Manifold and heat exchanger having the same

Abstract

The present invention discloses a manifold and a heat exchanger having the same. A plurality of slot holes are provided on the peripheral wall of the manifold, penetrating through the peripheral wall of the manifold in the wall thickness direction of the manifold. The length direction of each slot hole is parallel to the axial direction of the manifold, and the plurality of slot holes are arranged at intervals along the axial direction of the manifold. Wherein, the ratio of the distance between adjacent slot holes in the axial direction of the manifold to the width of the slot hole is between 0.9 and 4. The manifold according to the embodiment of the present invention has the advantages of strong pressure resistance, high heat transfer efficiency per unit area, good heat transfer effect, uniform water temperature distribution, etc.

Description

Technical Field

[0001] The present invention relates to the technical field of heat exchange, and more particularly, to a header pipe and a heat exchanger having the header pipe. Background Art

[0002] A heat pump water heater utilizes the reverse Carnot principle to transfer heat from a low-temperature object to high-temperature water through a medium. The heat pump device can cause the phase change of the medium (refrigerant), making it lower than the low-temperature heat source, so as to spontaneously absorb the heat of the low-temperature heat source; after returning to the compressor, the medium is compressed into a high-temperature (higher than the high-temperature water) and high-pressure gas, so as to spontaneously release heat to the high-temperature heat source; realizing the function of "transferring" heat from the low-temperature heat source to the high-temperature heat source. Due to the advantages of energy conservation and environmental protection of the multi-channel heat exchanger, more and more heat pump water heaters currently adopt multi-channel heat exchangers. The multi-channel heat exchanger applied to the heat pump water heater includes two main components, namely a heat exchange tube and a header pipe. The multi-channel heat exchanger is wrapped outside the inner tank of the water tank, so that the heat exchange tube contacts the inner tank of the water tank.

[0003] However, in the related art, the heat exchanger applied to the heat pump water heater either has poor pressure resistance and cannot meet the working requirements; or has a low heat transfer efficiency per unit area, which affects the heat transfer effect and the water temperature distribution is uneven. Summary of the Invention

[0004] The present invention aims to at least solve one of the above technical problems in the related art to some extent. For this purpose, the present invention provides a header pipe, which has the advantages of strong pressure resistance, high heat transfer efficiency per unit area, good heat transfer effect, and uniform water temperature distribution.

[0005] The present invention also provides a heat exchanger having the header pipe.

[0006] To achieve the above object, according to an embodiment of the first aspect of the present invention, a header pipe is provided. A plurality of slot holes penetrating the peripheral wall of the header pipe in the wall thickness direction of the header pipe are provided on the peripheral wall of the header pipe. The length direction of each slot hole is parallel to the axial direction of the header pipe, and the plurality of slot holes are arranged at intervals along the axial direction of the header pipe. Wherein, the distance between adjacent slot holes in the axial direction of the header pipe is less than one-third of the equivalent diameter of the header pipe.

[0007] The header pipe according to the embodiment of the present invention has the advantages of strong pressure resistance, high heat transfer efficiency per unit area, good heat transfer effect, and uniform water temperature distribution.

[0008] In addition, the header pipe according to the embodiment of the present invention may further have the following additional technical features:

[0009] According to an embodiment of the present invention, the distance between adjacent slot holes in the axial direction of the header pipe is not less than one-tenth of the equivalent diameter of the header pipe.

[0010] According to an embodiment of the present invention, the distance between adjacent ones of the slot holes in the axial direction of the header pipe is greater than one-fifth of the equivalent diameter of the header pipe.

[0011] According to an embodiment of the present invention, the distance between adjacent ones of the slot holes in the axial direction of the header pipe is greater than the wall thickness of the header pipe and less than three times the wall thickness of the header pipe.

[0012] According to an embodiment of the present invention, the ratio of the distance between adjacent ones of the slot holes in the axial direction of the header pipe to the width of the slot hole is between 0.9 and 4.

[0013] According to an embodiment of the present invention, the ratio of the cross-sectional area of the slot hole to the distance between adjacent ones of the slot holes in the axial direction of the header pipe is between 2 mm and 8 mm.

[0014] According to an embodiment of the present invention, the ratio of the equivalent diameter of the header pipe to the product of the distance between adjacent ones of the slot holes in the axial direction of the header pipe and the wall thickness of the header pipe is 1.7 mm -1 ~5 mm -1 between.

[0015] According to an embodiment of the present invention, the ratio of the product of the equivalent diameter of the header pipe and the wall thickness of the header pipe to the length of the slot hole is between 0.9 mm and 4 mm.

[0016] According to an embodiment of the second aspect of the present invention, there is provided a heat exchanger, which includes: a header pipe, the header pipe being the header pipe according to the embodiment of the first aspect of the present invention; a plurality of heat exchange pipes, end portions of the plurality of heat exchange pipes being respectively inserted into a plurality of slot holes of the header pipe.

[0017] The heat exchanger according to the embodiment of the present invention, by using the header pipe according to the embodiment of the first aspect of the present invention, has the advantages of strong pressure resistance, high heat exchange efficiency, good heat exchange effect, uniform water temperature distribution, etc.

[0018] According to an embodiment of the present invention, the heat exchange pipe is a flat pipe, and the ratio of the distance between adjacent ones of the heat exchange pipes in the axial direction of the header pipe to the thickness of the heat exchange pipe is between 0.9 and 4.

[0019] According to an embodiment of the present invention, the heat exchange pipe is a flat pipe, and the ratio of the cross-sectional area of the heat exchange pipe to the distance between adjacent ones of the heat exchange pipes is between 2 mm and 8 mm.

[0020] According to an embodiment of the present invention, the ratio of the product of the equivalent diameter of the header pipe and the wall thickness of the header pipe to the width of the heat exchange pipe is between 0.9 mm and 4 mm.

[0021] According to an embodiment of the third aspect of the present invention, a header pipe is provided. A plurality of slots are provided on the peripheral wall of the header pipe, penetrating the peripheral wall of the header pipe along the wall thickness direction of the header pipe. The length direction of each slot is parallel to the axial direction of the header pipe, and the plurality of slots are arranged at intervals along the axial direction of the header pipe. Wherein, the ratio of the distance between adjacent slots in the axial direction of the header pipe to the width of the slot is between 0.9 and 4.

[0022] The header pipe according to the embodiment of the present invention has the advantages of strong pressure resistance, high heat transfer efficiency per unit area, good heat transfer effect, uniform water temperature distribution, etc.

[0023] In addition, the header pipe according to the embodiment of the present invention may further have the following additional technical features:

[0024] According to an embodiment of the present invention, the distance between adjacent slots in the axial direction of the header pipe is less than one-third of the equivalent diameter of the header pipe.

[0025] According to an embodiment of the present invention, the distance between adjacent slots in the axial direction of the header pipe is not less than one-tenth of the equivalent diameter of the header pipe.

[0026] According to an embodiment of the present invention, the distance between adjacent slots in the axial direction of the header pipe is greater than one-fifth of the equivalent diameter of the header pipe.

[0027] According to an embodiment of the present invention, the distance between adjacent slots in the axial direction of the header pipe is greater than the wall thickness of the header pipe and less than three times the wall thickness of the header pipe.

[0028] According to an embodiment of the present invention, the ratio of the cross-sectional area of the slot to the distance between adjacent slots in the axial direction of the header pipe is between 2 mm and 8 mm.

[0029] According to an embodiment of the present invention, the ratio of the equivalent diameter of the header pipe to the product of the distance between adjacent slots in the axial direction of the header pipe and the wall thickness of the header pipe is between 1.7 mm -1 ~5 mm -1 Between.

[0030] According to an embodiment of the present invention, the ratio of the product of the equivalent diameter of the header pipe and the wall thickness of the header pipe to the length of the slot is between 0.9 mm and 4 mm.

[0031] According to an embodiment of the fourth aspect of the present invention, a heat exchanger is provided. The heat exchanger includes: a header pipe, the header pipe being the header pipe according to the embodiment of the third aspect of the present invention; a plurality of heat exchange pipes, and the end portions of the plurality of heat exchange pipes are respectively inserted into a plurality of slots of the header pipe.

[0032] The heat exchanger according to an embodiment of the present invention, by using the header pipe described in the embodiment of the third aspect of the present invention, has the advantages of strong pressure resistance, high heat exchange efficiency, good heat exchange effect, uniform water temperature distribution, etc.

[0033] According to an embodiment of the present invention, the heat exchange tube is a flat tube, and the ratio of the distance between adjacent heat exchange tubes in the axial direction of the header pipe to the thickness of the heat exchange tube is between 0.9 and 4.

[0034] According to an embodiment of the present invention, the heat exchange tube is a flat tube, and the ratio of the cross-sectional area of the heat exchange tube to the distance between adjacent heat exchange tubes is between 2 mm and 8 mm.

[0035] According to an embodiment of the present invention, the ratio of the product of the equivalent diameter of the header pipe and the wall thickness of the header pipe to the width of the heat exchange tube is between 0.9 mm and 4 mm. Description of the Drawings

[0036] Figure 1 is a schematic structural diagram of a heat exchanger according to an embodiment of the present invention.

[0037] Figure 2 is a schematic structural diagram of a header pipe according to an embodiment of the present invention.

[0038] Figure 3 is Figure 2 an enlarged view of area A in

[0039] Figure 4 is a radial view of a header pipe according to an embodiment of the present invention.

[0040] Figure 5 is an axial view of a header pipe according to an embodiment of the present invention.

[0041] Figure 6 is a schematic partial structural diagram of a heat exchanger according to another embodiment of the present invention.

[0042] Reference Signs:

[0043] Heat exchanger 1,

[0044] Header pipe 100, slot hole 110,

[0045] Heat exchange tube 200. Detailed Description of the Invention

[0046] Embodiments of the present invention will be described in detail below. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to explain the present invention, and should not be construed as limiting the present invention.

[0047] The present invention is based on the discovery and recognition by the inventors of the present application of the following facts and problems:

[0048] In the heat exchanger for a heat pump water heater in the related art, the width direction of the flat tube is parallel to the axial direction of the header pipe. The dimension of the heat exchanger in the length direction of the flat tube is called the length of the heat exchanger, and the dimension of the heat exchanger in the axial direction of the header pipe is called the height of the heat exchanger. The design parameters of the header pipe are crucial for the performance of the heat exchanger. In particular, the parameters of the flat tube grooves on the header pipe directly affect the pressure resistance and heat transfer capacity of the heat exchanger.

[0049] Specifically, under the condition that the length and height of the heat exchanger are constant, as the width of the flat tube decreases, the flow area inside the flat tube decreases, the flow velocity of the refrigerant is increased, and the heat transfer is enhanced to increase the heat transfer amount. On the other hand, if the width of the flat tube is too small, the number of flat tubes will be excessively increased, resulting in too many solder joints on the heat exchanger, affecting the pressure resistance and reliability of the heat exchanger.

[0050] Under the condition that the length and height of the heat exchanger are constant, as the distance between the flat tubes increases, the pressure resistance of the heat exchanger gradually increases, enhancing the reliability of the heat exchanger. On the other hand, if the distance between the flat tubes is too large, the number of flat tubes will be too small, resulting in insufficient heat transfer area of the heat exchanger, affecting the heat transfer capacity.

[0051] As the outer diameter of the header pipe decreases, the pressure resistance of the heat exchanger increases. On the other hand, if the outer diameter of the header pipe is too small, the flow area inside the heat exchanger becomes smaller, the flow resistance of the refrigerant increases, affecting the heat transfer capacity.

[0052] As the thickness of the flat tube increases, the corrosion resistance of the heat exchanger is improved. On the other hand, if the thickness of the flat tube is too large, the thermal resistance of heat conduction of the heat exchanger will increase, affecting the heat exchanger effect.

[0053] Considering the situation of the heat exchanger for a heat pump water heater in the related art, the present invention provides a header pipe having the advantages of strong pressure resistance, high heat transfer efficiency per unit area, good heat transfer effect, uniform water temperature distribution, etc., and a heat exchanger having the same.

[0054] A heat exchanger 1 according to an embodiment of the present invention will be described below with reference to the accompanying drawings.

[0055] As Figure 1 described, the heat exchanger 1 according to an embodiment of the present invention includes a header pipe 100 and a plurality of heat exchange tubes 200, wherein the heat exchange tubes 200 may be flat tubes.

[0056] First, the header pipe 100 according to an embodiment of the present invention will be described with reference to the accompanying drawings.

[0057] As Figures 2 - 5 shown, a plurality of slots 110 penetrating the peripheral wall of the header pipe 100 in the wall thickness direction of the header pipe 100 are provided on the peripheral wall of the header pipe 100. The length direction of each slot 110 is parallel to the axial direction of the header pipe 100, and the plurality of slots 110 are arranged at intervals along the axial direction of the header pipe 100. Preferably, the plurality of slots 110 are arranged at equal intervals along the axial direction of the header pipe 100.

[0058] In the heat exchanger 1 according to an embodiment of the present invention, there are at least two header pipes 100 arranged in parallel at intervals. One ends of a plurality of heat exchange pipes 200 are respectively inserted into a plurality of slots 110 of one header pipe 100, and the other ends of the plurality of heat exchange pipes 200 are respectively inserted into a plurality of slots 110 of another header pipe 100. That is, one end of each heat exchange pipe 200 is inserted into a slot 110 of one header pipe 100, and the other end of each heat exchange pipe 200 is inserted into a slot 110 of another header pipe 100.

[0059] Wherein, the distance between adjacent slots 110 in the axial direction of the header pipe 100 is WE, the equivalent diameter of the header pipe 200 is DI, the wall thickness of the header pipe 100 is DP, the width of the slot 110 is WH, and the length of the slot 110 is WI.

[0060] It should be understood here that when the outer dimension of the heat exchange pipe 200 is consistent with the dimension of the heat exchange pipe installation port (the dimension of the slot 110), the width WH of the slot 110 corresponds to the thickness of the heat exchange pipe 200, the length WI of the slot 110 corresponds to the width of the heat exchange pipe 200, the equivalent diameter of the header pipe 200 refers to the equivalent diameter of the outer contour of the header pipe 200, and the wall thickness of the header pipe 100 refers to the thickness of the peripheral wall of the header pipe 200. The header pipe 100 in the figure is a circular pipe, and of course, it can also be a pipe with other cross-sectional shapes, such as a D-shaped pipe, etc.

[0061] The above parameters satisfy: the distance WE between adjacent slots 110 in the axial direction of the header pipe 100 is less than one-third of the equivalent diameter DI of the header pipe 200, that is, WE < DI / 3.

[0062] After the inner tank of the heat pump water heater is shaped, the size of the heat exchanger 1 is usually fixed. According to the header pipe 100 of the embodiment of the present invention, by setting the parameter relationship between the pitch WE of the slots 110 and the equivalent diameter DI of the header pipe, the parameter relationship between the pitch of the heat exchange pipes 200 and the equivalent diameter DI of the heat exchange pipes 200 can be defined. Without changing the installation area of the heat exchanger 1, on the one hand, excessive local pressure concentration can be avoided, ensuring the pressure resistance performance of the heat exchanger 1, so as to meet the working requirements; on the other hand, the heat exchange efficiency per unit area can be ensured, improving the heat exchange effect and the uniformity of the water temperature distribution. That is, according to the header pipe 100 of the embodiment of the present invention, by adjusting the pitch of the heat exchange pipes 200, the pressure resistance performance, the heat exchange effect and the uniformity of the water temperature distribution can be taken into account.

[0063] According to the heat exchanger 1 of the embodiment of the present invention, by using the header pipe 100 of the above embodiment of the present invention, it has the advantages of strong pressure resistance performance, high heat exchange efficiency, good heat exchange effect, uniform water temperature distribution, etc.

[0064] Next, the header pipe 100 according to the specific embodiment of the present invention will be described with reference to the drawings.

[0065] As Figures 2 - 5 shown, a plurality of slots 110 penetrating the peripheral wall of the header pipe 100 in the wall thickness direction of the header pipe 100 are provided on the peripheral wall of the header pipe 100. The length direction of each slot 110 is parallel to the axial direction of the header pipe 100, and the plurality of slots 110 are arranged at intervals along the axial direction of the header pipe 100.

[0066] Furthermore, the distance WE between adjacent slots 110 in the axial direction of the header pipe 100 is not less than one-tenth of the equivalent diameter DI of the header pipe 200, that is, WE≥DI / 10. In other words, the distance between adjacent heat exchange pipes 200 in the axial direction of the header pipe 100 is less than one-third of the equivalent diameter DI of the header pipe 200 and greater than or equal to one-tenth of the equivalent diameter DI of the header pipe 200. Preferably, the distance WE between adjacent slots 110 in the axial direction of the header pipe 100 is greater than one-fifth of the equivalent diameter DI of the header pipe 200, that is, WE>DI / 5. In other words, the distance between adjacent heat exchange pipes 200 in the axial direction of the header pipe 100 is less than one-third of the equivalent diameter DI of the header pipe 200 and greater than one-fifth of the equivalent diameter DI of the header pipe 200. Thereby, not only the welding quality between the heat exchange pipes 200 and the header pipe 100 can be ensured, but also the local pressure can be further dispersed, thereby further improving the pressure resistance performance of the header pipe 100 and the heat exchanger 1.

[0067] In some specific embodiments of the present invention, such as Figures 2 - 5As shown, the distance WE between adjacent slots 110 in the axial direction of the header 100 is greater than the wall thickness DP of the header 100 and less than three times the wall thickness DP of the header 100, that is, DP < WE < 3DP. In other words, the distance between adjacent heat exchange tubes 200 in the axial direction of the header 100 is greater than the wall thickness DP of the header 100 and less than three times the wall thickness DP of the header 100, that is, DP < WE < 3DP. When the installation area of the heat exchanger 1 remains unchanged, by further limiting the parameter relationship between the spacing of the heat exchange tubes 200 and the wall thickness of the header 100, on the one hand, the internal volume of the header 100 can be reduced to reduce the flow resistance of the heat exchanger 1; on the other hand, the heat exchange area can be increased to improve the heat exchange efficiency. Therefore, the parameter relationship within the above range can improve the heat exchange efficiency per unit area and the pressure resistance performance, and can reasonably distribute the solder joints to reduce the leakage risk.

[0068] In some specific examples of the present invention, such as Figures 2 - 4 As shown, the ratio of the distance WE between adjacent slots 110 in the axial direction of the header 100 to the width WH of the slot 110 is greater than 0.9 and less than 4, that is, 0.9 < WE / WH < 4. In other words, the ratio of the distance between adjacent heat exchange tubes 200 in the axial direction of the header 100 to the thickness of the heat exchange tube 200 is greater than 0.9 and less than 4. When the installation area of the heat exchanger 1 remains unchanged, by further limiting the parameter relationship between the spacing of the heat exchange tubes 200 and the thickness of the heat exchange tube 200, on the one hand, the pressure resistance performance of the heat exchanger 1 can be ensured to improve its reliability; on the other hand, the corrosion resistance performance of the heat exchanger 1 can be ensured to reduce the leakage risk, thereby further improving the reliability.

[0069] In some specific embodiments of the present invention, such as Figures 2 - 4 As shown, the ratio of the product of the length WI of the slot 110 and the width WH of the slot 110 to the distance WE between adjacent slots 110 in the axial direction of the header 100 is greater than 2 mm and less than 8 mm, that is, the ratio of the cross-sectional area of the slot 110 to the distance between adjacent slots 110 in the axial direction of the header 200 is between 2 mm and 8 mm, 2 mm < (WI * WH) / WE < 8 mm. In other words, the ratio of the cross-sectional area of the outer contour of the heat exchange tube 200 to the distance between adjacent heat exchange tubes 200 in the axial direction of the header 100 is greater than 2 mm and less than 8 mm. Thus, the parameter relationship between the slotting area of the slot 110 and the spacing of the heat exchange tubes 200 can be limited. On the one hand, the heat exchange efficiency per unit area can be improved; on the other hand, the strength of the material and welding can be ensured to reduce welding defects and damage of the heat exchange tube 200, thereby improving the reliability of the heat exchanger 1.

[0070] In some specific examples of the present invention, such as Figures 2 - 5As shown, the ratio of the equivalent diameter DI of the header pipe to the product of the distance WE between adjacent slots 110 in the axial direction of the header pipe 100 and the wall thickness DP of the header pipe 100 is greater than 1.7 mm -1 and less than 5 mm -1 , that is, 1.7 mm -1 <DI / (WE*DP)<5 mm -1 . In other words, the ratio of the equivalent diameter DI of the header pipe to the product of the distance between adjacent heat exchange pipes 200 in the axial direction of the header pipe 100 and the wall thickness DP of the header pipe 100 is greater than 1.7 mm -1 and less than 5 mm -1 . Thus, on the one hand, the number of solder joints can be reduced, the pressure resistance of the heat exchanger 1 can be improved, and the leakage risk can be further reduced; on the other hand, the heat exchange area of the heat exchanger 1 can be increased, and the heat exchange effect can be enhanced.

[0071] In some specific embodiments of the present invention, as Figures 2 - 5 shown, the ratio of the product of the equivalent diameter DI of the header pipe and the wall thickness DP of the header pipe 100 to the length WI of the slot 110 is greater than 0.9 mm and less than 4 mm, that is, 0.9 mm < (DI*DP) / WI < 4 mm. In other words, the ratio of the product of the equivalent diameter DI of the header pipe 100 and the wall thickness DP of the header pipe 100 to the width of the heat exchange pipe 200 is greater than 0.9 mm and less than 4 mm. In this way, on the one hand, the pressure resistance of the heat exchanger 1 can be improved, thereby improving the reliability; on the other hand, the internal volume of the header pipe 100 can be reduced, the refrigerant filling amount can be reduced, and the reliability of the operation of the heat exchanger 1 can be further increased. In other specific embodiments of the present invention, as Figure 6 shown, it is convenient for installation and positioning, effectively controls the length of the heat exchange pipe 200 inserted into the header pipe 100, improves the welding strength, thereby improving the pressure resistance of the heat exchanger 1. The end of the heat exchange pipe 200 is provided with a necking, the width WI' of the heat exchange pipe 200 is greater than the length WI of the slot 110, the thickness WH' of the heat exchange pipe 200 is greater than the width WH of the slot 110, and the distance WE' between adjacent heat exchange pipes 200 is less than the distance WE between adjacent slots 110. At this time, the size parameters of the slot 110 need to be adjusted adaptively according to the size of the necking, so as to ensure:

[0072] The ratio of the distance WE' between adjacent heat exchange pipes 200 in the axial direction of the header pipe 100 to the thickness WH' of the heat exchange pipe 200 is greater than 0.9 and less than 4, that is, 0.9 < WE' / WH' < 4.

[0073] The cross-sectional area of the outer circumference of the non-necked part of the heat exchange pipe 200 is greater than 2 mm and less than 8 mm compared with the distance WE' between adjacent heat exchange pipes 200 in the axial direction of the header pipe 100, that is, 2 mm < (WI'*WH') / WE' < 8 mm.

[0074] The ratio of the product of the equivalent diameter DI of the header pipe 100 and the wall thickness DP of the header pipe 100 to the width WI' of the heat exchange pipe 200 is greater than 0.9 mm and less than 4 mm, that is, 0.9 mm < (DI * DP) / WI' < 4 mm.

[0075] The heat exchanger 1 according to an embodiment of the present invention will be described below with reference to the accompanying drawings.

[0076] As Figure 1 described, the heat exchanger 1 according to an embodiment of the present invention includes a header pipe 100 and a plurality of heat exchange pipes 200. Among them, the heat exchange pipes 200 can be flat pipes.

[0077] First, the header pipe 100 according to an embodiment of the present invention will be described with reference to the accompanying drawings.

[0078] As Figures 2 - 5 shown, a plurality of slot holes 110 penetrating the peripheral wall of the header pipe 100 in the wall thickness direction of the header pipe 100 are provided on the peripheral wall of the header pipe 100. The length direction of each slot hole 110 is parallel to the axial direction of the header pipe 100, and the plurality of slot holes 110 are arranged at intervals along the axial direction of the header pipe 100. Preferably, the plurality of slot holes 110 are arranged at equal intervals along the axial direction of the header pipe 100.

[0079] In the heat exchanger 1 according to an embodiment of the present invention, there are at least two header pipes 100 arranged in parallel at intervals. One ends of the plurality of heat exchange pipes 200 are respectively inserted into a plurality of slot holes 110 of one header pipe 100, and the other ends of the plurality of heat exchange pipes 200 are respectively inserted into a plurality of slot holes 110 of another header pipe 100. That is, one end of each heat exchange pipe 200 is inserted into a slot hole 110 of one header pipe 100, and the other end of each heat exchange pipe 200 is inserted into a slot hole 110 of another header pipe 100.

[0080] Among them, the distance between adjacent slot holes 110 in the axial direction of the header pipe 100 is WE, the equivalent diameter of the header pipe 200 is DI, the wall thickness of the header pipe 100 is DP, the width of the slot hole 110 is WH, and the length of the slot hole 110 is WI.

[0081] It should be understood here that when the external dimension of the heat exchange pipe 200 is the same as the dimension of the heat exchange pipe installation port (the dimension of the slot hole 110), the width WH of the slot hole 110 corresponds to the thickness of the heat exchange pipe 200, the length WI of the slot hole 110 corresponds to the width of the heat exchange pipe 200, the equivalent diameter of the header pipe 200 refers to the equivalent diameter of the outer contour of the header pipe 200, and the wall thickness of the header pipe 100 refers to the thickness of the peripheral wall of the header pipe 200. The header pipe 100 in the figure is a circular pipe, and of course, it can also be a pipe with other cross-sectional shapes, such as a D-shaped pipe, etc.

[0082] The above parameters satisfy that the ratio of the distance WE between adjacent slots 110 in the axial direction of the header pipe 100 to the width WH of the slot 110 is greater than 0.9 and less than 4, that is, 0.9 < WE / WH < 4. In other words, the ratio of the distance between adjacent heat exchange tubes 200 in the axial direction of the header pipe 100 to the thickness of the heat exchange tube 200 is greater than 0.9 and less than 4.

[0083] After the inner tank of the heat pump water heater is shaped, the size of the installed heat exchanger 1 is usually fixed. According to the header pipe 100 of the embodiment of the present invention, by setting the parameter relationship between the distance WE between the slots 110 and the width WH of the slot 110, and by limiting the parameter relationship between the distance between the heat exchange tubes 200 and the thickness of the heat exchange tube 200, on the one hand, the pressure resistance performance of the heat exchanger 1 can be ensured, and its reliability can be improved; on the other hand, the corrosion resistance performance of the heat exchanger 1 can be ensured, the leakage risk can be reduced, and the reliability can be further improved. Thus, both the pressure resistance performance can be ensured, the heat exchange efficiency per unit area can be improved, and the water temperature distribution can be made uniform.

[0084] According to the heat exchanger 1 of the embodiment of the present invention, by using the header pipe 100 according to the above embodiment of the present invention, it has the advantages of strong pressure resistance performance, high heat exchange efficiency, good heat exchange effect, uniform water temperature distribution, etc.

[0085] Next, the header pipe 100 according to the specific embodiment of the present invention will be described with reference to the accompanying drawings.

[0086] As Figures 2 - 5 shown, a plurality of slots 110 penetrating the peripheral wall of the header pipe 100 in the wall thickness direction of the header pipe 100 are provided on the peripheral wall of the header pipe 100. The length direction of each slot 110 is parallel to the axial direction of the header pipe 100, and the plurality of slots 110 are arranged at intervals along the axial direction of the header pipe 100.

[0087] Furthermore, the distance WE between adjacent slots 110 in the axial direction of the header pipe 100 is not less than one-tenth of the equivalent diameter DI of the header pipe 200, that is, WE ≥ DI / 10. In other words, the distance between adjacent heat exchange tubes 200 in the axial direction of the header pipe 100 is less than one-third of the equivalent diameter DI of the header pipe 200 and greater than or equal to one-tenth of the equivalent diameter DI of the header pipe 200. Preferably, the distance WE between adjacent slots 110 in the axial direction of the header pipe 100 is greater than one-fifth of the equivalent diameter DI of the header pipe 200, that is, WE > DI / 5. In other words, the distance between adjacent heat exchange tubes 200 in the axial direction of the header pipe 100 is less than one-third of the equivalent diameter DI of the header pipe 200 and greater than one-fifth of the equivalent diameter DI of the header pipe 200. Thereby, not only the welding quality between the heat exchange tube 200 and the header pipe 100 can be ensured, but also the local pressure can be further dispersed, thereby further improving the pressure resistance performance of the header pipe 100 and the heat exchanger 1.

[0088] In some specific embodiments of the present invention, such as Figures 2 - 5 shown, the distance WE between adjacent slots 110 in the axial direction of the header 100 is greater than the wall thickness DP of the header 100 and less than three times the wall thickness DP of the header 100, that is, DP < WE < 3DP. In other words, the distance between adjacent heat exchange tubes 200 in the axial direction of the header 100 is greater than the wall thickness DP of the header 100 and less than three times the wall thickness DP of the header 100, that is, DP < WE < 3DP. Without changing the installation area of the heat exchanger 1, by further defining the parameter relationship between the spacing of the heat exchange tubes 200 and the wall thickness of the header 100, on the one hand, the internal volume of the header 100 can be reduced to reduce the flow resistance of the heat exchanger 1; on the other hand, the heat exchange area can be increased to improve the heat exchange efficiency. Therefore, the parameter relationship within the above range can improve the heat exchange efficiency per unit area and the pressure resistance performance, and can reasonably distribute the solder joints to reduce the leakage risk. In some specific examples of the present invention, such as Figures 2 - 4 shown, the distance WE between adjacent slots 110 in the axial direction of the header 100 is less than one-third of the equivalent diameter DI of the header 200, that is, WE < DI / 3. After the inner tank of the heat pump water heater is shaped, the size of the installed heat exchanger 1 is usually fixed. According to the header 100 of the embodiment of the present invention, by setting the parameter relationship between the spacing WE of the slots 110 and the equivalent diameter DI of the header, the parameter relationship between the spacing of the heat exchange tubes 200 and the equivalent diameter DI of the heat exchange tubes 200 can be defined. Without changing the installation area of the heat exchanger 1, on the one hand, local pressure over-concentration can be avoided to ensure the pressure resistance performance of the heat exchanger 1, so as to meet the working requirements; on the other hand, the heat exchange efficiency per unit area can be ensured to improve the heat exchange effect and the uniformity of the water temperature distribution. That is, according to the header 100 of the embodiment of the present invention, by adjusting the spacing of the heat exchange tubes 200, the pressure resistance performance, the heat exchange effect and the uniformity of the water temperature distribution can be taken into account.

[0089] In some specific embodiments of the present invention, such as Figures 2 - 4 shown, the ratio of the product of the length WI and the width WH of the slot 110 to the distance WE between adjacent slots 110 in the axial direction of the header 100 is greater than 2 mm and less than 8 mm, that is, the ratio of the cross-sectional area of the slot 110 to the distance between adjacent slots 110 in the axial direction of the header 200 is between 2 mm and 8 mm, 2 mm < (WI * WH) / WE < 8 mm. In other words, the ratio of the cross-sectional area of the outer contour of the heat exchange tube 200 to the distance between adjacent heat exchange tubes 200 in the axial direction of the header 100 is greater than 2 mm and less than 8 mm. Thereby, the parameter relationship between the slotting area of the slot 110 and the spacing of the heat exchange tubes 200 can be defined. On the one hand, the heat exchange efficiency per unit area can be improved; on the other hand, the strength of the material and welding can be ensured, and the welding defects and damage of the heat exchange tubes 200 can be reduced, thereby improving the reliability of the heat exchanger 1.

[0090] In some specific examples of the present invention, such as Figures 2 - 5 shown, the ratio of the equivalent diameter DI of the header pipe to the product of the distance WE between adjacent slots 110 in the axial direction of the header pipe 100 and the wall thickness DP of the header pipe 100 is greater than 1.7 mm -1 and less than 5 mm -1 , that is, 1.7 mm -1 <DI / (WE*DP)<5 mm -1 . In other words, the ratio of the equivalent diameter DI of the header pipe to the product of the distance between adjacent heat exchange pipes 200 in the axial direction of the header pipe 100 and the wall thickness DP of the header pipe 100 is greater than 1.7 mm -1 and less than 5 mm -1 . Thus, on the one hand, the number of solder joints can be reduced, the pressure resistance of the heat exchanger 1 can be improved, and the leakage risk can be further reduced; on the other hand, the heat exchange area of the heat exchanger 1 can be increased, and the heat exchange effect can be enhanced.

[0091] In some specific embodiments of the present invention, such as Figures 2 - 5 shown, the ratio of the product of the equivalent diameter DI of the header pipe and the wall thickness DP of the header pipe 100 to the length WI of the slot 110 is greater than 0.9 mm and less than 4 mm, that is, 0.9 mm < (DI*DP) / WI < 4 mm. In other words, the ratio of the product of the equivalent diameter DI of the header pipe 100 and the wall thickness DP of the header pipe 100 to the width of the heat exchange pipe 200 is greater than 0.9 mm and less than 4 mm. In this way, on the one hand, the pressure resistance of the heat exchanger 1 can be improved, thereby improving the reliability; on the other hand, the internal volume of the header pipe 100 can be reduced, the refrigerant filling amount can be reduced, and the reliability of the operation of the heat exchanger 1 can be further increased. In some other specific embodiments of the present invention, such as Figure 6 shown, it is convenient for installation and positioning, the length of the heat exchange pipe 200 inserted into the header pipe 100 can be effectively controlled, the welding strength can be improved, thereby improving the pressure resistance of the heat exchanger 1. The end of the heat exchange pipe 200 is provided with a reduced opening. The width WI' of the heat exchange pipe 200 is greater than the length WI of the slot 110, the thickness WH' of the heat exchange pipe 200 is greater than the width WH of the slot 110, and the distance WE' between adjacent heat exchange pipes 200 is less than the distance WE between adjacent slots 110. At this time, the size parameters of the slot 110 need to be adjusted adaptively according to the size of the reduced opening, so as to ensure:

[0092] The ratio of the distance WE' between adjacent heat exchange pipes 200 in the axial direction of the header pipe 100 to the thickness WH' of the heat exchange pipe 200 is greater than 0.9 and less than 4, that is, 0.9 < WE' / WH' < 4.

[0093] The ratio of the cross-sectional area of the outer circumference of the non-necked portion of the heat exchange tube 200 to the distance WE' between adjacent heat exchange tubes 200 in the axial direction of the header 100 is greater than 2 mm and less than 8 mm, that is, 2 mm < (WI' * WH') / WE' < 8 mm.

[0094] The ratio of the product of the equivalent diameter DI of the header 100 and the wall thickness DP of the header 100 to the width WI' of the heat exchange tube 200 is greater than 0.9 mm and less than 4 mm, that is, 0.9 mm < (DI * DP) / WI' < 4 mm.

[0095] Other configurations and operations of the heat exchanger 1 according to the embodiments of the present invention are known to those of ordinary skill in the art and will not be described in detail here.

[0096] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and 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, and therefore should not be construed as a limitation of the present invention.

[0097] In addition, the terms "first" and "second" are only used for descriptive purposes and should not be construed as indicating or implying relative importance or implicitly specifying the quantity 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 invention, the meaning of "a plurality" is at least two, such as two, three, etc., unless otherwise specifically defined.

[0098] In the present invention, unless otherwise clearly defined and limited, the terms "mounted", "connected", "connected", "fixed", etc. should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or integrated; 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 internal communication of two elements or the interaction relationship between 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.

[0099] In the description of this specification, the descriptions referring to terms such as "one embodiment", "some embodiments", "examples", "specific examples", or "some examples", etc. mean 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. In addition, those skilled in the art can combine and combine the different embodiments or examples described in this specification.

[0100] Although the embodiments of the present invention have been shown and described above, it can be understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those of ordinary skill in the art can make changes, modifications, substitutions, and variations to the above embodiments within the scope of the present invention.

Claims

1. A manifold, characterized in that, A plurality of slot holes penetrating through the peripheral wall of the header pipe in the wall thickness direction of the header pipe are provided on the peripheral wall of the header pipe. The length direction of each slot hole is parallel to the axial direction of the header pipe, and the plurality of slot holes are arranged at intervals along the axial direction of the header pipe. Wherein, the distance between adjacent slot holes in the axial direction of the header pipe is less than one-third of the equivalent diameter of the header pipe, and the distance between adjacent slot holes in the axial direction of the header pipe is greater than the wall thickness of the header pipe and less than three times the wall thickness of the header pipe.

2. The manifold according to claim 1, wherein The distance between adjacent slot holes in the axial direction of the header pipe is not less than one-tenth of the equivalent diameter of the header pipe.

3. The manifold according to claim 1, wherein, The distance between adjacent slot holes in the axial direction of the header pipe is greater than one-fifth of the equivalent diameter of the header pipe.

4. The manifold according to any one of claims 1-3, characterized in that The ratio of the cross-sectional area of the slot hole to the distance between adjacent slot holes in the axial direction of the header pipe is between 2 mm and 8 mm.

5. The manifold according to any one of claims 1-3, characterized in that, The ratio of the equivalent diameter of the header pipe to the product of the distance between adjacent slots in the axial direction of the header pipe and the wall thickness of the header pipe is between 1.7 mm -1 and 5 mm -1 inclusive.

6. The manifold according to any one of claims 1-3, characterized in that The ratio of the product of the equivalent diameter of the header pipe and the wall thickness of the header pipe to the length of the slot hole is between 0.9 mm and 4 mm.

7. A heat exchanger, characterized in that, Comprising: A header pipe, the header pipe being the header pipe according to any one of claims 1-6; A plurality of heat exchange pipes, and the end portions of the plurality of heat exchange pipes are respectively inserted into the plurality of slot holes of the header pipe.

8. The heat exchanger according to claim 7, characterized in that, The heat exchange pipe is a flat pipe, and the ratio of the distance between adjacent heat exchange pipes in the axial direction of the header pipe to the thickness of the heat exchange pipe is between 0.9 and 4.

9. The heat exchanger according to claim 7, characterized in that, The heat exchange pipe is a flat pipe, and the ratio of the cross-sectional area of the heat exchange pipe to the distance between adjacent heat exchange pipes is between 2 mm and 8 mm.

10. The heat exchanger according to claim 8 or 9, characterized in that, The ratio of the product of the equivalent diameter of the header pipe and the wall thickness of the header pipe to the width of the heat exchange pipe is between 0.9 mm and 4 mm.

11. A manifold, characterized in that, A plurality of slot holes penetrating through the peripheral wall of the header pipe in the wall thickness direction of the header pipe are provided on the peripheral wall of the header pipe. The length direction of each slot hole is parallel to the axial direction of the header pipe, and the plurality of slot holes are arranged at intervals along the axial direction of the header pipe. Wherein, the ratio of the distance between adjacent slot holes in the axial direction of the header pipe to the width of the slot hole is between 0.9 and 4.

12. The manifold according to claim 11, wherein The distance between adjacent slot holes in the axial direction of the header pipe is less than one-third of the equivalent diameter of the header pipe.

13. The header according to claim 11, characterized in that, The distance between adjacent slot holes in the axial direction of the header pipe is not less than one-tenth of the equivalent diameter of the header pipe.

14. The manifold according to claim 11, wherein The distance between adjacent slot holes in the axial direction of the header pipe is greater than one-fifth of the equivalent diameter of the header pipe.

15. The manifold according to any one of claims 11-14, characterized in that, The distance between adjacent slot holes in the axial direction of the header pipe is greater than the wall thickness of the header pipe and less than three times the wall thickness of the header pipe.

16. The manifold according to any one of claims 11-14, characterized in that, The ratio of the cross-sectional area of the slot hole to the distance between adjacent slot holes in the axial direction of the header pipe is between 2 mm and 8 mm.

17. The manifold according to any one of claims 11-14, characterized in that, The ratio of the equivalent diameter of the header pipe to the product of the distance between adjacent slots in the axial direction of the header pipe and the wall thickness of the header pipe is between 1.7 mm -1 and 5 mm -1 inclusive.

18. The header according to any one of claims 11-14, characterized in that, The ratio of the product of the equivalent diameter of the header pipe and the wall thickness of the header pipe to the length of the slot hole is between 0.9 mm and 4 mm.

19. A heat exchanger, characterized in that, Comprising: A header pipe, the header pipe being the header pipe according to any one of claims 11-18; A plurality of heat exchange pipes, and the end portions of the plurality of heat exchange pipes are respectively inserted into the plurality of slot holes of the header pipe.

20. The heat exchanger according to claim 19, wherein, The heat exchange tubes are flat tubes, and the ratio of the distance between adjacent heat exchange tubes in the axial direction of the header to the thickness of the heat exchange tubes is between 0.9 and 4.

21. The heat exchanger according to claim 19, characterized in that, The heat exchange tubes are flat tubes, and the ratio of the cross-sectional area of the heat exchange tubes to the spacing between adjacent heat exchange tubes is between 2 mm and 8 mm.

22. The heat exchanger according to claim 20 or 21, characterized in that, The ratio of the product of the equivalent diameter of the header and the wall thickness of the header to the width of the heat exchange tubes is between 0.9 mm and 4 mm.

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