Plate heat exchanger and water electrolysis hydrogen production test system
By designing the interlaced flow channel structure and slope structure in the plate heat exchanger, the problem of insufficient pressure resistance in the low-power electrolytic hydrogen production system is solved, and efficient and low-cost electrolytic hydrogen production test is achieved.
Patent Information
- Application Number
- CN202510410028.0
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-04-02
- Publication Date
- 2025-07-25
AI Technical Summary
The existing plate heat exchangers lack pressure resistance in low-power electrolytic hydrogen production systems, resulting in large area and high test costs.
A plate heat exchanger is designed, using a runner structure including a runner body and a slope structure. The runner body and the surface of the heat exchanger sheet extend inclinedly. The runner structure is arranged interlaced on both sides of the heat exchanger sheet, and combined with 316L stainless steel material, it achieves high pressure resistance.
The pressure resistance of the runner structure is improved, the floor area and testing cost of the electrolytic water hydrogen production test system is reduced, and the heat exchange efficiency is improved.
Smart Images
Figure CN120368758A_ABST
Abstract
Description
Technical Field
[0001] The present application relates to the technical field of electrolytic water hydrogen production cells, and more particularly, to a plate heat exchanger and an electrolytic water hydrogen production test system. Background Art
[0002] With the rapid rise of the new energy field, the development and application of hydrogen fuel cells have gradually occupied the mainstream market, and the research on electrolytic water hydrogen production and supporting test systems has become increasingly in-depth. The pressure of the electrolytic water hydrogen production circulation loop is usually 3.5 - 5 Mpa, while the conventional plate heat exchangers on the market can usually only reach about 2 Mpa. If a heat exchanger with a higher pressure resistance is selected, not only the selection cost increases, but also the volume is relatively large, which will occupy a large test site for small-power hydrogen production systems / test benches.
[0003] In the application field of small-power electrolyzer equipment, there is an urgent need for a plate heat exchanger as a substitute for medium-sized and large-sized shell-and-tube and sleeve heat exchangers, which has the characteristics of low cost and convenient operation. Summary of the Invention
[0004] To this end, the present application provides a plate heat exchanger and an electrolytic water hydrogen production test system. The plate heat exchanger has a simple structure, occupies a small area, has a high pressure resistance, and reduces the floor area and test cost of the electrolytic water hydrogen production test system.
[0005] The plate heat exchanger according to the first aspect embodiment of the present application is applied to an electrolytic water hydrogen production test system, and includes a first end plate, a second end plate, and heat exchange fins. The heat exchange fins are disposed between the first end plate and the second end plate. A cold-side flow channel is formed between the heat exchange fins and the first end plate, and a hot-side flow channel is formed between the heat exchange fins and the second end plate. Wherein, both sides of the heat exchange fins include a plurality of spaced flow channel structures. The flow channel structure includes a flow channel body and ramp structures at both ends. The ramp structures extend obliquely from the flow channel body towards the surface of the heat exchange fins.
[0006] According to some embodiments of the present application, the heat exchange fins have a square sheet structure. A plurality of the flow channel structures on the same side of the heat exchange fins are spaced along the length direction of the heat exchange fins. The length direction of the flow channel body extends along the width direction of the heat exchange fins, and the ramp structures are respectively disposed at both ends in the length direction of the flow channel body.
[0007] According to some embodiments of the present application, the height difference between the flow channel body and the heat exchange fins is H, the dimension of the ramp structure in the length direction of the heat exchange fins is L, and the dimension of the ramp structure in the width direction of the heat exchange fins is W, satisfying: 0.4H ≤ L ≤ 0.6H, 0.4H ≤ W ≤ 0.6H.
[0008] According to some embodiments of the present application, both sides of the heat exchange fin in the thickness direction include a first surface and a second surface, and the flow channel structures on the first surface and the second surface are arranged alternately.
[0009] According to some embodiments of the present application, the flow channel structure provided on the first surface is recessed into the first surface, and the flow channel structure provided on the second surface is recessed into the second surface.
[0010] According to some embodiments of the present application, the first end plate includes a first inlet and a first outlet, both the first inlet and the first outlet are communicated with the cold-side flow channel, the second end plate includes a second inlet and a second outlet, and both the second inlet and the second outlet are communicated with the hot-side flow channel.
[0011] According to some embodiments of the present application, the first inlet and the first outlet are arranged diagonally, and the second inlet and the second outlet are arranged diagonally.
[0012] According to some embodiments of the present application, a first sealing ring is provided between the heat exchange fin and the first end plate, and a second sealing ring is provided between the heat exchange fin and the second end plate.
[0013] According to some embodiments of the present application, the material of the heat exchange fin is 316L stainless steel.
[0014] The electrolytic water hydrogen production test system according to the second aspect embodiment of the present application includes the plate heat exchanger according to the first aspect embodiment of the present application.
[0015] Compared with the prior art, the present solution has the following beneficial effects:
[0016] Both ends of the flow channel structure of the plate heat exchanger according to the embodiment of the present application are provided with slope structures, which can reduce the resistance when the cold-side or hot-side fluid passes through the flow channel, so it has better pressure resistance. It not only occupies a small area but also has good pressure resistance, reducing the floor area and test cost of the electrolytic water hydrogen production test system.
[0017] The additional aspects and advantages of the present application will be partially given in the following description, partially become obvious from the following description, or be understood through the practice of the present application. Description of the Drawings
[0018] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the following will briefly introduce the drawings required in the embodiments. It should be understood that the following drawings only show some embodiments of the present application, so they should not be regarded as limiting the scope. For those of ordinary skill in the art, without creative efforts, other related drawings can also be obtained based on these drawings.
[0019] Figure 1 The structural schematic diagram of the plate heat exchanger provided by the embodiment of the present application from the first perspective;
[0020] Figure 2 The structural schematic diagram of the plate heat exchanger provided by the embodiment of the present application from the second perspective (the first sealing ring and the second sealing ring are not shown);
[0021] Figure 3 The structural schematic diagram of the first surface of the heat exchange fin of the plate heat exchanger provided by the embodiment of the present application;
[0022] Figure 4 It is Figure 3 The partial enlarged view at position A in
[0023] Figure 5 The structural schematic diagram of the second surface of the heat exchange fin of the plate heat exchanger provided by the embodiment of the present application;
[0024] Figure 6 It is Figure 5 The sectional view taken along line B-B in
[0025] Figure 7 It is Figure 6 The partial enlarged view at position C in
[0026] Icon: 100 - plate heat exchanger; 110 - first end plate; 111 - first inlet; 112 - first outlet; 113 - cold side flow channel; 114 - first sealing ring; 115 - first mounting hole; 120 - second end plate; 121 - second inlet; 122 - second outlet; 123 - hot side flow channel; 130 - heat exchange fin; 131 - first surface; 132 - second surface; 133 - flow channel structure; 1331 - flow channel main body; 1332 - ramp structure; 134 - third mounting hole; 135 - sealing groove. Detailed implementation manners
[0027] To make the objectives, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are some, but not all, of the embodiments of the present application. Usually, the components of the embodiments of the present application described and illustrated in the accompanying drawings here can be arranged and designed in various different configurations.
[0028] Therefore, the following detailed description of the embodiments of the present application provided in the accompanying drawings is not intended to limit the scope of the present application claimed, but merely represents the selected embodiments of the present application. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present application without creative efforts shall fall within the protection scope of the present application.
[0029] As Figure 1 shown Figure 2 in Figure 3 Figures Figure 4 72, 73, 74, 75, and 76, some embodiments of the plate heat exchanger 100 of the present application are applied to an electrolytic water hydrogen production test system, including a first end plate 110, a second end plate 120, and heat exchange fins 130. The heat exchange fins 130 are disposed between the first end plate 110 and the second end plate 120. A cold-side flow channel 113 is formed between the heat exchange fins 130 and the first end plate 110, and a hot-side flow channel 123 is formed between the heat exchange fins 130 and the second end plate 120. Among them, both sides of the heat exchange fins 130 include a plurality of spaced flow channel structures 133. The flow channel structure 133 includes a flow channel main body 1331 and ramp structures 1332 at both ends. The ramp structures 1332 extend obliquely from the flow channel main body 1331 towards the surface of the heat exchange fins 130.
[0030] The flow channel structure 133 may extend linearly, or may extend in a zigzag or wavy line shape; the flow channel structure 133 may extend along the width direction of the heat exchange fins 130, or may extend in other directions of the heat exchange fins 130; the flow channel structure 133 is recessed into the surface of the heat exchange fins 130. One end of the ramp structure 1332 is connected to the flow channel main body 1331, and the other end may extend to the surface of the heat exchange fins 130, or may extend to the side wall of the flow channel structure 133, and there is a spacing between it and the surface of the heat exchange fins 130; the ramp structure 1332 may be a plane, or may be an arc surface or a multi-segment surface.
[0031] Both sides of the heat exchange fins 130 in the thickness direction include a first surface 131 and a second surface 132. The gap between the first surface 131 and the first end plate 110 forms the cold-side flow channel 113, and the gap between the second surface 132 and the second end plate 120 forms the hot-side flow channel 123; the plate heat exchanger 100 is disposed in the electrolytic water hydrogen production circulation loop. The hot-side flow channel 123 is communicated with the return water pipeline of deionized water for hydrogen production, and the cold-side flow channel 113 is communicated with an external cooling water source to cool the return water of deionized water.
[0032] The ramp structures 1332 are provided at both ends of the flow channel structure 133 of the plate heat exchanger 100 according to the embodiments of the present application, which can reduce the resistance of the cold-side or hot-side fluid passing through the flow channel, and thus has better pressure resistance. It not only occupies a small area, but also has better pressure resistance, reducing the floor area and test cost of the electrolytic water hydrogen production test system.
[0033] As Figure 3 shown Figure 4 in Figure 5As shown, in some embodiments of the present application, the heat exchange fin 130 has a square sheet structure. A plurality of flow channel structures 133 on the same side of the heat exchange fin 130 are arranged at intervals along the length direction of the heat exchange fin 130. The length direction of the flow channel body 1331 extends along the width direction of the heat exchange fin 130, and slope structures 1332 are respectively arranged at both ends of the length direction of the flow channel body 1331.
[0034] Both ends of the flow channel structure 133 in the X direction do not extend to the edge of the heat exchange fin 130. That is to say, the flow channel structure 133 is formed inside the first surface 131 or the second surface 132.
[0035] The length direction of the heat exchange fin 130 extends along the Z direction, the width direction extends along the X direction, and the thickness direction extends along the Y direction. The flow channel structure 133 extends linearly. A plurality of flow channel structures 133 on the first surface 131 of the heat exchange fin 130 are arranged at intervals along the Z direction, and a plurality of flow channel structures 133 on the second surface 132 of the heat exchange fin 130 are arranged at intervals along the Z direction. The length direction of the flow channel body 1331 extends along the X direction, and slope structures 1332 are respectively arranged at both ends of the X direction of the flow channel body 1331.
[0036] Through this setting form, the structure of the heat exchange fin 130 can be simplified, and the heat exchange efficiency and pressure resistance of the heat exchange fin 130 and the plate heat exchanger 100 can be improved.
[0037] In other embodiments, the flow channel structure 133 can also extend along other directions, and the flow channel structure 133 can also be curved or zigzag, etc.
[0038] In some embodiments of the present application, the height difference between the flow channel body 1331 and the heat exchange fin 130 is H, the dimension of the slope structure 1332 in the length direction of the heat exchange fin 130 is L, and the dimension of the slope structure 1332 in the width direction of the heat exchange fin 130 is W, satisfying:
[0039] 0.4H ≤ L ≤ 0.6H, 0.4H ≤ W ≤ 0.6H.
[0040] As Figure 4 and Figure 7 shown, taking the flow channel structure 133 on the first surface 131 of the heat exchange fin 130 as an example, the surface difference in the Y direction between the flow channel body 1331 and the first surface 131 of the heat exchange fin 130 is H, the dimension of the slope structure 1332 in the X direction is L, and the dimension in the X direction is W.
[0041] The ramp structure 1332 is a planar structure. The flow channel structure 133 includes a bottom wall and two side walls in the X direction. One end of the ramp structure 1332 in the X direction is connected to the flow channel body 1331, and the other end is far away from the flow channel body 1331 and extends towards the direction close to the plane where the flow channel structure 133 is located until it is connected to the side wall on the same side in the X direction.
[0042] Limiting the above parameters within the above ranges can not only reduce the resistance of the hot side or the cold side water flow through, improve the pressure resistance of the plate heat exchanger 100, but also enable the heat exchange fins 130 to have better structural strength.
[0043] As a preferred embodiment, L = 0.5H and W = 0.5H.
[0044] In other embodiments, the ramp structure 1332 can also be an arc surface structure, and the other end of the ramp structure 1332 can also directly extend to the surface where the flow channel structure 133 is located.
[0045] Such as Figure 6 and Figure 7 shown, in some embodiments of the present application, both sides of the heat exchange fin 130 in the thickness direction include a first surface 131 and a second surface 132, and the flow channel structures 133 on the first surface 131 and the flow channel structures 133 on the second surface 132 are arranged staggeredly.
[0046] That is to say, in the XZ plane, the projections of the flow channel structures 133 on the first surface 131 and the flow channel structures 133 on the second surface 132 do not overlap.
[0047] Staggeringly arranging the flow channel structures 133 on both sides of the heat exchange fin 130 can, on the one hand, increase the heat exchange area and improve the heat exchange efficiency of the plate heat exchanger 100; on the other hand, the flow channel structures 133 arranged staggeredly on both sides can be used as the support structure of the panel, reducing the stress area of each surface and improving the pressure resistance.
[0048] In other embodiments, the projections of the flow channel structures 133 on the first surface 131 and the flow channel structures 133 on the second surface 132 can also be arranged to overlap.
[0049] Such as Figure 7 shown, in some embodiments of the present application, the flow channel structure 133 arranged on the first surface 131 is recessed into the first surface 131, and the flow channel structure 133 arranged on the second surface 132 is recessed into the second surface 132.
[0050] Through this setting form, the heat exchange area of the heat exchange fin 130 can be increased, and the heat exchange efficiency and pressure resistance of the heat exchange fin 130 can be improved.
[0051] In other embodiments, the flow channel structure 133 can also be a flow disturbing structure protruding from the heat exchange fins 130.
[0052] As Figure 1 and Figure 2 shown, in some embodiments of the present application, the first end plate 110 includes a first inlet 111 and a first outlet 112. Both the first inlet 111 and the first outlet 112 are communicated with the cold-side flow channel 113. The second end plate 120 includes a second inlet 121 and a second outlet 122. Both the second inlet 121 and the second outlet 122 are communicated with the hot-side flow channel 123.
[0053] The first inlet 111 is communicated with an external cooling water source, and the first outlet 112 is communicated with the return water pipeline of the external cooling water source. The second inlet 121 and the second outlet 122 are connected in series on the return water pipeline of the deionized water for hydrogen production.
[0054] Through this setting form, it can be realized that the hot-side flow channel 123 is communicated with the return water pipeline of the deionized water for hydrogen production, and the cold-side flow channel 113 is communicated with the external cooling water source.
[0055] As Figure 1 and Figure 2 shown, in some embodiments of the present application, the first inlet 111 and the first outlet 112 are diagonally arranged, and the second inlet 121 and the second outlet 122 are diagonally arranged.
[0056] The first inlet 111 and the first outlet 112 are diagonally arranged in the Z direction, and the second inlet 121 and the second outlet 122 are diagonally arranged in the Z direction.
[0057] Through this setting form, the distance between the water inlet and the water outlet can be maximized, improving the heat exchange efficiency of the plate heat exchanger 100; the flow directions of the media in the cold-side flow channel 113 and the hot-side flow channel 123 are the same as the interval arrangement direction of the multiple flow channel structures 133, which can improve the heat exchange efficiency, reduce the flow resistance, and improve the pressure resistance in the media flow direction.
[0058] In some embodiments of the present application, the first inlet 111 is located at the upper corner of the first end plate 110, the first outlet 112 is located at the lower corner of the first end plate 110, the arrangement positions of the first inlet 111 and the second inlet 121 in the XZ plane are the same, and the arrangement positions of the first outlet 112 and the second outlet 122 in the XZ plane are the same, so as to realize the same structure of the first end plate 110 and the second end plate 120; in other embodiments, the structures of the first end plate 110 and the second end plate 120 can also be different, and the first inlet 111 can also be arranged at the lower corner of the first end plate 110.
[0059] As Figure 3 and Figure 6As shown, in some embodiments of the present application, a first sealing ring 114 is provided between the heat exchange fin 130 and the first end plate 110, and a second sealing ring is provided between the heat exchange fin 130 and the second end plate 120.
[0060] For example, a sealing groove 135 is provided on the first surface 131 of the heat exchange fin 130, and the first sealing ring 114 is installed in the sealing groove 135.
[0061] By providing the first sealing ring 114 and the second sealing ring, the cold-side flow channel 113 and the hot-side flow channel 123 can be sealed on the peripheral side, improving the sealing performance of the plate heat exchanger 100.
[0062] In some embodiments of the present application, the material of the heat exchange fin 130 is 316L stainless steel, which has a relatively low ion release rate in the field of electrolytic cell applications, making the conductivity of deionized water meet the requirements.
[0063] The first end plate 110 is provided with a plurality of first mounting holes 115, the second end plate 120 is provided with a plurality of second mounting holes, and the heat exchange fin 130 is provided with a plurality of third mounting holes 134. The first mounting holes 115, the second mounting holes, and the third mounting holes 134 are arranged in one-to-one correspondence, and the first end plate 110, the second end plate 120, and the heat exchange fin 130 are assembled into one body by means of threaded parts and nuts.
[0064] The electrolytic water hydrogen production test system of some embodiments of the present application includes a plate heat exchanger 100.
[0065] The structure of the plate heat exchanger 100 in the embodiments of the present application is simple. The flow channel structures 133 on the front and back sides of the heat exchange fin 130 are arranged in a staggered manner, having a relatively high heat exchange efficiency, and can improve the pressure resistance of the plate heat exchanger 100, meeting the development and application of small-power electrolytic cells.
[0066] It should be noted that, without conflict, the features in the embodiments of the present application can be combined with each other.
[0067] The above are only the preferred embodiments of the present application and are not intended to limit the present application. For those skilled in the art, the present application can have various changes and modifications. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.
Claims
1. A plate heat exchanger (100) is applied to an electrolytic water hydrogen production test system, and is characterized in that, It includes a first end plate (110), a second end plate (120) and heat exchange fins (130). The heat exchange fins (130) are arranged between the first end plate (110) and the second end plate (120). A cold-side flow channel (113) is formed between the heat exchange fins (130) and the first end plate (110), and a hot-side flow channel (123) is formed between the heat exchange fins (130) and the second end plate (120). Wherein, both sides of the heat exchange fins (130) include a plurality of spaced flow channel structures (133). The flow channel structures (133) include a flow channel body (1331) and ramp structures (1332) at both ends. The ramp structures (1332) extend obliquely from the flow channel body (1331) towards the surface of the heat exchange fins (130).
2. The plate heat exchanger (100) according to claim 1, wherein, The heat exchange fins (130) are in a square sheet structure. A plurality of the flow channel structures (133) on the same side of the heat exchange fins (130) are arranged at intervals along the length direction of the heat exchange fins (130). The length direction of the flow channel body (1331) extends along the width direction of the heat exchange fins (130), and the ramp structures (1332) are respectively arranged at both ends in the length direction of the flow channel body (1331).
3. The plate heat exchanger (100) according to claim 2, characterized in that, The height difference between the flow channel body (1331) and the heat exchange fins (130) is H. The dimension of the ramp structure (1332) in the length direction of the heat exchange fins (130) is L, and the dimension of the ramp structure (1332) in the width direction of the heat exchange fins (130) is W, satisfying: 0.4H ≤ L ≤ 0.6H, 0.4H ≤ W ≤ 0.6H.
4. The plate heat exchanger (100) according to claim 1, characterized in that, Both sides of the heat exchange fins (130) in the thickness direction include a first surface (131) and a second surface (132). The flow channel structures (133) on the first surface (131) and the flow channel structures (133) on the second surface (132) are arranged in an interleaved manner.
5. The plate heat exchanger (100) according to claim 4, characterized in that, The flow channel structures (133) arranged on the first surface (131) are recessed into the first surface (131), and the flow channel structures (133) arranged on the second surface (132) are recessed into the second surface (132).
6. The plate heat exchanger (100) according to claim 1, characterized in that, The first end plate (110) includes a first inlet (111) and a first outlet (112). Both the first inlet (111) and the first outlet (112) are communicated with the cold-side flow channel (113). The second end plate (120) includes a second inlet (121) and a second outlet (122). Both the second inlet (121) and the second outlet (122) are communicated with the hot-side flow channel (123).
7. The plate heat exchanger (100) according to claim 6, characterized in that, The first inlet (111) and the first outlet (112) are diagonally arranged, and the second inlet (121) and the second outlet (122) are diagonally arranged.
8. The plate heat exchanger (100) according to claim 1, characterized in that, A first sealing ring (114) is provided between the heat exchange fins (130) and the first end plate (110), and a second sealing ring is provided between the heat exchange fins (130) and the second end plate (120).
9. The plate heat exchanger (100) according to claim 1, characterized in that, The material of the heat exchange fins (130) is 316L stainless steel.
10. An electrolytic water hydrogen production test system, characterized in that, Comprising a plate heat exchanger (100) according to any one of claims 1 to 9.