Heat exchange sheet, heat exchanger and gas water heater

Abstract

The utility model belongs to the technical field of heat supply, and particularly discloses a heat exchange sheet, a heat exchanger and a gas water heater. The heat sheet comprises a substrate, a plurality of first turnups and a plurality of second turnups. A plurality of heat exchange pipe holes are formed in the base plate at intervals in the length direction of the base plate, the first turnups are arranged on the base plate, the first turnups are arranged on the right downstream portions of at least part of the heat exchange pipe holes in the overall circulation direction of smoke, the second turnups are arranged on the base plate, and the right downstream portions between any two adjacent heat exchange pipe holes are arranged in the overall circulation direction of the smoke. The projection of the first turned-over edge and the projection of the second turned-over edge partially coincide in the overall flowing direction of the smoke. The heat exchange sheet provided by the utility model has higher heat exchange efficiency, and meanwhile, the combustion efficiency of the gas water heater comprising the heat exchange sheet provided by the embodiment of the utility model is higher, so that the energy loss is further reduced.

Description

Technical Field

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

[0002] In a gas water heater, a heat exchanger is usually used to receive the high-temperature flue gas generated by the combustion of gas in the gas water heater, so that the high-temperature flue gas heats the water passing through the inside of the heat exchanger. Specifically, the heat exchanger usually includes a plurality of heat exchange fins and heat exchange tubes connected to the plurality of heat exchange fins. First, the high-temperature flue gas is heat-exchanged with the heat exchange fins and the heat exchange tubes, and then the heat exchange fins are heat-exchanged with the heat exchange tubes and the water in the heat exchange tubes to heat the water in the heat exchange tubes.

[0003] However, due to the limitation of the internal space of the gas water heater, the heat exchange area of the heat exchange fins is limited, and the flow velocity of the high-temperature flue gas is relatively fast, resulting in low heat exchange efficiency and high heat loss, causing energy waste. Summary of the Utility Model

[0004] One of the technical problems to be solved by the utility model is to provide a heat exchange fin which can effectively improve the heat exchange efficiency of the heat exchange fin and reduce energy loss.

[0005] Another technical problem to be solved by the utility model is to provide a heat exchanger which can improve the heat exchange performance of the heat exchanger by using the aforementioned heat exchange fin with high heat exchange efficiency.

[0006] Another technical problem to be solved by the utility model is to provide a gas water heater which can improve the overall heat exchange efficiency of the gas water heater and reduce energy waste by using the aforementioned heat exchanger with good heat exchange performance.

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

[0008] A heat exchange fin includes:

[0009] A substrate, along the length direction of the substrate, a plurality of heat exchange tube holes are arranged at intervals on the substrate:

[0010] A plurality of first flanges, the first flanges are arranged on the substrate, and at least part of the first flanges are arranged directly downstream of the heat exchange tube holes along the overall flow direction of the flue gas; and

[0011] A plurality of second flanges, the second flanges are arranged on the substrate, and the second flanges are arranged directly downstream of any two adjacent heat exchange tube holes along the overall flow direction of the flue gas. In the projection plane perpendicular to the overall flow direction of the flue gas, the positive projection of the first flange and the positive projection of the second flange partially overlap;

[0012] Wherein, both the first flanging and the second flanging are strip-shaped, and the first flanging is provided with an opening penetrating through two opposite surfaces along the overall flow direction of the flue gas.

[0013] Compared with the background art, the heat exchange fin of the present utility model has the following beneficial effects:

[0014] By providing the first flanging and the second flanging on the substrate, and along the overall flow direction of the flue gas, making the first flanging located directly downstream of the heat exchange tube hole, making the second flanging located directly downstream between any two adjacent heat exchange tube holes, and making the projection of the first flanging partially coincide with the projection of the second flanging, it is possible to cooperate the first flanging and the second flanging to block the flowing high-temperature flue gas, so as to lengthen the time that the high-temperature flue gas stays near the heat exchange tube hole, and further improve the heat exchange efficiency between the high-temperature flue gas and the heat exchange fin. At the same time, by providing an opening penetrating through two opposite surfaces along the overall flow direction of the flue gas on the first flanging located directly downstream of the heat exchange tube hole along the overall flow direction of the flue gas, the blocked flue gas can be discharged, so that on the one hand, the flue gas can be guided to flow along the first flanging and flow out from the opening, so that the flue gas can flow around the outer periphery of the heat exchange tube hole along the first flanging to improve the heat exchange efficiency at the heat exchange tube hole, and on the other hand, a relatively reasonable flue gas flow can be ensured, so that sufficient oxygen can enter the gas water heater for combustion. In other words, the heat exchange fin provided by the present utility model can have a high heat exchange efficiency while having a high combustion efficiency of the gas water heater to further reduce energy loss.

[0015] In addition, by making the first flanging provided at least partially directly downstream of the heat exchange tube hole, making the second flanging provided directly downstream between any two adjacent heat exchange tube holes, and along the overall flow direction of the flue gas, the projection of the first flanging partially coincides with the projection of the second flanging. In other words, by alternately arranging the first flanging and the second flanging and staggering them along the overall flow direction of the flue gas, it is possible to better turbulize the flue gas, so as to guide part of the flue gas to flow out from the gap between the first flanging and the second flanging, and then a relatively reasonable flue gas flow can be achieved, so that sufficient oxygen can enter the gas water heater for combustion, so that the combustion efficiency of the gas water heater is relatively high, and further energy loss can be reduced.

[0016] In one embodiment, the first flanging is an arc-shaped strip flanging, and the first flanging bends and protrudes towards the direction close to the corresponding heat exchange tube hole, or the first flanging bends and protrudes towards the direction away from the corresponding heat exchange tube hole;

[0017] And / or, along the overall flow direction of the flue gas, the minimum distance between the first flanging and the center of the heat exchange tube hole located directly upstream of itself is h1, and 10mm ≤ h1 ≤ 12mm.

[0018] In one embodiment, along the overall flow direction of the flue gas, the opening is located directly downstream of the heat exchange tube hole; and / or,

[0019] Along the length direction of the substrate, the opening has a dimension w1, where 4 mm ≤ w1 ≤ 5 mm.

[0020] In one embodiment, along the overall flow direction of the flue gas, the second flanging is located on the downstream side of the first flanging, or the second flanging is located on the upstream side of the first flanging.

[0021] In one embodiment, along the length direction of the substrate, the second flanging has a dimension w2, the center distance between two adjacent heat exchange tube holes is w3, and the spacing between two adjacent heat exchange tube holes is w4, where w4 < w2 < w3.

[0022] In one embodiment, the heat exchange fin further includes a third flanging, the third flanging is in the shape of an annular cylinder, and the third flanging is arranged on the substrate and located between two adjacent heat exchange tube holes and the second flanging.

[0023] In one embodiment, along the overall flow direction of the flue gas, the distance between the center point of the third flanging and the center of the heat exchange tube hole is h2, where 6 mm ≤ h2 ≤ 7 mm; and / or,

[0024] The spacing between the third flanging and the adjacent heat exchange tube hole is d, where 4 mm ≤ d ≤ 5 mm.

[0025] In one embodiment, the heat exchange fin further includes a plurality of first convex bumps, the first convex bumps are arranged on the substrate, and the first convex bumps are spaced at least on one side along the length direction of the substrate of the first flanging; and / or,

[0026] The heat exchange fin further includes a plurality of second convex bumps, the second convex bumps are arranged on the substrate, and a plurality of the second convex bumps are spaced and circumferentially arranged around at least the outer periphery of the side of the heat exchange tube hole facing away from the first flanging; and / or,

[0027] The heat exchange fin further includes an annular flanging group, the annular flanging group includes two annular cylinder-shaped fourth flangings spaced along the length direction of the substrate, and for the heat exchange tube hole closest to the edge of the substrate along the length direction of the substrate, the annular flanging group is located downstream of the heat exchange tube hole along the overall flow direction of the flue gas.

[0028] The above second technical problem is solved by the following technical solutions:

[0029] A heat exchanger includes: heat exchange tubes and a plurality of heat exchange fins as provided in the foregoing technical solution. The plurality of heat exchange fins are arranged at intervals in a direction perpendicular to the plate surface of the substrate, and the plurality of heat exchange tubes are inserted into the heat exchange tube holes of the heat exchange fins.

[0030] Compared with the background art, the heat exchanger of the present utility model has the following beneficial effects:

[0031] By using the foregoing heat exchange fins with high heat exchange efficiency, the heat exchange performance and combustion efficiency of the heat exchanger can be improved.

[0032] The above-mentioned third technical problem is solved by the following technical solution:

[0033] A gas water heater includes: a water inlet pipe, a water outlet pipe, and a heat exchanger as provided in the foregoing technical solution. The water inlet pipe and the water outlet pipe are respectively communicated with two ends of the heat exchange tube.

[0034] Compared with the background art, the gas water heater of the present utility model has the following beneficial effects:

[0035] By using the foregoing heat exchanger with good heat exchange performance and combustion efficiency, the overall heat exchange efficiency and combustion efficiency of the gas water heater can be improved, and energy waste can be reduced. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] Figure 1 It is a three-dimensional structure schematic diagram of the heat exchange fin provided by the first embodiment of the present utility model;

[0037] Figure 2 It is a front view structure schematic diagram of the heat exchange fin (indicating the local flow direction of the flue gas) provided by the first embodiment of the present utility model;

[0038] Figure 3 It is a front view structure schematic diagram of the heat exchange fin provided by the first embodiment of the present utility model;

[0039] Figure 4 It is a three-dimensional structure schematic diagram of the heat exchange fin provided by the second embodiment of the present utility model;

[0040] Figure 5 It is a three-dimensional structure schematic diagram of the heat exchange fin provided by the second embodiment of the present utility model;

[0041] Figure 6 It is a simplified structure schematic diagram of the heat exchanger provided by the embodiment of the present utility model;

[0042] Figure 7 It is a simplified partial structure schematic diagram of the gas water heater provided by the embodiment of the present utility model;

[0043] Label description:

[0044] 1. Gas water heater;

[0045] 11. Heat exchanger;

[0046] 110. Heat exchange fin; 1100. Substrate; 1100a. Heat exchange tube hole; 1101. First flanging; 1101a. Opening; 1102. Second flanging; 1103. Third flanging; 1104. First convex hull; 1105. Second convex hull; 1106. Annular flanging group; 1106a. Fourth flanging;

[0047] 111. Heat exchange tube;

[0048] 12. Water inlet pipe;

[0049] 13. Water outlet pipe. Detailed implementation manners

[0050] Next, the technical solutions in the embodiments of the present application will be clearly and completely described in conjunction with the accompanying 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.

[0051] 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 accompanying 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 therefore cannot be understood as a limitation to the present application.

[0052] The terms "first" and "second" are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present application, unless otherwise stated, the meaning of "a plurality" is two or more.

[0053] In the description of the present application, it should be noted that unless otherwise clearly specified and defined, the terms "installed", "connected", and "coupled" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific circumstances.

[0054] As Figures 1 to 3 shown, this embodiment provides a heat exchange fin 110, including a substrate 1100, a plurality of first flanges 1101, and a plurality of second flanges 1102. Along the length direction S1 of the substrate 1100, a plurality of heat exchange tube holes 1100a are provided at intervals on the substrate 1100. The first flanges 1101 are provided on the substrate 1100. Along the overall flow direction S2 of the flue gas, at least part of the first flanges 1101 are provided directly downstream of the heat exchange tube holes 1100a. The second flanges 1102 are provided on the substrate 1100. Along the overall flow direction S2 of the flue gas, the second flanges 1102 are provided directly downstream between any two adjacent heat exchange tube holes 1100a. In the projection plane perpendicular to the overall flow direction S2, the orthographic projection of the first flange 1101 partially overlaps with the orthographic projection of the second flange 1102;

[0055] Among them, both the first flange 1101 and the second flange 1102 are strip-shaped, and the first flange 1101 is provided with an opening 1101a penetrating through its two opposite surfaces along the overall flow direction S2 of the flue gas.

[0056] By providing a first flange 1101 and a second flange 1102 on the substrate 1100, and along the overall flow direction S2 of the flue gas, positioning the first flange 1101 directly downstream of the heat exchange tube hole 1100a, positioning the second flange 1102 directly downstream between any two adjacent heat exchange tube holes 1100a, and making the projection of the first flange 1101 partially overlap with the projection of the second flange 1102, it is possible to cooperate the first flange 1101 with the second flange 1102 to block the flowing high-temperature flue gas, so as to lengthen the time that the high-temperature flue gas stays near the heat exchange tube hole 1100a, and further improve the heat exchange efficiency between the high-temperature flue gas and the heat exchange fins 110. At the same time, by providing an opening 1101a in the first flange 1101 located directly downstream of the heat exchange tube hole 1100a along the overall flow direction S2 of the flue gas, which penetrates through two opposite surfaces of the first flange 1101 along the overall flow direction S2 of the flue gas, the blocked flue gas can be discharged. On the one hand, it can guide the flue gas to flow along the first flange 1101 and flow out from the opening 1101a, so that the flue gas can flow around the outer periphery of the heat exchange tube hole 1100a along the first flange 1101, to improve the heat exchange efficiency at the heat exchange tube hole 1100a. On the other hand, it can ensure a relatively reasonable flue gas flow, so that a sufficient amount of oxygen can enter the gas water heater for combustion. In other words, the heat exchange fins 110 provided by the present utility model can have a high heat exchange efficiency while enabling the gas water heater including the heat exchange fins 110 of this embodiment to have a high combustion efficiency, so as to further reduce energy loss.

[0057] In addition, by providing the first flange 1101 directly downstream of at least some of the heat exchange tube holes 1100a, providing the second flange 1102 directly downstream between any two adjacent heat exchange tube holes 1100a, and along the overall flow direction S2 of the flue gas, the projection of the first flange 1101 partially overlaps with the projection of the second flange 1102. In other words, the first flange 1101 and the second flange 1102 are alternately and staggeredly arranged along the overall flow direction S2 of the flue gas, which can better achieve the turbulence of the flue gas, so as to guide some of the flue gas to flow out from the gap between the first flange 1101 and the second flange 1102, and then have a relatively reasonable flue gas flow, so that a sufficient amount of oxygen can enter the gas water heater for combustion, enabling the gas water heater to have a high combustion efficiency, so as to further reduce energy loss.

[0058] It should be noted that the "overall flow direction S2 of the flue gas" mentioned above specifically refers to the general direction in which the flue gas flows from one side of the heat exchange fins 110 to the other side as a whole. During the overall flow of the flue gas through the heat exchange fins 110, there will be a situation where the local flow direction of the flue gas forms an angle with the overall flow direction of the flue gas, such as Figure 2 shown Figure 2 where the dotted line and arrow in

[0059] In addition, generally, the overall flow direction S2 of the flue gas forms an angle with the length direction S1 of the substrate 1100. Exemplarily, in this embodiment, the overall flow direction S2 of the flue gas is perpendicular to the length direction S1 of the substrate 1100, as Figures 1 to 3 shown Figures 1 to 3 The coordinates in show the length direction S1 of the substrate 1100 and the overall flow direction S2 of the flue gas.

[0060] The relative position of the second flange 1102 and the first flange 1101 can be flexibly set according to actual space requirements. Specifically, in one embodiment, along the overall flow direction S2 of the flue gas, the second flange 1102 can be located on the downstream side of the first flange 1101. Please refer to Figure 4 , in another embodiment, along the overall flow direction S2 of the flue gas, the second flange 1102 can be located on the upstream side of the first flange 1101.

[0061] In one embodiment, the first flange 1101 is an arc-shaped strip flange, and the first flange 1101 bends and protrudes toward the corresponding heat exchange tube hole 1100a. Thus, while the first flange 1101 can play a better role in blocking the flue gas, it makes it relatively easy for the flue gas to continue flowing downstream from the opening 1101a in the middle of the first flange 1101 and at both ends of the first flange 1101. That is, it can extend the time of the flue gas located outside the heat exchange tube hole 1100a through the first flange 1101, and can also ensure a relatively reasonable flue gas flow, so that a sufficient amount of oxygen can enter the gas water heater for combustion.

[0062] Please refer to Figure 5 , in one embodiment, the first flange 1101 is an arc-shaped strip flange, and the first flange 1101 bends and protrudes away from the corresponding heat exchange tube hole 1100a. Thus, while the first flange 1101 can play a better role in blocking the flue gas, it makes it relatively easy for the flue gas to continue flowing downstream from the opening 1101a in the middle of the first flange 1101. At this time, the first flange 1101 has a better effect of extending the time of the flue gas located outside the heat exchange tube hole 1100a by blocking the flue gas, and can also ensure a relatively reasonable flue gas flow, so that a sufficient amount of oxygen can enter the gas water heater for combustion.

[0063] At this time, in one embodiment, the first flange 1101 can be an arc-shaped strip flange concentric with the heat exchange tube hole 1100a, so that the first flange 1101 can intermittently cover the outer periphery of part of the heat exchange tube hole 1100a, so as to be able to guide the flue gas to flow more fully on the outer periphery of the part of the heat exchange tube hole 1100a close to the downstream, so as to achieve more efficient heat exchange between the flue gas and the heat exchange tube hole 1100a.

[0064] Please refer to again togetherFigures 1 to 3 Along the overall flow direction S2 of the flue gas, the minimum distance between the first flanging 1101 and the center of the heat exchange tube hole 1100a located directly upstream of itself is h1. When the distance h1 is too small, the blocking force of the first flanging 1101 on the flue gas flowing towards the downstream side of the heat exchange tube hole 1100a is too large, resulting in that it is more difficult for the flue gas to flow around the part of the outer periphery of the heat exchange tube hole 1100a facing the downstream side. Furthermore, the heat exchange efficiency at the position of the heat exchange tube hole 1100a facing the downstream side is relatively low. And because the flue gas flowing towards the downstream side of the heat exchange tube hole 1100a is prone to directly flow towards the opening 1101a of the first flanging 1101, when the distance h1 is too large, the flue gas flowing towards the downstream side of the heat exchange tube hole 1100a is also difficult to flow around the part of the outer periphery of the heat exchange tube hole 1100a facing the downstream side. Therefore, the distance h1 cannot be too small or too large. Based on this, in one embodiment, the distance h1 can satisfy: 10mm ≤ h1 ≤ 12mm. For example, the distance h1 can be: 10mm, 10.2mm, 10.4mm, 10.5mm, 10.6mm, 10.8mm, 11mm, 11.2mm, 11.4mm, 11.5mm, 11.6mm, 11.8mm or 12mm, etc.

[0065] In one embodiment, the first flanging 1101 can be an arc-shaped strip flanging, and the minimum distance h1 between the first flanging 1101 and the center of the heat exchange tube hole 1100a located directly upstream of itself satisfies 10mm ≤ h1 ≤ 12mm, so that the flue gas can circulate more fully around the part of the outer periphery of the heat exchange tube hole 1100a close to the downstream, so as to achieve more efficient heat exchange between the flue gas and the heat exchange tube hole 1100a.

[0066] In one embodiment, the opening 1101a can be a through hole spaced from the side surface of the first flanging 1101 away from the substrate 1100. Thus, part of the structure of the first flanging 1101 is located on the side of the opening 1101a away from the substrate 1100, which can make the structural strength of the first flanging 1101 better.

[0067] In one embodiment, the opening 1101a can be a notch penetrating the side surface of the first flanging 1101 away from the substrate 1100. Thus, the opening area of the opening 1101a can be made larger on the limited surface of the first flanging 1101, so as to improve the smoke exhaust efficiency at the opening 1101a. Furthermore, the flue gas flow rate flowing around the part of the outer periphery of the heat exchange tube hole 1100a close to the downstream can be effectively increased, so as to improve the heat exchange efficiency at the heat exchange tube hole 1100a.

[0068] In one embodiment, one side wall surface of the opening 1101a may also be located on the surface of the substrate 1100, so that the opening area of the opening 1101a can also be made larger on the limited surface of the first flange 1101, so as to improve the smoke exhaust efficiency at the opening 1101a, and further effectively improve the smoke flow rate flowing around the outer periphery of the downstream part of the heat exchange tube hole 1100a, so as to improve the heat exchange efficiency at the heat exchange tube hole 1100a.

[0069] At this time, when, as described in the foregoing embodiment, the opening 1101a is a notch penetrating the side surface of the first flange 1101 away from the substrate 1100, it can be understood that the first flange 1101 is truncated by the opening 1101a into two sections of flanges located on both sides of the opening 1101a respectively.

[0070] In one embodiment, along the overall flow direction S2 of the flue gas, the opening 1101a is located directly downstream of the heat exchange tube hole 1100a, so that the flow rate and flow velocity of the flue gas flowing from both sides of the heat exchange tube hole 1100a in the direction perpendicular to the overall flow direction S2 of the flue gas to the opening 1101a are relatively consistent, and thus the heat exchange efficiency at both sides of the heat exchange tube hole 1100a is relatively balanced.

[0071] Along the length direction S1 of the substrate 1100, the opening 1101a has a dimension w1. The larger the dimension w1 is, the larger the smoke flow path at the opening 1101a is, but the smaller the blocking effect of the first flange 1101 on the flue gas on both sides of the opening 1101a in the direction perpendicular to the overall flow direction S2 of the flue gas is, which is not conducive to making the flue gas flow around the outer periphery of the downstream side of the heat exchange tube hole 1100a. And the smaller the dimension w1 is, the greater the blocking effect of the first flange 1101 on the flue gas on both sides of the opening 1101a in the direction perpendicular to the overall flow direction S2 of the flue gas is, but the smaller the smoke flow path at the opening 1101a is, and the smaller the flow rate of the flue gas that can flow along the outer periphery of the downstream side of the heat exchange tube hole 1100a to the opening 1101a is. Therefore, the dimension w1 cannot be too large or too small. Based on this, in one embodiment, the dimension w1 may satisfy: 4mm ≤ w1 ≤ 5mm. For example, the dimension w1 may be 4mm, 4.1mm, 4.2mm, 4.3mm, 4.4mm, 4.5mm, 4.6mm, 4.7mm, 4.8mm, 4.9mm or 5mm, etc.

[0072] Along the length direction S1 of the substrate 1100, the second flanging 1102 has a dimension w2, the center distance between the centers of two adjacent heat exchange tube holes 1100a is w3, and the distance between two adjacent heat exchange tube holes 1100a is w4. Since the first flanging 1101 is provided directly downstream of the heat exchange tube hole 1100a, in order to avoid an excessive overlapping area between the projection of the first flanging 1101 and the projection of the second flanging 1102 along the overall flow direction S2 of the flue gas, which may instead make it difficult for the flue gas to flow out from the gap between the first flanging 1101 and the second flanging 1102, the dimension w2 can be made smaller than the dimension w3. In order to enable the second flanging 1102 to extend its blocking effect on the flue gas to the outer periphery of the heat exchange tube hole 1100a, the dimension w2 can be made larger than the dimension w4. Based on this, in one embodiment, the dimension w2 can satisfy: w4 < w2 < w3.

[0073] In one embodiment, the heat exchange fin 110 further includes a third flanging 1103. The third flanging 1103 is in the shape of an annular cylinder. The third flanging 1103 is provided on the substrate 1100 and is located between two adjacent heat exchange tube holes 1100a and the second flanging 1102. In other words, along the overall flow direction S2 of the flue gas, the third flanging 1103 is located on the downstream side of the center of the heat exchange tube hole 1100a and on the upstream side of the second flanging 1102. By providing the third flanging 1103, the flow of the flue gas can be further blocked from the downstream side of two adjacent heat exchange tube holes 1100a, so that more flue gas can flow close to the outer periphery of the downstream side of the heat exchange tube hole 1100a, thereby further improving the heat exchange efficiency between the outer periphery of the downstream side of the heat exchange tube hole 1100a and the flue gas.

[0074] Along the overall flow direction S2 of the flue gas, the distance between the center point of the third flanging 1103 and the center of the heat exchange tube hole 1100a is h2. The larger the distance h2 is, the smaller the effect of the third flanging 1103 on blocking the flow of the flue gas and making more flue gas flow close to the outer periphery of the downstream side of the heat exchange tube hole 1100a. The smaller the distance h2 is, the greater the effect of the third flanging 1103 on making more flue gas flow close to the outer periphery of the downstream side of the heat exchange tube hole 1100a, but the greater the impact of the third flanging 1103 on the fluidity of the flue gas. Based on this, the distance h2 cannot be too small or too large. In one embodiment, the distance h2 can satisfy: 6 mm ≤ h2 ≤ 7 mm. For example, the distance h2 can be 6 mm, 6.1 mm, 6.2 mm, 6.3 mm, 6.4 mm, 6.5 mm, 6.6 mm, 6.7 mm, 6.8 mm, 6.9 mm or 7 mm, etc.

[0075] The distance between the third flanging 1103 and the adjacent heat exchange tube hole 1100a is d. The larger the distance d, the better the flue gas flowability between the third flanging 1103 and the adjacent heat exchange tube hole 1100a. The third flanging 1103 blocks the flue gas flow, so that the effect of making more flue gas flow along the outer periphery of the downstream side of the heat exchange tube hole 1100a is smaller. The smaller the distance d, the greater the effect of the third flanging 1103 making more flue gas flow along the outer periphery of the downstream side of the heat exchange tube hole 1100a. However, the influence of the third flanging 1103 on the flue gas flowability is also greater. Based on this, the distance d should not be too small or too large. In one embodiment, the distance d can satisfy: 4mm ≤ d ≤ 5mm. For example, the distance d can be 4mm, 4.1mm, 4.2mm, 4.3mm, 4.4mm, 4.5mm, 4.6mm, 4.7mm, 4.8mm, 4.9mm or 5mm, etc.

[0076] In one embodiment, while the distance h2 can be made to satisfy 6mm ≤ h2 ≤ 7mm, the distance d can be made to satisfy 4mm ≤ d ≤ 5mm, so that the relative position between the third flanging 1103 and the adjacent heat exchange tube hole 1100a can be made more reasonable. While the third flanging 1103 has a better effect of making more flue gas flow along the outer periphery of the downstream side of the heat exchange tube hole 1100a, the flue gas flowability between the third flanging 1103 and the adjacent heat exchange tube hole 1100a is better, so that the combustion efficiency of the gas water heater including the heat exchange fin 110 of this embodiment is higher.

[0077] In one embodiment, the heat exchange fin 110 further includes a plurality of first convex hulls 1104. The first convex hulls 1104 are arranged on the substrate 1100. The first convex hulls 1104 are arranged at intervals on at least one side of the first flanging 1101 along the length direction S1 of the substrate 1100. Thus, the flue gas at the end of the first flanging 1101 can be turbulently flowed through the first convex hulls 1104. On the one hand, the residence time of the flue gas between the first flanging 1101 and the outer periphery of the heat exchange tube hole 1100a can be further increased to further improve the heat exchange efficiency between the outer periphery of the heat exchange tube hole 1100a and the flue gas. On the other hand, the surface area of the heat exchange fin 110 can be increased, and then the heat exchange area between the heat exchange fin 110 and the flue gas can be increased to further improve the overall heat exchange efficiency between the heat exchange fin 110 and the flue gas.

[0078] In one embodiment, the heat exchange fin 110 further includes a plurality of second convex hulls 1105. The second convex hulls 1105 are provided on the substrate 1100. A plurality of second convex hulls 1105 are spaced around the outer periphery of at least the side of the heat exchange tube hole 1100a facing away from the first flanging 1101. On the one hand, the second convex hulls 1105 can block and turbulently flow the flue gas upstream of the heat exchange tube hole 1100a, so as to slow down the flow rate of the high-temperature flue gas, thereby increasing the residence time of the flue gas at the outer periphery of the heat exchange tube hole 1100a, and further improving the heat exchange efficiency between the outer periphery of the heat exchange tube hole 1100a and the flue gas. On the other hand, it can increase the surface area of the heat exchange fin 110, and then increase the heat exchange area between the heat exchange fin 110 and the flue gas, so as to further improve the overall heat exchange efficiency between the heat exchange fin 110 and the flue gas.

[0079] In one embodiment, the heat exchange fin 110 further includes an annular flanging group 1106. The annular flanging group 1106 includes two annular cylindrical fourth flangings 1106a spaced along the length direction S1 of the substrate 1100 on the substrate 1100. For the heat exchange tube hole 1100a closest to the edge of the substrate 1100 along the length direction S1 of the substrate 1100, the annular flanging group 1106 is located directly downstream of the heat exchange tube hole 1100a along the overall flow direction S2 of the flue gas. In other words, the interval between the two fourth flangings 1106a is located directly downstream of the heat exchange tube hole 1100a along the overall flow direction S2 of the flue gas. Since the blocking effect of the annular flanging group 1106 on the flue gas is weaker than that of the first flanging 1101, arranging the annular flanging group 1106 directly downstream of the heat exchange tube hole 1100a closest to the edge of the substrate 1100 along the length direction S1 of the substrate 1100 can make the flue gas more easily discharged from directly downstream of the heat exchange tube hole 1100a closest to the edge of the substrate 1100 along the length direction S1 of the substrate 1100. On the one hand, it can cause a certain blockage to the flue gas, so as to increase the time for the flue gas to pass through the outer periphery of the heat exchange tube hole 1100a and improve the heat exchange efficiency. On the other hand, it is beneficial to keep the flue gas flowing reasonably, so that sufficient oxygen can enter the gas water heater for combustion, so that the gas water heater provided with the heat exchange fin 110 of this embodiment has a high combustion efficiency, and further reduces energy loss. On the other hand, since there is no outlet for the flue gas at the outermost edge of the substrate 1100 along the length direction S1, the flue gas flow rate around the outer periphery of the heat exchange tube hole 1100a closest to the edge along the length direction S1 is usually small, resulting in low heat exchange efficiency. By such an arrangement, more flue gas can also flow around the outer periphery of the heat exchange tube hole 1100a closest to the edge along the length direction S1, thereby improving the heat exchange efficiency at the outer periphery of the heat exchange tube hole 1100a closest to the edge along the length direction S1.

[0080] In one embodiment, the heat exchange fin 110 may simultaneously include at least two of the first convex hull 1104, the second convex hull 1105, and the annular flanging group 1106, so that the heat exchange efficiency of the heat exchange fin 110 is higher.

[0081] Please refer to Figure 6 and Figure 1 As shown, this embodiment also proposes a heat exchanger 11, including: a heat exchange tube 111 and a plurality of heat exchange fins 110 as described in the foregoing technical solution. The plurality of heat exchange fins 110 are arranged at intervals in a direction perpendicular to the plate surface of the substrate 1100. The heat exchange tube 111 passes through the heat exchange tube holes 1100a of the heat exchange fins 110. Since the heat exchange fins 110 described in the foregoing technical solution have a high heat exchange efficiency, the heat exchange efficiency and combustion efficiency of the heat exchanger 11 can be made relatively high.

[0082] In one embodiment, the heat exchanger 11 may include a plurality of heat exchange tubes 111. For the same heat exchange fin 110, the plurality of heat exchange tubes 111 respectively pass through a plurality of heat exchange tube holes 1100a of the heat exchange fin 110 one by one.

[0083] In other embodiments, the same heat exchange tube 111 may be partially bent to pass through a plurality of heat exchange tube holes 1100a of the same heat exchange fin 110.

[0084] As Figure 7 shown, this embodiment also proposes a gas water heater 1, including: a water inlet pipe 12, a water outlet pipe 13, and a heat exchanger 11 as described in the foregoing technical solution. The water inlet pipe 12 and the water outlet pipe 13 are respectively communicated with two ends of the heat exchange tube 111 of the heat exchanger 11. Since the gas water heater 1 described in the foregoing technical solution has a high heat exchange efficiency and combustion efficiency, the overall heat exchange efficiency and combustion efficiency of the gas water heater 1 are relatively high, and energy waste can be reduced.

[0085] In the specific content of the above specific embodiments, the technical features can be combined arbitrarily without contradiction. For the sake of brevity of description, not all possible combinations of the above technical features are described. However, as long as the combinations of these technical features do not conflict, they should all be considered to be within the scope described in this specification.

[0086] The specific content of the above specific embodiments only expresses several embodiments of the present invention, and 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 invention. It should be noted that for those of ordinary skill in the art, without departing from the concept of the present invention, several deformations and improvements can still be made, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the patent of the present invention should be subject to the appended claims.

Claims

1. A heat exchange fin, characterized in that, Comprising: A substrate (1100), along the length direction of the substrate (1100), a plurality of heat exchange tube holes (1100a) are spaced on the substrate (1100): A plurality of first flanges (1101), the first flanges (1101) are provided on the substrate (1100), along the overall flow direction of the flue gas, at least part of the first flanges (1101) are provided directly downstream of the heat exchange tube holes (1100a); and A plurality of second flanges (1102), the second flanges (1102) are provided on the substrate (1100), along the overall flow direction of the flue gas, the second flanges (1102) are provided directly downstream between any two adjacent heat exchange tube holes (1100a), in the projection plane perpendicular to the overall flow direction of the flue gas, the positive projection of the first flange (1101) and the positive projection of the second flange (1102) partially overlap; Wherein, both the first flange (1101) and the second flange (1102) are strip-shaped, and the first flange (1101) is provided with an opening (1101a) penetrating through two opposite surfaces along the overall flow direction of the flue gas.

2. The heat exchange fin according to claim 1, wherein, The first flange (1101) is an arc-shaped strip flange, the first flange (1101) bends and protrudes towards the direction close to the corresponding heat exchange tube hole (1100a), or, the first flange (1101) bends and protrudes towards the direction away from the corresponding heat exchange tube hole (1100a); And / or, along the overall flow direction of the flue gas, the minimum distance between the first flange (1101) and the center of the heat exchange tube hole (1100a) located directly upstream of itself is h1, 10mm ≤ h1 ≤ 12mm.

3. The heat exchange fin according to claim 1, wherein Along the overall flow direction of the flue gas, the opening (1101a) is located directly downstream of the heat exchange tube hole (1100a); and / or, Along the length direction of the substrate (1100), the opening (1101a) has a size w1, 4mm ≤ w1 ≤ 5mm.

4. The heat exchange fin according to any one of claims 1-3, characterized in that, Along the overall flow direction of the flue gas, the second flange (1102) is located on the downstream side of the first flange (1101), or, the second flange (1102) is located on the upstream side of the first flange (1101).

5. The heat exchange fin according to claim 4, characterized in that, Along the length direction of the substrate (1100), the second flange (1102) has a size w2, the center distance between two adjacent heat exchange tube holes (1100a) is w3, the distance between two adjacent heat exchange tube holes (1100a) is w4, w4 < w2 < w3.

6. The heat exchange fin according to any one of claims 1-3, characterized in that, The heat exchange fin (110) further includes a third flange (1103), the third flange (1103) is a ring-shaped cylinder, the third flange (1103) is provided on the substrate (1100) and is located between two adjacent heat exchange tube holes (1100a) and the second flange (1102).

7. The heat exchange fin according to claim 6, wherein Along the overall flow direction of the flue gas, the distance between the center point of the third flange (1103) and the center of the heat exchange tube hole (1100a) is h2, 6mm ≤ h2 ≤ 7mm; and / or, The distance between the third flanging (1103) and the adjacent heat exchange tube hole (1100a) is d, where 4 mm ≤ d ≤ 5 mm.

8. The heat exchange fin according to any one of claims 1-3, characterized in that, The heat exchange fin (110) further includes a plurality of first convex hulls (1104). The first convex hulls (1104) are arranged on the substrate (1100), and the first convex hulls (1104) are arranged at intervals on at least one side of the substrate (1100) along the length direction of the substrate (1100); and / or The heat exchange fin (110) further includes a plurality of second convex hulls (1105). The second convex hulls (1105) are arranged on the substrate (1100), and a plurality of the second convex hulls (1105) are arranged at intervals around the outer periphery of at least the side of the heat exchange tube hole (1100a) facing away from the first flanging (1101); and / or The heat exchange fin (110) further includes an annular flanging group (1106). The annular flanging group (1106) includes two annular cylindrical fourth flangings (1106a) arranged at intervals on the substrate (1100) along the length direction of the substrate (1100). For the heat exchange tube hole (1100a) closest to the edge of the substrate (1100) along the length direction of the substrate (1100), the annular flanging group (1106) is located downstream of the heat exchange tube hole (1100a) along the overall flow direction of the flue gas.

9. A heat exchanger, characterized in that, Comprising: A heat exchange tube (111) and a plurality of heat exchange fins (110) as described in any one of claims 1-8. The plurality of heat exchange fins (110) are arranged at intervals in a direction perpendicular to the plate surface of the substrate (1100), and the heat exchange tube (111) is inserted through the heat exchange tube holes (1100a) of the heat exchange fins (110).

10. A gas water heater, characterized in that, Comprising: A water inlet pipe (12), a water outlet pipe (13), and a heat exchanger (11) as described in claim 9. The water inlet pipe (12) and the water outlet pipe (13) are respectively communicated with both ends of the heat exchange tube (111).

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