangent line (m) is not less than A. On the preset center line (l), the distance between the side edge of the first notch (4) and the adjacent first heat exchange tube hole (2) is C, C≤7mm.

2. The heat exchange plate according to claim 1, characterized in that: A≤5 / 3B.

3. The heat exchange plate according to claim 1, characterized in that: The edge of the first notch (4) corresponding to the second heat exchange tube hole (3) is arranged to be in an arc shape coaxial with the second heat exchange tube hole (3); And / or, the minimum distance D between the second heat exchange tube hole (3) and the first notch (4) is ≤7 mm.

4. The heat exchange plate according to any one of claims 1 to 3, characterized in that: The heat exchange plate further comprises a first spoiler structure (5), the first spoiler structure (5) being arranged between the adjacent first heat exchange tube hole (2) and the second heat exchange tube hole (3) and being located downstream of the preset tangent line (m), the first spoiler structure (5) being arranged around the second heat exchange tube hole (3) along the flow direction of the airflow, the first spoiler structure (5) cooperating with the first heat exchange tube hole (2) and the second heat exchange tube hole (3) to form a first airflow channel and a second airflow channel; And / or, the heat exchange plate further comprises a second notch (7), the second notch (7) being arranged at the exhaust end of the substrate (1), and the second notch (7) being arranged opposite to the first heat exchange tube hole (2).

5. The heat exchange plate according to claim 4, characterized in that: The width of the second air flow channel decreases along the air flow direction.

6. The heat exchange plate according to claim 4, characterized in that The inlet width of the first air flow channel is E, the inlet width of the second air flow channel is F, 1<E / F≤1.6 or 1<F / E≤1.

6.

7. The heat exchange plate according to claim 4, characterized in that: The shortest distance between the first spoiler structure (5) and the edge of the first notch (4) is G, 0.5mm≤G≤2mm; and / or the shortest distance between the side edge of the second notch (7) and the first spoiler structure (5) is H≤2mm.

8. The heat exchange plate according to any one of claims 1 to 3, characterized in that: The exhaust end of the base plate (1) is folded to provide a guide folded edge (8), and an exhaust port is provided on the guide folded edge (8).

9. The heat exchange plate according to claim 8, characterized in that: The heat exchange plate further comprises a first spoiler structure (5) arranged between the first heat exchange tube hole (2) and the second heat exchange tube hole (3); the first spoiler structure (5) is arranged around the second heat exchange tube hole (3) along the flow direction of the airflow; the exhaust port comprises a first exhaust port (9) arranged corresponding to the first heat exchange tube hole (2), a second exhaust port (10) arranged corresponding to the second heat exchange tube hole (3), and a third exhaust port (11) arranged corresponding to the first spoiler structure (5); the length of the first exhaust port (9) is between 2 mm and 5 mm, the length of the second exhaust port (10) is between 2 mm and 8 mm, and the length of the third exhaust port (11) is between 3 mm and 10 mm.

10. A heat exchanger, characterized in that It comprises a heat exchange tube and the heat exchange plate according to any one of claims 1 to 9, wherein the heat exchange plates are stacked, and a plurality of the heat exchange tubes are penetrated in the first heat exchange tube hole (2) and the second heat exchange tube hole (3).

11. Gas water heater, characterized in that: The invention comprises a burner and the heat exchanger as claimed in claim 10, wherein the burner is arranged at the air inlet end of the heat exchanger.

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