Heat exchanger

Abstract

The utility model provides a heat exchanger and relates to the technical field of heat exchangers. The heat exchanger comprises fin units, and turbulent flow gaps are formed between fins of the fin units. The corrugated plate heat exchange assembly is connected with the fin unit; a turbulent flow channel is formed between at least one side of the corrugated plate heat exchange assembly and the fin unit. According to the technical scheme, the turbulent flow gaps are formed between the fins, the turbulent flow channels in irregular shapes are formed between the corrugated plate heat exchange assembly and the fin units, and the turbulent flow gaps and the turbulent flow channels are arranged in a combined mode, so that the flowing direction of fluid in the turbulent flow channels is continuously changed; therefore, the fluid can reach a turbulent flow state under the condition of low flow speed, the turbulent flow effect of the fluid can be effectively improved, and the heat exchange efficiency is improved.

Description

Technical Field

[0001] This utility model relates to the field of heat exchanger technology, and more specifically, to a heat exchanger. Background Technology

[0002] In existing heat exchangers, only turbulence channels are provided on the fins. However, the medium passing through the turbulence channel must first transfer heat to the fins, then to the heat exchanger through the heat conduction of the metal fins, and finally to the fluid in the channel through the metal heat exchanger. This greatly reduces the efficiency of heat transfer, making the turbulence method on the fins ineffective.

[0003] There is currently no effective solution to the above problems. Utility Model Content

[0004] The main objective of this invention is to provide a heat exchanger that solves the problem of poor heat transfer performance in existing heat exchangers.

[0005] To achieve the above objectives, according to one aspect of the present invention, a heat exchanger is provided, comprising: a finned unit, wherein turbulence gaps are formed between the fins of the finned unit; and a corrugated plate heat exchange assembly connected to the finned unit; wherein the corrugated plate heat exchange assembly has a plurality of protruding sections and recessed sections, at least one protruding section of the corrugated plate heat exchange assembly contacts the finned unit, and at least one recessed section of the corrugated plate heat exchange assembly forms turbulence channels with the finned unit.

[0006] Furthermore, there are multiple fin units, which are arranged at intervals along the thickness direction of the corrugated plate heat exchange assembly; the corrugated plate heat exchange assembly is disposed between two adjacent fin units; wherein, a first turbulence channel is formed between the first side of the corrugated plate heat exchange assembly and one of the fin units in the adjacent arrangement, and a second turbulence channel is formed between the second side of the corrugated plate heat exchange assembly and another fin unit.

[0007] Furthermore, there are multiple first and second turbulence channels, and the multiple first and multiple second turbulence channels are arranged at intervals along the length direction of the corrugated plate heat exchange assembly, wherein the multiple first turbulence channels and the multiple second turbulence channels are arranged in a one-to-one correspondence.

[0008] Furthermore, along the thickness direction of the corrugated plate heat exchange assembly, the geometric center line of the cross-section of the first turbulence channel is set at a distance from the geometric center line of the cross-section of the corresponding second turbulence channel; and / or, along the thickness direction of the corrugated plate heat exchange assembly, the geometric center line of the cross-section of the first turbulence channel is set collinearly with the geometric center line of the cross-section of the corresponding second turbulence channel.

[0009] Furthermore, the corrugated plate heat exchange assembly also has flow channels, which are staggered with the first and second turbulence channels.

[0010] Furthermore, at least one of the first turbulence channel, the second turbulence channel, and the flow channel includes multiple component sections, which extend along the width direction of the corrugated plate heat exchange assembly, and the geometric center lines of each component section are arranged at an angle.

[0011] Further, the corrugated plate heat exchange assembly includes: a first corrugated plate, on which multiple first peaks and multiple first troughs are formed, the multiple first peaks and multiple first troughs being alternately arranged along the length direction of the first corrugated plate, and the tops of two adjacent first peaks contacting adjacent fin units, so that a first turbulence channel is formed between the first corrugated plate and the fin unit located between adjacent first peaks. A second corrugated plate, on which multiple second peaks and multiple second troughs are formed, the multiple second peaks and multiple second troughs being alternately arranged along the length direction of the second corrugated plate, and the tops of two adjacent second peaks contacting another adjacent fin unit, so that a second turbulence channel is formed between the second corrugated plate and the fin unit located between adjacent second peaks.

[0012] Furthermore, the first corrugated plate is arranged in contact with the adjacent first trough and the second corrugated plate is arranged in contact with the adjacent second trough, and a flow channel is formed between the first corrugated plate and the corresponding second trough.

[0013] Furthermore, the corrugated plate heat exchange assembly includes a stress relief structure, which is protrudingly disposed on the surface of at least one of the first and second troughs, and the height of the stress relief structure is lower than the depth of the first or second trough.

[0014] Furthermore, at least one of the first corrugated plate and the second corrugated plate has a plurality of flow guiding channels at its inlet end. The plurality of flow guiding channels are used to communicate with the flow channel. The plurality of flow guiding channels are evenly distributed along the width direction of the first corrugated plate or the second corrugated plate, or the plurality of flow guiding channels are arranged to be interconnected with each other.

[0015] By applying the technical solution of this utility model, turbulence gaps can be formed between the fins themselves. The corrugated plate heat exchange assembly includes multiple raised sections and recessed sections. The raised sections contact the fin units, so that irregularly shaped turbulence channels are formed between the recessed sections and the fin units. By combining the turbulence gaps and turbulence channels, the flow direction of the fluid inside the turbulence gaps and turbulence channels is constantly changed, so that the fluid can reach a turbulent state even at low flow rates, which can effectively increase the turbulence effect of the fluid and improve the heat exchange efficiency. Attached Figure Description

[0016] The accompanying drawings, which form part of this application, are used to provide a further understanding of the present invention. The illustrative embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an undue limitation of the present invention. In the drawings:

[0017] Figure 1 A schematic diagram of the structure of a first embodiment of a heat exchanger according to the present invention is shown;

[0018] Figure 2 It shows Figure 1 Enlarged view of point A in the middle;

[0019] Figure 3 A schematic diagram of the structure of a second embodiment of the heat exchanger according to the present invention is shown;

[0020] Figure 4 A schematic diagram of the structure of a third embodiment of the heat exchanger according to the present invention is shown;

[0021] Figure 5 A schematic diagram of the structure of a fourth embodiment of the heat exchanger according to the present invention is shown;

[0022] Figure 6 A schematic diagram of the structure of a first embodiment of the flow guiding channel according to the present invention is shown;

[0023] Figure 7 A schematic diagram of a second embodiment of the flow guiding channel according to the present invention is shown.

[0024] The above figures include the following reference numerals:

[0025] 10. Finned unit;

[0026] 20. Corrugated plate heat exchange assembly; 200. Stress relief structure; 201. First corrugated plate; 2010. First peak; 2011. First trough; 202. Second corrugated plate; 2020. Second peak; 2021. Second trough; 21. First turbulence channel; 22. Second turbulence channel; 23. Flow channel;

[0027] 30. Flow channel. Detailed Implementation

[0028] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0029] Combination Figures 1 to 7 As shown, according to a specific embodiment of this application, a heat exchanger is provided. Specifically, as... Figure 1 , Figure 2As shown, the heat exchanger includes finned units 10 and corrugated plate heat exchange assembly 20. Turbulent gaps are formed between the fins of the finned units 10. The corrugated plate heat exchange assembly 20 is connected to the finned units 10. The corrugated plate heat exchange assembly 20 has multiple protruding sections and recessed sections. At least one protruding section of the corrugated plate heat exchange assembly 20 contacts the finned units 10, and at least one recessed section of the corrugated plate heat exchange assembly 20 forms a turbulent channel with the finned units 10.

[0030] Applying the technical solution of this embodiment, the fins themselves form turbulence gaps. The corrugated plate heat exchange assembly 20 includes multiple raised sections and recessed sections. The raised sections contact the fin unit 10, so that an irregularly shaped turbulence channel is formed between the recessed section and the fin unit 10. By combining the turbulence gaps and turbulence channels, the flow direction of the fluid inside the turbulence gaps and turbulence channels is constantly changed, so that the fluid can reach a turbulent state even at low flow rates, which can effectively increase the turbulence effect of the fluid and improve the heat exchange efficiency.

[0031] It should be noted that, as Figure 1 As shown, the finned unit 10 adopts a dense plate-like or folded structure, which greatly increases the surface area of ​​the heat exchanger. The structure in which the finned unit 10 and the corrugated plate heat exchange assembly 20 are arranged adjacent to each other allows the turbulence gap and turbulence channel to be used together, which improves the heat transfer performance. The corrugated structure can also provide additional support and improve the stability of the heat exchanger assembly. In addition, the combination of the corrugated plate and the finned unit 10 can also reduce the amount of metal used and reduce costs.

[0032] Specifically, there are multiple finned units 10, which are spaced apart along the thickness direction of the corrugated plate heat exchange assembly 20; the corrugated plate heat exchange assembly 20 is disposed between two adjacent finned units 10; wherein, a first turbulence channel 21 is formed between the first side of the corrugated plate heat exchange assembly 20 and one of the adjacent finned units 10, and a second turbulence channel 22 is formed between the second side of the corrugated plate heat exchange assembly 20 and another finned unit 10. In this embodiment, as... Figures 1 to 3 As shown, a corrugated plate heat exchange assembly 20 is provided between two adjacent finned units 10, and a finned unit 10 is provided between two adjacent corrugated plate heat exchange assemblies 20, which can significantly improve the overall performance and heat exchange efficiency of the heat exchanger.

[0033] Specifically, such as Figure 1 , Figure 2As shown, there are multiple first turbulence channels 21 and multiple second turbulence channels 22. These multiple first turbulence channels 21 and multiple second turbulence channels 22 are spaced apart along the length of the corrugated plate heat exchange assembly 20, with each of the multiple first turbulence channels 21 and multiple second turbulence channels 22 corresponding to one another. When the multiple first turbulence channels 21 and multiple second turbulence channels 22 are connected along the length of the corrugated plate heat exchange assembly 20, the fluid's flow path is increased due to the corrugated shape of the channels, allowing the fluid to reach a turbulent state even at low speeds, thus improving the convective heat transfer coefficient. The one-to-one correspondence between the multiple first turbulence channels 21 and multiple second turbulence channels 22 allows for a more uniform turbulence distribution within the heat exchanger, preventing localized overheating or undercooling and improving overall heat exchange performance.

[0034] In one embodiment of this application, multiple first turbulence channels 21 are interconnected to form an S-shaped path for fluid flow, and multiple second turbulence channels 22 are interconnected to form an S-shaped path for fluid flow. This changes the straight-plate flow channel in the prior art, increases the turbulence of the fluid, improves the heat transfer coefficient, and the S-shaped channel path can distribute the fluid more evenly, avoiding the problems of local high temperature and low local heat transfer efficiency. At the same time, the S-shaped structure can form multiple support points on the corrugated plate heat exchange assembly 20, enhance the rigidity of the corrugated plate heat exchange assembly 20, and improve the stability and pressure resistance of the corrugated plate heat exchange assembly 20.

[0035] Optionally, the first turbulence channel 21 and the second turbulence channel 22 may also be configured as V-shaped or other complex structural shapes to change the flow path of the fluid.

[0036] It should be noted that the length direction of the corrugated plate heat exchange assembly 20 is the direction in which the fluid medium flows along the first turbulence channel 21, and also the direction in which the fluid medium flows along the second turbulence channel 22. The first turbulence channel 21 and the second turbulence channel 22 are connected in the direction of fluid medium flow.

[0037] In one embodiment of this application, such as Figure 4 As shown, along the thickness direction of the corrugated plate heat exchange assembly 20, the geometric center line of the cross-section of the first turbulence channel 21 is set at a distance from the geometric center line of the cross-section of the corresponding second turbulence channel 22. When adjacent corrugated plates are stacked in a staggered manner, the support points of the corrugated plates are in contact with each other, causing the fluid medium to flow between the first turbulence channel 21 and the second turbulence channel 22. This generates a more complex fluid turbulence effect, and the fluid experiences multiple changes in velocity and direction as it flows through the two turbulence channels, generating additional eddies. This further enhances the turbulence of the fluid, reduces the thermal resistance on the fluid side, and improves heat exchange efficiency and performance.

[0038] In another embodiment of this application, Figure 5 As shown, along the thickness direction of the corrugated plate heat exchange assembly 20, the geometric center line of the cross-section of the first turbulence channel 21 is collinear with the geometric center line of the cross-section of the corresponding second turbulence channel 22. This arrangement of adjacent corrugated plates in parallel ensures that the fluid medium experiences continuous and uniform turbulence as it passes through the two adjacent turbulence channels. This maintains the uniformity of fluid flow, avoids excessive or insufficient local turbulence, reduces fluid deviation, and increases the contact area and time between the fluid and the corrugated plate, thereby improving heat exchange efficiency. Furthermore, the collinear arrangement of the geometric center lines of the first and second turbulence channels 21 and 22 makes the structure of the heat exchange assembly more compact, facilitating the achievement of a larger heat exchange area within a limited space.

[0039] It should be noted that the geometric center line of the cross-section of the first turbulence channel 21 and the geometric center line of the corresponding second turbulence channel 22 can be set according to the actual working conditions in order to maximize the performance of the heat exchanger. For example, the geometric center line of the cross-section of the first turbulence channel 21 and the geometric center line of the cross-section of the corresponding second turbulence channel 22 can be set at a distance. However, the first turbulence channel 21 and the second turbulence channel 22 do not adopt a completely symmetrical structure. That is, the first turbulence channel 21 and the second turbulence channel 22 are staggered, which is still beneficial to the turbulence of the fluid and improve the heat exchange effect.

[0040] Furthermore, such as Figure 1 , Figure 2 As shown, the corrugated plate heat exchange assembly 20 also forms a flow channel 23, which is staggered from the first turbulence channel 21 and the second turbulence channel 22. In this embodiment, air flows in the first turbulence channel 21 and the second turbulence channel 22, while fluid flows in the flow channel 23. During the heat exchange process of the corrugated plate heat exchange assembly 20, the heat of the air in the first turbulence channel 21 and the second turbulence channel 22 is exchanged with the heat of the fluid in the flow channel 23 through the irregular flow between the air and the fluid, thus transferring heat. The arrangement of the flow channel 23 can make the fluid distribution more uniform, further increase the turbulence state of the fluid, and improve the heat exchange efficiency.

[0041] Specifically, at least one of the first turbulence channel 21, the second turbulence channel 22, and the flow channel 23 includes multiple component sections. These component sections extend along the width direction of the corrugated plate heat exchange assembly 20, and the geometric center lines of each component section are arranged at an angle. This arrangement allows the fluid in each component section to flow fully, further increasing the turbulence of the fluid and making the contact between the turbulence channel and the fluid in the flow channel 23 more thorough and uniform, thereby improving the heat exchange efficiency.

[0042] Optionally, the included angle of the geometric center lines of each component segment is V-shaped. The included angles of the geometric center lines of the component segments on the first turbulence channel 21 and the second turbulence channel 22 are opposite, that is, after the component segment on the first turbulence channel 21 is rotated 180°, the included angle of the geometric center line of the component segment on the second turbulence channel 22 is the same. At the same time, the contact points between the component segments on the first turbulence channel 21 and the component segments on the second turbulence channel 22 can be set as groove structures and protrusion structures. The contact points between the groove structure and the protrusion structure are filled with brazing material and joined by brazing. This ensures that the two component segments maintain a certain distance from each other under the formation of the flow channel 23, thereby making the fluid flow in the flow channel 23 more stable.

[0043] Furthermore, such as Figures 1 to 4 As shown, the corrugated plate heat exchange assembly 20 includes a first corrugated plate 201 and a second corrugated plate 202. The first corrugated plate 201 has multiple first peaks 2010 and multiple first troughs 2011 formed on it. The multiple first peaks 2010 and multiple first troughs 2011 are alternately arranged along the length of the first corrugated plate 201, and the tops of two adjacent first peaks 2010 contact adjacent fin units 10, so that the first corrugated plate 201 located between adjacent first peaks 2010 contacts the fin unit. A first turbulence channel 21 is formed between the 10 units; a plurality of second wave peaks 2020 and a plurality of second wave troughs 2021 are formed on the second corrugated plate 202, the plurality of second wave peaks 2020 and the plurality of second wave troughs 2021 are alternately arranged along the length direction of the second corrugated plate 202, and the top of two adjacent second wave peaks 2020 contacts another adjacent fin unit 10, so that a second turbulence channel 22 is formed between the second corrugated plate 202 and the fin unit 10 located between adjacent second wave peaks 2020.

[0044] In this embodiment, the first corrugated plate 201 is configured to distinguish between the first wave crests 2010 and the first wave troughs 2011. The structure of the first corrugated plate 201 and the contact method between the first corrugated plate 201 and its adjacent fin unit 10 are configured such that multiple first wave crests 2010 are in contact with the fin unit 10, and multiple first wave troughs 2011 are far away from the fin unit 10. Furthermore, the structure of the first turbulence channel 21 is configured such that the first turbulence channel 21 is set as an S-shaped corrugated turbulence channel, which increases the turbulence effect on the fluid and improves the heat exchange efficiency. The second corrugated plate 202 distinguishes the second wave peaks 2020 and the second wave troughs 2021. The structure of the second corrugated plate 202 and the contact method between the second corrugated plate 202 and its adjacent fin unit 10 are configured such that multiple second wave peaks 2020 are in contact with the fin unit 10, and multiple second wave troughs 2021 are far away from the fin unit 10. The structure of the second turbulence channel 22 is further configured such that the second turbulence channel 22 is set as an S-shaped corrugated turbulence channel, which increases the turbulence effect on the fluid and improves the heat exchange efficiency.

[0045] In this embodiment, as Figure 4 As shown, a first corrugated plate 201 and a second corrugated plate 202 are provided between two adjacent fin units 10. The first wave crest 2010 of the first corrugated plate 201 contacts one of the fin units 10, and the second wave crest 2020 of the second corrugated plate 202 contacts the other fin unit 10. The first wave trough 2011 of the first corrugated plate 201 contacts the second wave trough 2021 of the second corrugated plate 202. The first wave trough 2011 and the second wave trough 2021 are in contact and are staggered along the width direction of the corrugated plate heat exchange assembly 20. This achieves a distance between the geometric center line of the cross section of the first turbulence channel 21 and the geometric center line of the cross section of the corresponding second turbulence channel 22, which can improve the heat exchange efficiency and the performance of the heat exchanger.

[0046] Furthermore, such as Figure 1 , Figure 2As shown, the first corrugated plate 201 has an adjacent first trough 2011 in contact with the second corrugated plate 202 has an adjacent second trough 2021 in contact with it, and the first corrugated plate 201 and the second corrugated plate 202 between the adjacent first trough 2011 and the corresponding second trough 2021 form a flow channel 23. In this embodiment, the structure of the flow channel 23 is configured such that the flow channel 23 is formed by the first corrugated plate 201 and the second corrugated plate 202 between adjacent first troughs 2011 and corresponding second troughs 2021. The flow channel 23 is located between the first turbulence channel 21 and the second turbulence channel 22, making the flow path of the fluid in the turbulence channel and the flow channel 23 more complex, which can further improve the turbulence of the fluid and improve the heat exchange efficiency. Moreover, the formation structure of the flow channel 23 requires that adjacent first troughs 2011 and second troughs 2021 be connected. Combined with the structure of the first corrugated plate 201 and the second corrugated plate 202, the structure of the heat exchanger is more stable and the maintenance cost is reduced.

[0047] Furthermore, the corrugated plate heat exchange assembly 20 includes a stress relief structure 200, which protrudes from the surface of at least one of the first trough 2011 and the second trough 2021. The height of the stress relief structure 200 is less than the depth of the first trough 2011 or the second trough 2021. The stress relief structure 200 is disposed on the surface of one of the contacting surfaces of the first trough 2011 and the second trough 2021. The stress relief structure 200 can effectively alleviate stress concentration problems caused by thermal expansion and contraction, making it suitable for environments with frequent temperature changes. It reduces thermal stress damage to the heat exchanger, improves equipment stability and service life, and reduces maintenance costs.

[0048] In this embodiment, the stress relief structure 200 adopts a raised structure on one of the first trough 2011 or the second trough 2021, and a groove structure on the other. The contact point between the raised structure and the groove structure can be filled with brazing material and connected by brazing process. This arrangement allows the heat exchanger to absorb a certain amount of welding stress and is suitable for environments with severe stress corrosion.

[0049] Furthermore, such as Figure 3 , Figure 4 , Figure 6 , Figure 7As shown, at least one of the first corrugated plate 201 and the second corrugated plate 202 has a plurality of flow guiding channels 30 at its inlet end. These channels 30 communicate with the flow channel 23. The flow guiding channels 30 are uniformly distributed along the width direction of the first corrugated plate 201 or the second corrugated plate 202, or they are arranged in an alternating manner. The arrangement of the flow guiding channels 30 allows for a more uniform distribution of the fluid when it enters the finned unit 10 and the corrugated plate heat exchange assembly 20, thereby ensuring uniform flow of the fluid within the multiple corrugated plate heat exchange assemblies 20. This prevents localized overheating or undercooling within the heat exchanger and improves heat exchange efficiency.

[0050] Optionally, the flow channels 30 can be arranged in an interlaced manner or in a V-shaped expansion manner to allow the fluid to flow more evenly into the heat exchange component. When the flow channels 30 are arranged in a V-shaped manner at both ends of the fluid inlet of the heat exchanger, based on the principle that the sum of any two sides of a triangle is greater than the third side, the heat exchange area of ​​a corrugated plate of the same size is 1.05 to 1.1 times that of a flat plate (the moisture absorption varies depending on the ratio of corrugation depth and width).

[0051] Furthermore, such as Figures 1 to 3 As shown, there are multiple corrugated plate heat exchanger assemblies 20, with at least one corrugated plate heat exchanger assembly 20 disposed between adjacent fin units 10. In this way, by increasing the number of corrugated plate heat exchanger assemblies 20 inside a heat exchanger, the heat exchange efficiency and handling capacity of the heat exchanger can be further improved, making it adaptable to high flow and high heat load working environments, improving heat exchange efficiency and performance, and also improving the stability and reliability of the equipment.

[0052] This application also provides a preferred embodiment of a heat exchanger, which uses corrugated plates instead of traditional flat tubes to improve the heat transfer performance of the heat exchanger and reduce the cost.

[0053] Specifically, the heat exchanger includes two stacked corrugated plates with a pressed herringbone pattern of protrusions and grooves. After one of the corrugated plates is rotated 180° in its plane, the protrusions and grooves of the two adjacent corrugated plates will form contact points, creating a turbulence channel between the two plates. At this time, the two corrugated plates will maintain a certain distance from each other. The contact points between the protrusions and grooves of the two corrugated plates are brazed by filling brazing material, thereby forming a joint between the protrusions and grooves of the two corrugated plates.

[0054] According to the heat transfer formula for indirect heat exchangers: K = 1 / (1 / h) h +δ / λ+1 / h c );

[0055] The relationship affecting the heat transfer coefficient K of the heat exchanger can be simply summarized as f(k) = (h h ,δ,λ,h c), and 1 / h h , δ / λ, 1 / h c The three thermal resistances are key factors affecting the overall heat transfer coefficient of the heat exchanger. If we remove the influence of the heat exchanger material and thickness on the heat transfer performance of the heat exchanger and only consider the influence of the convective heat transfer coefficient on the heat transfer performance of the heat exchanger, then when the convective heat transfer coefficients of the fluids on both sides are closer, the overall heat transfer performance of the heat exchanger can be considered to be at its best. Based on this, and considering that in the gas-liquid heat exchange process, since the gas-side thermal resistance is much greater than the liquid-side thermal resistance, the gas-side thermal resistance is the component that affects the overall heat transfer performance of the heat exchanger, so the convective heat transfer coefficient on the air side should be increased.

[0056] As can be seen from the above description, the embodiments of this utility model achieve the following technical effects:

[0057] 1) The corrugated plate heat exchanger assembly 20 consists of two corrugated plates, forming an irregular channel. The fluid flows in the channel. Because the corrugated channel constantly changes the flow state of the fluid, it can achieve a turbulent state even at low flow rates, thereby greatly improving the convective heat transfer coefficient.

[0058] 2) Two adjacent corrugated plate groups are stacked upside down, forming several intersections at the crest position of each flow channel, so that the two corrugated plates have a strong mutual support effect, which can prevent the corrugations from deforming due to high pressure. The heat exchanger has a high pressure resistance.

[0059] 3) In addition to the means of enhancing heat transfer on the fins, a separate S-shaped channel is formed between the fin root and the corrugated plate flow channel. The unique structure of the corrugated plate itself is used to form turbulence for convection. The heat of the fluid is directly transferred to the corrugated plate for heat exchange, making it easier for the fluid to release energy. This improves the heat transfer coefficient of the fluid on the fin side and greatly improves the overall heat transfer performance of the heat exchanger.

[0060] 4) The corrugated plate itself has a stress relief zone, and the overall heat exchanger can absorb a certain amount of welding stress, which can be used in some situations with severe stress corrosion.

[0061] 5) The corrugated plate is equipped with multiple types of flow channels 30 at the fluid inlet, so that the fluid can be evenly distributed throughout the channel.

[0062] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0063] It should be noted that the terms "first," "second," etc., in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such terms can be used interchangeably where appropriate so that the embodiments of this application described herein can be implemented, for example, in orders other than those illustrated or described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover a non-exclusive inclusion; for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0064] Exemplary embodiments according to this application will now be described in more detail with reference to the accompanying drawings. However, these exemplary embodiments may be implemented in many different forms and should not be construed as being limited to the embodiments set forth herein. It should be understood that these embodiments are provided so that the disclosure of this application is thorough and complete, and that the concept of these exemplary embodiments is fully conveyed to those skilled in the art. In the drawings, for clarity, the thickness of layers and regions may be exaggerated, and the same reference numerals are used to denote the same devices, and therefore their description will be omitted.

[0065] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0066] In addition to the above, it should be noted that the terms "one embodiment," "another embodiment," and "embodiment" used in this specification refer to specific features, structures, or characteristics described in connection with that embodiment, which are included in at least one embodiment described in the general description of this application. The appearance of the same expression in multiple places in the specification does not necessarily refer to the same embodiment. Furthermore, when a specific feature, structure, or characteristic is described in connection with any embodiment, the intention is to suggest that implementing such a feature, structure, or characteristic in conjunction with other embodiments also falls within the scope of this utility model.

[0067] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions in other embodiments.

[0068] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A heat exchanger, characterized in that, include: A finned unit (10) has turbulence gaps formed between the fins of the finned unit (10); A corrugated plate heat exchange assembly (20) is connected to the finned unit (10); The corrugated plate heat exchange assembly (20) has multiple raised sections and recessed sections. At least one of the raised sections of the corrugated plate heat exchange assembly (20) contacts the finned unit (10), and a turbulence channel is formed between at least one of the recessed sections of the corrugated plate heat exchange assembly (20) and the finned unit (10).

2. The heat exchanger according to claim 1, characterized in that, There are multiple finned units (10), and the multiple finned units (10) are arranged at intervals along the thickness direction of the corrugated plate heat exchange assembly (20). The corrugated plate heat exchange assembly (20) is disposed between two adjacent finned units (10); A first turbulence channel (21) is formed between the first side of the corrugated plate heat exchange assembly (20) and one of the adjacent fin units (10), and a second turbulence channel (22) is formed between the second side of the corrugated plate heat exchange assembly (20) and another fin unit (10).

3. The heat exchanger according to claim 2, characterized in that, There are multiple first turbulence channels (21) and multiple second turbulence channels (22), and the multiple first turbulence channels (21) and multiple second turbulence channels (22) are arranged at intervals along the length direction of the corrugated plate heat exchange assembly (20). Among them, a plurality of the first turbulence channels (21) are provided in a one-to-one correspondence with a plurality of the second turbulence channels (22).

4. The heat exchanger according to claim 3, characterized in that, Along the thickness direction of the corrugated plate heat exchange assembly (20), the geometric center line of the cross section of the first turbulence channel (21) is set at a distance from the geometric center line of the cross section of the corresponding second turbulence channel (22); and / or, along the thickness direction of the corrugated plate heat exchange assembly (20), the geometric center line of the cross section of the first turbulence channel (21) is set collinearly with the geometric center line of the cross section of the corresponding second turbulence channel (22).

5. The heat exchanger according to any one of claims 2 to 4, characterized in that, The corrugated plate heat exchange assembly (20) also forms a flow channel (23), which is offset from the first turbulence channel (21) and the second turbulence channel (22).

6. The heat exchanger according to claim 5, characterized in that, At least one of the first turbulence channel (21), the second turbulence channel (22) and the flow channel (23) includes a plurality of component segments, which are arranged to extend along the width direction of the corrugated plate heat exchange assembly (20), and the geometric center lines of each component segment are arranged at an angle.

7. The heat exchanger according to claim 5, characterized in that, The corrugated plate heat exchange assembly (20) includes: A first corrugated plate (201) has a plurality of first peaks (2010) and a plurality of first troughs (2011) formed on it. The plurality of first peaks (2010) and the plurality of first troughs (2011) are alternately arranged along the length direction of the first corrugated plate (201), and the top of two adjacent first peaks (2010) contacts the adjacent fin unit (10) so that the first corrugated plate (201) located between the adjacent first peaks (2010) and the fin unit (10) forms the first turbulence channel (21). The second corrugated plate (202) has a plurality of second peaks (2020) and a plurality of second troughs (2021) formed thereon. The plurality of second peaks (2020) and the plurality of second troughs (2021) are alternately arranged along the length direction of the second corrugated plate (202), and the top of two adjacent second peaks (2020) contacts another adjacent fin unit (10) so that a second turbulence channel (22) is formed between the second corrugated plate (202) located between adjacent second peaks (2020) and the fin unit (10).

8. The heat exchanger according to claim 7, characterized in that, The first corrugated plate (201) is disposed adjacent to the first trough (2011) and the second corrugated plate (202) is disposed in contact with the second trough (2021) adjacent to the first trough (2011) and the corresponding second trough (2021), and the first corrugated plate (201) and the second corrugated plate (202) between the adjacent first trough (2011) and the corresponding second trough (2021) form the flow channel (23).

9. The heat exchanger according to claim 7, characterized in that, The corrugated plate heat exchange assembly (20) includes a stress relief structure (200) which is protrudingly disposed on the surface of at least one of the first trough (2011) and the second trough (2021), and the height of the stress relief structure (200) is less than the depth of the first trough (2011) or the second trough (2021).

10. The heat exchanger according to claim 7, characterized in that, At least one of the first corrugated plate (201) and the second corrugated plate (202) has a plurality of flow channels (30) at its inlet end. The plurality of flow channels (30) are used to communicate with the flow channel (23). The plurality of flow channels (30) are evenly distributed along the width direction of the first corrugated plate (201) or the second corrugated plate (202), or the plurality of flow channels (30) are arranged to be interconnected and interleaved.

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