Heat exchange core and water vapor generator

Abstract

This invention discloses a heat exchange core and a steam generator. The heat exchange core includes multiple baffles spaced apart along a first direction and filler particles. Adjacent baffles enclose a flow channel, and the multiple flow channels are sequentially assigned as alternating hot and cold flow channels. Each baffle includes a base plate and baffle structures. The base plate has a cold side facing the cold flow channel, and the baffle structures protrude from the cold side and extend along a second direction. The baffle structures of two adjacent baffles forming the cold flow channel abut against each other, dividing the corresponding cold flow channel into an evaporation section and a superheated section distributed and interconnected along a third direction. The evaporation section is filled with filler particles. The first and second directions are perpendicular to the third direction. This invention effectively suppresses pressure fluctuations caused by vaporization and ensures more stable steam pressure from the cold flow channel.

Description

Technical Field

[0001] This invention relates to the field of heat exchange technology, and in particular to a heat exchange core and a steam generator. Background Technology

[0002] Heat exchangers enable heat transfer between two or more fluids at different temperatures and are widely used in electrochemical energy conversion systems such as fuel cell systems and electrolyzer systems. Water vapor plays a crucial role in solid oxide fuel cell power generation systems, heating liquid water to form high-temperature steam; such heat exchangers are commonly called steam generators. The pressure and flow rate of water vapor affect the stability of fuel cell operation, so maintaining a stable water vapor supply over a long period is a critical design consideration for steam generators. Convection-type steam generators are the most common. The heat exchange core of a convection-type steam generator consists of multiple spaced baffles that divide the core into hot and cold flow channels. Corrugated plates on the baffles enhance heat exchange efficiency.

[0003] However, existing convection heat exchange steam generators typically have corrugated structures on both sides of the baffle. During the boiling process of liquid water, the liquid water in the cold flow channel undergoes a phase change, and bubbles are continuously generated at the vaporization point. The generation and breakup of these bubbles cause pressure and flow fluctuations, and the steam flow and pressure fluctuations are large. This results in unstable output from the steam generator and large pressure fluctuations, which affects the use of subsequent systems. Summary of the Invention

[0004] The technical problem to be solved by the present invention is that during the boiling process of liquid water in the steam generator, the liquid water in the cold flow channel undergoes a phase change, and bubbles are continuously generated at the vaporization position. The generation and breaking of bubbles will cause pressure fluctuations and flow fluctuations, and the steam flow rate and steam pressure fluctuate greatly, which leads to unstable output of the steam generator.

[0005] To solve the above-mentioned technical problems, the present invention provides a heat exchange core, comprising a plurality of partitions spaced apart along a first direction and filling particles, wherein a flow channel is formed between two adjacent partitions, and the plurality of flow channels are sequentially assigned as alternating hot flow channels and cold flow channels. The partition includes a base plate portion and a baffle structure. The base plate portion has a cold side surface facing the cold flow channel. The baffle structure protrudes from the cold side surface and extends along a second direction. The baffle structures of two adjacent partitions surrounding the cold flow channel abut each other to divide the corresponding cold flow channel into an evaporation section and a superheating section that are distributed and interconnected along a third direction. The evaporation section is filled with the filler particles. The first direction, the second direction, and the third direction are perpendicular to each other.

[0006] Furthermore, the baffle structure includes a ridge and a support platform. The ridge protrudes from the cold side and the support platform protrudes from the ridge toward the cold flow channel. A plurality of support platforms are spaced apart along the extension direction of the ridge. The support platforms of two adjacent partitions surrounding the cold flow channel abut against each other, so that a cold flow through hole connecting the evaporation section and the superheated section is formed between the ridges of the two partitions.

[0007] Furthermore, the partition is a one-piece structure; The substrate portion has a hot side facing the hot flow channel, and the baffle structure further includes a first protrusion that protrudes from the hot side and abuts against the first protrusions of two adjacent baffles surrounding the hot flow channel.

[0008] Furthermore, the baffle structure also includes a protruding ring formed on the cold side and a first recess. The height of the protruding ring is the same as the height of the support platform. The protruding rings of two adjacent partitions forming the cold flow channel abut each other. The first recess is located in the middle of the protruding ring, and the periphery of the protruding ring is recessed to form a notch communicating with the first recess.

[0009] Furthermore, the height of the ridge relative to the substrate is h1, and the height of the support platform relative to the substrate is h2, h1 < h2, and h1:h2 = (0.1-0.9):1.

[0010] Furthermore, the particle size of the filler particles is larger than the particle size of the cold flow through-hole, and D > 2*(h2-h1), where D is the particle size of the filler particles.

[0011] Furthermore, the filler particles are one or more of ceramic particles or metal particles.

[0012] Furthermore, the partition also includes a raised strip and a boss, the raised strip protruding from the hot side surface, the boss protruding from the raised strip and / or the hot side surface, and the height of the boss is greater than the height of the raised strip, and the bosses of two adjacent partitions forming the hot flow channel abut against each other.

[0013] Furthermore, the cold flow inlet of the cold flow channel is located in the evaporation section, and the cold flow outlet of the cold flow channel is located in the superheated section, so that the fluid in the cold flow channel flows along the evaporation section toward the superheated section, and the fluid flow direction of the cold flow channel is opposite to the fluid flow direction of the hot flow channel.

[0014] The present invention also provides a steam generator, comprising the heat exchange core as described above.

[0015] Compared with the prior art, the heat exchange core and steam generator of this invention have the following advantages: This invention utilizes a baffle structure to divide the cold flow channel into a connected evaporation section and a superheating section. During operation, liquid water is introduced into the cold flow channel, and high-temperature exhaust gas is introduced into the hot flow channel. The liquid water enters the heat exchange core and boils and vaporizes into water vapor in the evaporation section. Because the evaporation section is filled with packing particles, pressure fluctuations caused by vaporization are effectively suppressed, ensuring a more stable water vapor pressure exiting the cold flow channel. The water vapor passes through the baffle structure to reach the superheating section, where it continues to heat up to the required temperature before finally leaving the heat exchange core. Furthermore, the baffle structure also prevents the packing particles from overflowing into the superheating section. Attached Figure Description

[0016] The present application will be further described in detail below with reference to the accompanying drawings and preferred embodiments. However, those skilled in the art will appreciate that these drawings are drawn only for the purpose of explaining the preferred embodiments and therefore should not be construed as limiting the scope of the present application. Furthermore, unless specifically indicated, the drawings are intended only to conceptually represent the composition or structure of the described objects and may contain exaggerated representations, and the drawings are not necessarily drawn to scale.

[0017] Figure 1 This is a schematic diagram of the structure of the heat exchange core provided in an embodiment of the present invention; Figure 2 This is a front view of two plate pairs provided in an embodiment of the present invention; Figure 3 This is provided along with the embodiments of the present invention. Figure 2 A cross-sectional view along the AA direction; Figure 4 This is a schematic diagram of the cold side surface of the partition provided in an embodiment of the present invention; Figure 5 This is provided by the embodiments of the present invention. Figure 4 A magnified view of part A circled in the diagram; Figure 6 This is a schematic diagram of the thermal side surface of the partition provided in an embodiment of the present invention; Figure 7 This is provided by the embodiments of the present invention. Figure 6A magnified view of part B circled in the diagram; Figure 8 This is provided along with the embodiments of the present invention. Figure 2 A cross-sectional view along the BB direction; Figure 9 This is provided by the embodiments of the present invention. Figure 8 A magnified view of part C circled in the diagram; Figure 10 This is a schematic diagram of the structure of two plate pairs provided in an embodiment of the present invention; Figure 11 This is an exploded view of two plate pairs provided in an embodiment of the present invention; Figure 12 This is provided by the embodiments of the present invention. Figure 10 A magnified view of part D circled in the diagram; In the figure, 1 is a partition; 11 is a base plate; 111 is a cold side; 112 is a hot side; 12 is a baffle structure; 121 is a raised ridge; 122 is a support platform; 123 is a first protrusion; 124 is a raised ring; 125 is a first recess; 126 is a notch; 13 is a raised strip; 14 is a boss; 15 is a second recess; 16 is a groove; 17 is a second protrusion; 18 is a third protrusion; 2 is a flow channel; 21 is a cold flow channel; 211 is an evaporation section; 212 is a superheated section; 213 is a cold flow inlet; 214 is a cold flow outlet; 22 is a hot flow channel; 221 is a hot flow inlet; 222 is a hot flow outlet; 23 is a cold flow through-hole; and 3 is a sealing key. Detailed Implementation

[0018] Embodiments of the present invention are described in detail below, examples of which are illustrated 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 intended to explain the present invention, and should not be construed as limiting the present invention.

[0019] like Figures 1 to 3 As shown, the present invention provides a heat exchange core, comprising multiple partitions 1 spaced apart along a first direction and filler particles (not shown). Adjacent partitions 1 enclose a flow channel 2, which is sequentially assigned as alternating hot flow channels 22 and cold flow channels 21. Understandably, adjacent cold flow channels 21 and hot flow channels 22 share a partition 1, meaning one side of a partition 1 contacts the cold flow channel 21 and the other side contacts the hot flow channel 22, thus preventing communication between the two. Liquid water is introduced into the cold flow channel 21, transforming into high-temperature steam after heat exchange. High-temperature exhaust gas generated by the fuel cell system is introduced into the hot flow channel 22, which can also be other high-temperature gases.

[0020] In addition, such as Figure 3 and Figure 4 As shown, the partition 1 includes a substrate portion 11 and a baffle structure 12. The substrate portion 11 has a cold side surface 111 facing the cold flow channel 21. The baffle structure 12 protrudes from the cold side surface 111 and extends along a second direction. The baffle structures 12 of two adjacent partitions 1 that form the cold flow channel 21 abut against each other to divide the corresponding cold flow channel 21 into an evaporation section 211 and a superheating section 212 that are distributed along a third direction and are interconnected. The evaporation section 211 is filled with filler particles, wherein the first direction, the second direction and the third direction are perpendicular to each other.

[0021] During the heat exchange process, liquid water heats up, boils, and vaporizes, generating a large number of bubbles. This causes significant pressure fluctuations in the cold flow channel 21, resulting in unstable water vapor pressure exiting the cold flow channel 21, which can easily affect the operation of subsequent systems. This embodiment uses a baffle structure 12 to divide the cold flow channel 21 into a connected evaporation section 211 and a superheating section 212. During operation, liquid water is introduced into the cold flow channel 21, and high-temperature exhaust gas is introduced into the hot flow channel 22. After entering the heat exchange core, the liquid water boils and vaporizes in the evaporation section 211, turning into water vapor. Because the evaporation section 211 is filled with packing particles, the pressure fluctuations caused by vaporization are effectively suppressed, ensuring a more stable water vapor pressure exiting the cold flow channel 21. The water vapor passes through the baffle structure 12 to reach the superheating section 212, where it continues to heat up to the required temperature before finally leaving the heat exchange core.

[0022] Understandably, there are gaps between the filling particles to allow the flow of cold air (i.e., water vapor after the liquid water in the cold flow channel 21 has vaporized). In addition, the baffle structure 12 can prevent the filling particles from leaking out of the evaporation section 211 into the superheated section 212. At the same time, the baffle structure 12 partially abuts and does not contact other parts. The non-contacting parts form cold flow gaps, which only allow water vapor to pass through, ensuring that the particles do not enter the superheated section 212.

[0023] It should be noted that in this embodiment, two adjacent partitions 1 are configured as a pair of plates. The two partitions 1 of the pair of plates enclose each other to form a cold flow channel 21, and the two adjacent pairs of plates enclose each other to form a hot flow channel 22, so that the two baffle structures 12 in each pair of plates abut against each other to divide the corresponding cold flow channel 21 into an evaporation section 211 and a superheating section 212 that are distributed along a third direction and are interconnected.

[0024] Understandably, in this embodiment, two adjacent partitions 1 are configured as a plate pair. The two partitions 1 of the plate pair enclose each other to form a hot flow channel 22, and two adjacent plate pairs enclose each other to form a cold flow channel 21. At this time, the two baffle structures 12 of the two adjacent plate pairs abut each other to separate the corresponding cold flow channel 21 into an evaporation section 211 and a superheating section 212 that are distributed along a third direction and are interconnected. Without special limitation, this embodiment only requires two partitions 1 to enclose each other to form an independent flow channel 2, and another flow channel 2 to be formed between the plate pairs to ensure that the hot and cold fluids are distributed alternately.

[0025] like Figure 5 As shown, the baffle structure 12 includes a ridge 121 and a support platform 122. The ridge 121 protrudes from the cold side 111, and the support platform 122 protrudes from the ridge 121 toward the cold flow channel 21. Multiple support platforms 122 are spaced apart along the extension direction of the ridge 121. The support platforms 122 of two adjacent partitions 1 surrounding the cold flow channel 21 abut against each other, so that a cold flow through hole 23 connecting the evaporation section 211 and the superheated section 212 is formed between the ridges 121 of the two partitions 1.

[0026] In this embodiment, after the two partitions 1 are installed in a pair, the support platforms 122 arranged opposite each other abut against each other, which not only provides support and improves the deformation resistance of the partitions 1, but also strengthens the baffle structure 12. At the same time, it forms a cold flow passage 23 for cold flow to pass through and prevents the filling particles filled in the cold flow channel 21 from entering the overheating section 212.

[0027] It should be noted that the temperature of the superheated section 212 is relatively high, and the thermal deformation of the baffle 1 is large. The cold flow channel 21 will be expanded, and the baffle 1 will deform towards the hot flow channel 22. The cold flow through hole 23 is also easily expanded. If the cold flow channel 21 is completely filled with filler particles, at high temperatures, the particles in the superheated section 212 will easily settle into the evaporation section 211 under the action of gravity, which will open up the position of the baffle 1 in the evaporation section 211. Since the particles settle in the evaporation section 211, the baffle 1 cannot be restored after the temperature drops, which will make the baffle 1 unusable in the future. Therefore, in this embodiment, it is only necessary to fill the evaporation section 211 with filler particles, and it is not necessary to fill the superheated section 212. In addition, there is no vaporization process in the superheated section 212, and the pressure fluctuation is not large, so it is not necessary to fill with particles to suppress the pressure fluctuation.

[0028] like Figure 6 and Figure 7 As shown, the partition 1 is an integral structure; the substrate portion 11 has a hot side surface 112 facing the hot flow channel 22, and the baffle structure 12 also includes a first protrusion 123, which protrudes from the hot side surface 112 and the first protrusions 123 of two adjacent partitions 1 surrounding the hot flow channel 22 abut against each other.

[0029] In this embodiment, by providing a first protrusion 123 on the hot side 112, the first protrusion 123 can support the hot runner 22 when the partitions 1 on both sides of the hot runner 22 are installed together, ensuring that the hot runner 22 will not deform excessively under pressure, thus improving its resistance to deformation. In addition, the cooperation between the first protrusion 123, the ridge 121, and the support platform 122 ensures that the baffle structure 12 is provided with a supporting structure on both the cold runner 21 side and the hot runner 22 side. Even if the cold flow expands and compresses the hot runner 22, the first protrusion 123 can still provide support, so that the baffle structure 12 will not deform in the direction of the hot runner 22, and the two support platforms 122 can still firmly abut against each other, preventing the cold flow from pushing open the abutment between the support platforms 122 and causing the cold flow through hole 23 to be enlarged.

[0030] This embodiment ensures the reliability of the connection between the support platforms 122 by providing support structures on both sides of the partition 1. Furthermore, the number of first protrusions 123 can be set according to actual conditions; in this embodiment, two are provided.

[0031] like Figure 5 , Figure 8 and Figure 9 As shown, the baffle structure 12 also includes a protruding ring 124 and a first recess 125 protruding from the cold side 111. The height of the protruding ring 124 is the same as the height of the support platform 122. The protruding rings 124 of the two adjacent baffles 1 forming the cold flow channel 21 abut against each other. The first recess 125 is located in the middle of the protruding ring 124, and the periphery of the protruding ring 124 is recessed to form a notch 126 that communicates with the first recess 125.

[0032] Based on the above structure, when the two partitions 1 are installed together, the protruding rings 124 of the two partitions 1 will abut against each other, creating a space between the two partitions 1 and forming a stable fluid flow channel. Simultaneously, the abutting manner of the protruding rings 124 enhances the overall strength of the baffle structure 12, preventing deformation under high pressure. Furthermore, the protruding rings 124 can provide corresponding support to the first protrusion 123 on the other side of the partition 1, ensuring the stability of the first protrusion 123.

[0033] In this embodiment, the notch 126 can discharge the air in the first recess during the operation of the heat exchange core, thus preventing the air in the first recess from being unable to be discharged when the two protruding rings 124 abut against each other during operation, which would lead to deformation and damage of the partition 1 later.

[0034] It should be noted that in this embodiment, the partition 1 is integrally stamped from a metal sheet, and the baffle structure 12 is formed by stamping the partition 1. That is, a first protrusion 123 is formed on the hot side 112, and a first recess is formed on the cold side 111. With this double-sided support structure, welding is not required, which can ensure the reliability of the connection between the support platforms 122, improve service life and reliability, and reduce the processing difficulty.

[0035] Furthermore, the height of the ridge 121 relative to the substrate 11 is h1, and the height of the support platform 122 relative to the substrate 11 is h2, where h1 < h2, and h1:h2 = (0.1-0.9):1.

[0036] In this embodiment, the height of the substrate portion 11 is set to 0, the height of the ridge 121 relative to the substrate portion 11 is h1, and the height of the support platform 122 relative to the substrate portion 11 is h2. Then, h1 < h2, and the height of the cold flow through-hole 23 is 2*(h2-h1), where (h2-h1) is half the height of the cold flow through-hole 23. It can be understood that if h1 is too large, the gap of the cold flow through-hole 23 is too small, and the pressure loss of the cold flow channel 21 is too large. If h1 is too small, the gap of the cold flow through-hole 23 is large, and the filling particles filled in the evaporation section 211 need to be replaced with larger particle size particles. Otherwise, the filling particles will leak into the superheated section 212. If the filling particles are too large, they are not easy to fill, and the thickness of the cold flow channel 21 will be too large, thus increasing the volume of the entire heat exchange core. In addition, if the particle size of the filling particles is too large, the effect of suppressing vaporization fluctuations will decrease. Therefore, in this embodiment, h1:h2 = (0.1-0.9):1, which ensures that the gap of the cold flow through-hole 23 is appropriate and that the filling particles can suppress vaporization fluctuations. Preferably, h1:h2 = (0.5-0.9):1.

[0037] In this embodiment, h1 ranges from 0.1 to 0.5 mm, and h2 ranges from 0.3 to 0.9 mm.

[0038] Furthermore, the particle size of the filler particles is larger than the diameter of the cold flow through-hole 23, and D > 2*(h2-h1), where D is the particle size of the filler particles.

[0039] In this embodiment, the selected particle size facilitates filling the evaporation section 211 and effectively suppresses pressure fluctuations during vaporization. If the particle size is too small, the cold flow through-holes 23 need to be very small, making the cold flow through-holes 23 difficult to manufacture and resulting in excessive cold flow pressure loss. If the particle size is too large, it is difficult to fill the particles, leading to excessive thickness of the cold flow channel 21 and thus increasing the overall volume of the heat exchange core. Furthermore, a large particle size reduces the effectiveness of suppressing vaporization fluctuations, failing to meet the requirements. Preferably, the particle size range of the filler particles is 0.5-2 mm.

[0040] Furthermore, the filler particles are one or more of ceramic particles or metal particles. Ceramic particles are preferred, as they are characterized by high temperature resistance, low cost, resistance to rust, and light weight. Specifically, the ceramic particles can be porous ceramics, which can further suppress pressure fluctuations generated during the boiling of liquid water.

[0041] It should be noted that the metal particles in this embodiment include at least one of iron particles, nickel particles, copper particles, aluminum particles, aluminum alloy particles, iron-nickel alloy particles, nickel-cobalt alloy particles, titanium particles, titanium alloy particles, silver particles, and steel particles; the ceramic particles include at least one of alumina ceramic particles, zirconia ceramic particles, and silicon carbide ceramic particles. In practical applications, different materials of filler particles can be used as needed, or different materials of filler particles can be mixed and used; no particular limitation is made here.

[0042] like Figures 4 to 7 As shown, the partition 1 also includes protruding strips 13, bosses 14, second recesses 15, and grooves 16. The protruding strips 13 protrude from the hot side surface 112, so that the second recesses 15 are formed on the cold side surface 111. Multiple protruding strips 13 are spaced apart along a third direction. The bosses 14 protrude from the protruding strips 13 and / or the hot side surface 112, so that the grooves 16 are formed on the second recesses 15 and / or the cold side surface 111. The height of the bosses 14 is greater than the height of the protruding strips 13. Therefore, when two adjacent partitions 1 are installed together, the bosses 14 of the two adjacent partitions 1 forming the hot flow channel 22 abut against each other to form a hot flow gap, allowing high-temperature exhaust gas to flow through the hot flow gap. The first direction, the second direction, and the third direction are perpendicular to each other.

[0043] In this embodiment, the partition 1 has multiple raised strips 13 on the hot side 112 to increase the heat exchange area and thus improve the heat exchange efficiency. Meanwhile, since both the hot runner 22 and the cold runner 21 are cavities, their resistance to deformation is low. Especially during heat exchange, the liquid water in the cold runner 21 boils and generates bubbles, which will squeeze the partition 1 from the cold side 111, causing the partition 1 to deform towards the hot runner 22. In this embodiment, protrusions 14 are provided between the two partitions 1 on both sides of the hot runner 22 to abut against each other, providing support for the hot runner 22 and effectively preventing deformation of the partition 1.

[0044] Furthermore, since the height of the boss 14 is higher than that of the protrusion 13, a gap is formed between the bosses 14, and the heat flow (i.e., high-temperature exhaust gas) can flow through the gap, which not only increases the heat exchange area, but also reduces the pressure loss of the medium in the hot flow channel 22.

[0045] In one alternative embodiment, the raised strip 13 may be a wavy pattern, and the raised strip 13 extends along the second direction. In other embodiments, the raised strip 13 may be a herringbone pattern, a mesh pattern, etc., and is not limited thereto.

[0046] In the first direction, the height of the protrusion 13 relative to the substrate portion 11 is h3, and the height of the first boss 14 relative to the substrate portion 11 is h4, where h3:h4 = (0.2-0.9):1. If h3:h4 is less than 0.2:1, it indicates that the height of the protrusion 13 is too small, the surface area of ​​the partition 1 is too small, and the heat exchange effect is affected. If h3:h4 is greater than 0.9:1, it indicates that the height of the protrusion 13 is too large, the heat flow gap formed between the first bosses 14 of adjacent partitions is too small, and the pressure loss is too large.

[0047] Preferably, in an optional embodiment, h3:h4 = (0.5-0.8):1. The inventors have found that h3:h4 within this range can better balance heat exchange performance and pressure loss, while the volume of the heat exchange core is also within a reasonable range.

[0048] Understandably, since the baffle 1 is integrally stamped, the cold side surface 111 of the baffle 1 forms a groove corresponding to the raised strip 13 and a recess corresponding to the boss 14. This can effectively reduce the pressure loss of the cold flow channel 21 while increasing the heat exchange area, and at the same time ensure that the heat exchange core is smaller. Since the baffle 1 is directly stamped from a single metal plate, compared with the traditional plate-fin steam generator, the baffle 1 does not require any welding inside. This not only reduces the processing difficulty but also prevents the boss 14, raised strip 13, and other structures from falling off after a long period of use, thus improving their service life.

[0049] Furthermore, each partition 1 has the same structure to save production costs. In any two adjacent partitions 1, one partition 1 is configured to be rotated 180° relative to the other partition 1 along the second direction. Since the structure of each partition 1 in this embodiment is the same, only the orientation is different when stacked, during installation, the hot side 112 is aligned with the hot side 112, and the cold side 111 is aligned with the cold side 111. Specifically, rotating the partition 1 180° along the second direction can obtain the placement direction of adjacent partitions 1. For example, rotating one partition 1 180° around the baffle structure 12 as the rotation axis can obtain the orientation direction of another partition 1.

[0050] The partition 1 further includes a second protrusion 17, a first clearance portion, a third protrusion 18, and a second clearance portion; the second protrusion 17 protrudes from the cold side 111, and the cold side 111 has a first clearance portion corresponding to the second protrusion 17, and the second protrusion 17 is configured to abut against the first clearance portion of another partition 1 opposite to it.

[0051] In this embodiment, the second protrusion 17 serves to support the cold flow channel 21. In this embodiment, each partition 1 has three second protrusions 17. After assembly, since adjacent partitions 1 are placed by rotating 180° along the second direction, in the same plate alignment, the second protrusion 17 of one partition 1 is in the evaporation section 211, while the second protrusion 17 of the other partition 1 is in the superheating section 212. In this way, the partitions 1 in the same plate alignment can be supported on both the cold side 111 and the superheating section 212. It should be noted that in other embodiments, other distribution methods can also be used, as long as sufficient support is provided for the upper and lower parts of the cold flow channel 21.

[0052] Since the two adjacent partitions 1 are to be stacked in a position that is rotated 180° along the second direction, the second protrusion 17 also serves as a foolproof feature when assembling a pair of partitions 21. If the partitions 1 are not placed correctly, the second protrusions 17 of the two partitions 1 will align and interfere with each other, making installation impossible. Only when the partitions 1 are placed correctly can the two partitions 1 be installed properly. It should be noted that the first clearance portion in this embodiment can be an area formed by the two protruding strips 13, and no other structure is provided in this area to facilitate the installation of the second protrusion 17.

[0053] Furthermore, a third protrusion 18 protrudes from the hot side surface 112, and a second clearance portion is formed on the hot side surface 112 corresponding to the third protrusion 18. The third protrusion 18 is configured to match the second clearance portion of another partition 1 disposed opposite to it.

[0054] Since the two adjacent partitions 1 are to be stacked in a position that is rotated 180° along the second direction, if the partitions 1 are not placed correctly during the stacking process and the hot runner 22 is assembled, the third protrusions 18 of the two partitions 1 will align and interfere with each other, making installation impossible. Only when the partitions 1 are placed correctly can the two partitions 1 be installed properly. Understandably, in this embodiment, the third protrusion 18 can only serve as a foolproof function, and a gap can be formed between the third protrusion 18 and the second clearance portion.

[0055] Furthermore, in some embodiments, the third protrusion 18 can serve as a support, such that in the two partitions 1 that form the hot flow channel 22, the third protrusion 18 of one partition 1 is in the lower half, while the third protrusion 18 of the other partition 1 is in the upper half, so that the adjacent partitions 1 form support on both the upper and lower parts of the hot side surface 112. That is, the third protrusion 18 and the second clearance part abut against each other at this time.

[0056] It should be noted that the second clearance portion in this embodiment can be an area enclosed by two protruding strips 13, and no other structure is provided in this area to facilitate the installation of the third protruding portion 18.

[0057] like Figure 1 , Figures 10 to 12 As shown, the cold flow inlet 213 of the cold flow channel 21 is located in the evaporation section 211, and the cold flow outlet 214 of the cold flow channel 21 is located in the superheated section 212, so that the fluid in the cold flow channel 21 flows along the evaporation section 211 toward the superheated section 212. That is, it ensures that the cold flow enters from the evaporation section 211, is heated up, and then flows out from the superheated section 212.

[0058] Furthermore, the hot flow inlet 221 of the hot flow channel 22 is located on the upward-facing side of the heat exchange core along the third direction, and the hot flow outlet 222 of the hot flow channel 22 is located on the downward-facing side of the heat exchange core along the third direction. The cold flow inlet 213 of the cold flow channel 21 is located in the evaporation section 211 and is located on one or both sides of the heat exchange core along the second direction. The cold flow outlet 214 of the cold flow channel 21 is located in the superheated section 212 and is located on one or both sides of the heat exchange core along the second direction. Through the above arrangement, the hot flow inlet 221 is at the top and the hot flow outlet 222 is at the bottom, forming a top-in, bottom-out heat flow pattern. The cold flow outlet 214 and the cold flow inlet 213 are located on the surface distributed along the second direction, and the cold flow inlet is located near the hot flow outlet 222, and the cold flow outlet 214 is located near the hot flow inlet 221, so that the flow directions of the cold and hot flows are basically opposite, close to countercurrent heat exchange, resulting in higher heat exchange efficiency.

[0059] In other embodiments, the heat inlet 221 and the heat outlet 222 may also be located on one or both sides of the heat exchange core along the second direction, with the heat inlet 221 near the superheated section 212 and the heat outlet 222 near the evaporation section 211. The cold inlet 213 of the cold flow channel 21 is located on the downward side of the heat exchange core along the third direction, and the cold outlet 214 of the cold flow channel 21 is located on the upward side of the heat exchange core along the third direction.

[0060] In summary, other structural configurations can also be adopted, as long as the cold flow inlet 213 of the cold flow channel 21 is located in the evaporation section 211, the cold flow outlet 214 is located in the superheating section 212, and the flow directions of the cold flow and the hot flow are generally opposite in the heat exchange core, which is countercurrent heat exchange.

[0061] Specifically, the cold flow inlet 213 and the cold flow outlet 214 can be configured in the following ways: (1) The cold flow inlet 213 is located on one side of the heat exchange core along the second direction and is adjacent to the hot flow outlet 222; the cold flow outlet 214 is located on the other side of the heat exchange core along the second direction and is adjacent to the hot flow inlet 221.

[0062] (2) The cold flow inlet 213 is located on both sides of the heat exchange core along the second direction and near the hot flow outlet 222; the cold flow outlet 214 is located on one side of the heat exchange core along the second direction and near the hot flow inlet 221.

[0063] (3) The cold flow inlet 213 is located on one side of the heat exchange core along the second direction and is adjacent to the hot flow outlet 222; the cold flow outlet 214 is located on both sides of the heat exchange core along the second direction and is adjacent to the hot flow inlet 221.

[0064] (4) The cold flow inlet 213 is located on both sides of the heat exchange core along the second direction and near the hot flow outlet 222; the cold flow outlet 214 is located on both sides of the heat exchange core along the second direction and near the hot flow inlet 221.

[0065] Furthermore, it also includes a sealing key strip 3, which surrounds the periphery of the partition 1 and has an opening between two adjacent partitions 1. The opening in the hot runner 22 is configured as a hot flow inlet 221 and a hot flow outlet 222, and the hot flow inlet 221 and the hot flow outlet 222 are connected through the hot runner 22. The opening in the cold runner 21 is configured as a cold flow inlet 213 and a cold flow outlet 214, and the cold flow inlet 213 and the cold flow outlet 214 are connected through the cold runner 21.

[0066] In this embodiment, a sealing key strip 3 is provided to connect the two partitions 1 while simultaneously sealing the area outside the opening. This ensures that the fluid in the cold flow channel 21 or the hot flow channel 22 can only flow in or out through the corresponding opening, preventing leakage. Understandably, the sealing key strip 3 in this embodiment does not completely cover the perimeter of the partition 1; the uncovered portion forms the fluid inlet and outlet. For the hot flow channel 22, these are the hot flow inlet 221 and the hot flow outlet 222, and for the cold flow channel 21, they are the cold flow inlet 213 and the cold flow outlet 214.

[0067] The present invention also provides a steam generator, comprising the heat exchange core as described above.

[0068] In summary, the present invention provides a heat exchange core and a steam generator. The cold flow channel 21 is divided into a connected evaporation section 211 and a superheating section 212 by a baffle structure 12. During operation, liquid water is introduced into the cold flow channel 21 and high-temperature exhaust gas is introduced into the hot flow channel 22. After the liquid water enters the heat exchange core, it boils and vaporizes into steam in the evaporation section 211. Since the evaporation section 211 is filled with packing particles, the pressure fluctuation caused by vaporization can be effectively suppressed, ensuring that the pressure of the steam coming out of the cold flow channel 21 is more stable. The steam passes through the baffle structure 12 to reach the superheating section 212 and continues to heat up to the required temperature before finally leaving the heat exchange core.

[0069] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and substitutions can be made without departing from the technical principles of the present invention, and these improvements and substitutions should also be considered within the scope of protection of the present invention.

Claims

1. A heat exchange core, characterized by, It includes multiple baffles spaced apart along a first direction, with adjacent baffles forming a flow channel, and the multiple flow channels are sequentially assigned as alternating hot and cold flow channels; The partition includes a base plate portion and a baffle structure. The base plate portion has a cold side surface facing the cold flow channel. The baffle structure protrudes from the cold side surface and extends along a second direction. The baffle structures of two adjacent partitions surrounding the cold flow channel abut each other to divide the corresponding cold flow channel into an evaporation section and a superheating section that are distributed and interconnected along a third direction. The evaporation section is filled with filler particles. The first direction, the second direction, and the third direction are perpendicular to each other.

2. The heat exchange core according to claim 1, characterized in that, The baffle structure includes a ridge and a support platform. The ridge protrudes from the cold side and the support platform protrudes from the ridge toward the cold flow channel. A plurality of support platforms are spaced apart along the extension direction of the ridge. The support platforms of two adjacent partitions surrounding the cold flow channel abut each other, so that a cold flow through hole connecting the evaporation section and the superheating section is formed between the ridges of the two partitions.

3. The heat exchange core according to claim 2, characterized in that, The partition is a one-piece structure; The substrate portion has a hot side facing the hot flow channel, and the baffle structure further includes a first protrusion that protrudes from the hot side and abuts against the first protrusions of two adjacent baffles surrounding the hot flow channel.

4. The heat exchange core according to claim 3, characterized in that, The baffle structure also includes a protruding ring formed on the cold side and a first recess. The height of the protruding ring is the same as the height of the support platform. The protruding rings of two adjacent partitions that form the cold flow channel abut each other. The first recess is located in the middle of the protruding ring, and the periphery of the protruding ring is recessed to form a notch that communicates with the first recess.

5. The heat exchange core according to claim 2, characterized in that, The height of the ridge relative to the substrate is h1, and the height of the support platform relative to the substrate is h2, where h1 < h2, and h1:h2 = (0.1-0.9):

1.

6. The heat exchange core according to claim 5, characterized in that, The particle size of the filler particles is larger than the diameter of the cold flow through-hole, and D > 2*(h2-h1), where D is the particle size of the filler particles.

7. The heat exchange core according to claim 1 or 5, characterized in that, The filler particles are one or more of ceramic particles or metal particles.

8. The heat exchange core according to claim 3, characterized in that, The partition also includes a raised strip and a boss. The raised strip protrudes from the hot side surface, and the boss protrudes from the raised strip and / or the hot side surface. The height of the boss is greater than the height of the raised strip, and the bosses of two adjacent partitions forming the hot flow channel abut against each other.

9. The heat exchange core according to claim 1, characterized in that, The cold flow inlet of the cold flow channel is located in the evaporation section, and the cold flow outlet of the cold flow channel is located in the superheated section, so that the fluid in the cold flow channel flows along the evaporation section toward the superheated section, and the fluid flow direction of the cold flow channel is opposite to the fluid flow direction of the hot flow channel.

10. A steam generator, characterized in that, Includes the heat exchange core as described in any one of claims 1-9.

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