Heat exchanger

Abstract

The present disclosure relates to a heat exchanger (100) comprising a stack (105) of heat exchanger plates (107), a first set of channels (401) and a second set of channels (402), in each channel of the respective set of channels (401, 402), a fin structure (210) positioned between the heat exchanger plates (107), each heat exchanger plate (107) comprising a first inlet port (201), a first outlet port (211), a second inlet port (202) and a second outlet port (212), and a plurality of fin structures (210) formed at respective corner portions of respective heat exchanger plates (107) and extending through the stack (105), the heat exchanger (100) further comprising a distribution structure (220) at respective inlet ports (201, 202) and a collection structure (230) at respective outlet ports (211, 212), the distribution structure (220), the collection structure (230) being positioned between the ports (201, 202, 211, 212) and the respective fin structures (210), an internal interface (228) between the respective distribution structure (220) and the fin structure (210) in a respective channel of the first set of channels (401) and / or in a respective channel of the second set of channels (402) and / or an internal interface (238) between the respective collection structure (230) and the fin structure (210) is inclined with respect to the longitudinally extending fin direction (FD) and also with respect to the transverse direction (TD).

Description

Technical Field

[0001] The invention relates to a heat exchanger comprising a stack of heat exchanger plates which are stacked one on top of the other in a stacking direction. Background Art

[0002] Plate heat exchangers for transferring heat between different media (e.g., different fluids or gases) are well known in the art. A plate heat exchanger may include a plurality of heat exchanger plates in a stack, one stacked on top of the other between two end plates. A first set of channels may be formed in each second gap between the heat exchanger plates, and a second set of channels may be formed in other gaps between the heat exchanger plates. The components of the plate heat exchanger, and in particular the heat exchanger plates, are typically made of metal, but may also be made of any other material, as long as the material is strong enough and has sufficient thermal conductivity. The components of the plate heat exchanger may be assembled by being sandwiched between the end plates, or, for example, by using brazing, bonding or welding. Since the medium is in contact with the large surface area on the corresponding side of each heat exchanger plate, the plate heat exchanger provides efficient heat transfer. The plate heat exchanger may be a type commonly referred to as a plate-fin heat exchanger. A plate-fin heat exchanger typically includes stacked heat exchanger plates with a wavy structure sandwiched between the heat exchanger plates.

[0003] In order to efficiently utilize the available surface area of ​​the heat exchanger plates, it is typically desirable to design the heat exchanger so as to exhibit efficient distribution of the media flow across the entire width of the heat exchanger plates, and typically also to efficiently collect the media flow. Furthermore, it is typically desirable to design the heat exchanger so as to have mechanical stability in terms of material consumption, manufacturing cost and / or final weight.

[0004] In order to solve this problem, document CN207963578U discloses a plate-fin heat exchanger with guide distribution fins and exchange fins.

[0005] However, as will be explained below, the prior art literature does not disclose a heat exchanger which adequately meets the set of design criteria of providing an efficient distribution of the medium flow across the entire width of the heat exchanger plates and preferably also an efficient collection of the medium flow, while preferably also taking into account that the heat exchanger should be mechanically stable in terms of material consumption, manufacturing costs and / or final weight. Summary of the invention

[0006] The object of the present invention is to provide a heat exchanger which adequately meets a set of design criteria, namely providing an efficient distribution of the medium flow across the entire width of the heat exchanger plates and preferably also an efficient collection of the medium flow, while preferably also taking into account that the heat exchanger should be mechanically stable in terms of material consumption, manufacturing costs and / or final weight.

[0007] This object has been achieved by a heat exchanger comprising:

[0008] A stack of heat exchanger plates, which are stacked one on top of the other in the stacking direction,

[0009] a first set of channels formed in each first and second interspace between the heat exchanger plates,

[0010] a second set of channels formed in each second interspace between the heat exchanger plates,

[0011] wherein, in each of the first and second sets of channels, a fin structure formed by a sheet material folded back and forth is positioned between the heat exchanger plates such that the respective fin structure abuts the heat exchanger plates along a plurality of contact lines having a main extension extending parallel to the longitudinally extending fin direction, thereby defining a plurality of fluid channels forming the first and second sets of channels,

[0012] wherein each heat exchanger plate comprises four through-openings, the four through-openings being formed at respective corner portions of the respective heat exchanger plate and being configured to form a first inlet port extending through the stack along the stacking direction, a first outlet port extending through the stack along the stacking direction, a second inlet port extending through the stack along the stacking direction, and a second outlet port extending through the stack along the stacking direction, the first inlet port and the first outlet port being fluidly connected to each other via a first set of channels, and the second inlet port and the second outlet port being fluidly connected to each other via a second set of channels,

[0013] The heat exchanger further comprises: in each gap between the heat exchanger plates, a distribution structure at the corresponding inlet port and a collection structure at the corresponding outlet port,

[0014] wherein the respective distribution structure, respectively the respective collection structure is positioned between the respective port and the respective fin structure in the respective first group of channels and the respective second group of channels,

[0015] Wherein, the internal interface between the corresponding distribution structure and the fin structure in the corresponding channel in the first group of channels and / or in the corresponding channel in the second group of channels and / or the internal interface between the corresponding collecting structure and the fin structure is inclined relative to the longitudinally extending fin direction and also inclined relative to the transverse direction.

[0016] The first set of channels and the second set of channels are arranged alternately so that in each interspace between the heat exchanger plates there is either a channel from the first set of channels or a channel from the second set of channels. This can also be expressed as the first set of channels and the second set of channels are arranged alternately so that in each second interspace there is a channel from the first set of channels and in other interspaces between the heat exchanger plates, i.e. in interspaces that do not form part of the first set of channels there are channels from the second set of channels. In the phrase "each first second interspace", the word "first" is primarily a label within the phrase "each second interspace". In the phrase "each second second interspace", the first occurrence of the word "second" is primarily a label within the phrase "each second interspace". It may be noted that it is envisaged that the repetitive pattern of channels from the first set of channels or channels from the second set of channels in each interspace between the heat exchanger plates may be interrupted after a number of repetitions. Similarly, the ports extending through the stack may extend through all plates of the heat exchanger, or may extend through only a subset of adjacent plates forming one stack. The latter configuration may be the case, for example, when multiple stacks are brought together to form a combined heat exchanger. One example where this different configuration may be used is in a so-called multi-pass heat exchanger, for example.

[0017] It may be noted that in a preferred embodiment the fin structures are folded such that each fold has sufficient extension to bridge the distance between adjacent heat exchanger plates so that the respective fin structure abuts the adjacent heat exchanger plate between which it is positioned. In a preferred embodiment, the respective fin structure abuts the respective heat exchanger plate along a plurality of contact lines (which extend along the longitudinally extending fin direction), wherein the actual abutment forms a continuous or semi-continuous line contact. It may be noted in this context that the fin structures may be folded along a straight line such that the contact line may be a straight line extending along the longitudinally extending fin direction. However, the fin structures may be folded along a line having other shapes, such as, for example, a wavy line or a curved line, such that the contact line becomes a wavy line or a curved line that undulates back and forth along the main extension. Regardless of the shape of the folding line, it is preferred that the main extension extends parallel to the longitudinally extending fin direction.

[0018] In a preferred embodiment, the channels of the first group of channels (preferably each channel of the first group of channels) comprise a respective first fin structure positioned between the heat exchanger plates, and the channels of the second group of channels (preferably each channel of the second group of channels) comprise a respective second fin structure positioned between the heat exchanger plates. However, it should be noted that it is also conceivable that the heat exchanger may be designed such that only the channels of the first group of channels comprise a fin structure. Alternatively, it is also conceivable that the heat exchanger may be designed such that only the channels of the first group of channels comprise a fin structure.

[0019] The stacking direction is preferably orthogonal to the longitudinally extending fin direction.

[0020] The fin structure may be said to form part of a heat transfer area in which heat is transferred from the respective heat exchanger plate to the respective medium or from the respective medium to the respective heat exchanger plate. Since the respective fin structure is formed such that it presents a plurality of folds or partitions bridging the height of the respective channel, the medium in the respective channel is in contact not only with the respective heat exchanger plate but also with all folds or partitions in said channel. Since the respective fin structure also abuts the heat exchanger plate, heat may be transferred from the medium directly to the respective heat exchanger plate and may also be transferred indirectly by transferring to the fin structure which in turn transfers the heat to the respective heat exchanger plate.

[0021] The fin structure may be in the form of a thin sheet material folded back and forth. The fin structure is preferably formed by a thin metal sheet material folded back and forth. This may be referred to as a fin structure folded back and forth in an accordion-like design. The back and forth folds may have different designs. The folds may, for example, be shaped as repeating triangle waves, repeating square waves, repeating sine waves, or a combination thereof. The folds may, for example, be repeating square waves with fully rounded tops / bottoms or with rounded corners on each side of the tops / bottoms of each cycle. The rounding may, for example, be the shape of a sine wave or a radius. The folds may be in the form of a wave pattern, which may also be referred to as a repeating pattern of interconnected U-shapes and inverted U-shapes.

[0022] An advantage of a fold based on a square wave, a sine wave or a wave pattern is that the area of ​​the fin structure abutting the heat exchanger plate is increased compared to a fold pattern formed by, for example, repeating triangular waves. When this abutment area is increased, an increase in heat transfer can be achieved. In any case, the fact that the fin structure abuts the heat exchanger plate provides an improved stability between the fin structure and the heat exchanger plate. This is further advantageous because it allows a mechanically stable heat exchanger with improved structural support.

[0023] As seen along the flow direction of the corresponding medium, the corresponding fin structure is positioned between the corresponding distribution structure and the corresponding collection structure. As mentioned above, the corresponding distribution structure is positioned between the corresponding inlet port and the corresponding fin structure in the first group of channels and the second group of channels. The corresponding distribution structure is configured to distribute the flow from the corresponding inlet port to the corresponding fin structure so that the flow of the medium is distributed over the entire width of the corresponding channel. The corresponding collection structure is configured to collect the flow from the corresponding fin structure and guide the flow to the corresponding outlet port.

[0024] By designing the internal interface between the respective distribution structure and the fin structure in the respective channels in the first set of channels and / or in the respective channels in the second set of channels and / or the internal interface between the respective collection structure and the fin structure so that it is inclined relative to the longitudinally extending fin direction and also inclined relative to the transverse direction, it is facilitated to design a heat exchanger with ports of different shapes and sizes and still utilize a distribution and / or collection structure formed by a fin structure formed by folding back and forth material. Such a distribution or collection fin structure has multiple channels extending along its own or local fin direction and it must have an edge extending along the local fin direction and one side forming an interface with the port and one side forming an interface with the main fin structure. By allowing the interface between the distribution or collection structure and the main fin structure to be inclined, it provides greater variation in the shape of the interface with the port and still allows the distribution or collection structure to be substantially triangular or truncated triangle, which in turn facilitates manufacturing and assembly.

[0025] The respective inner interface may form an angle β with the fin direction, wherein the angle β is between 95° and 130°, preferably between 95° and 120°, or between 50° and 85°, preferably between 60° and 85°.

[0026] In this context it may be noted that the angle β may be angled such that the designer has two options available to him or her depending, for example, on the desired relative shape and size of the ports at the same transverse extension side (i.e. ports at the same longitudinal position), the desired thickness of the pressure panel portion closing the ports, the desired size and shape of the ports relative to the lateral width of the heat exchanger.

[0027] It may also be noted that in some cases, see e.g. Figure 6 , the internal interface can be inclined in the same direction on both main surfaces at the same port. For example, if there is a significant difference in the size of the ports, with a large port and a small port arranged side by side, the internal interface is typically inclined so that it is closer to the transversely extending centerline of the heat exchanger at the longitudinal side of the two main surfaces of the heat exchanger plate closest to the large port, and farther away from the said transversely extending centerline of the heat exchanger at the longitudinal side of the two main surfaces of the heat exchanger plate closest to the small port. However, the angle β on one main surface may be slightly different from the angle β on the other main surface, because the available area is basically determined by the port size and the pressurized portion of the selective closure of one or the other port. Figure 6In the example, the large port on the left leads to the channel in front of the plate, while the small port on the right is isolated from the channel in front of the plate. On the other side, the general direction of the tilt is the same, but because there is a compressed section along the underside of the large port on the left (right if viewed from the opposite side) that isolates it from the channel on the other side of the plate, the left-hand side (right-hand if viewed from the opposite side) of the interface needs to be more Figure 6 The inclination is slightly lower in the right hand side (left hand side if looking from the opposite side), while on the right hand side (left hand side if looking from the opposite side), the interface can extend all the way to the lower corner of the smaller port, because that port leads to a channel on the other side of the plate. Therefore, on the other side of the plate, the inclination is slightly greater, where the larger port is isolated from the channel on that side of the plate.

[0028] It may also be noted that in some cases, see e.g. Figure 7 , the internal interface may be inclined in opposite directions on the two major surfaces at the same port. For example, if the ports do not differ significantly in size, the internal interface is typically inclined so that on a first major side, it is closer to the transversely extending centerline of the heat exchanger at the longitudinal side closest to the port that is isolated from the channel on that major surface, and farther away from the transversely extending centerline at the longitudinal side closest to the port that leads to the channel on that major surface. Because the ports are of the same or substantially the same size, the available area varies primarily by whether there is a pressurized portion at the corresponding major surface that isolates the port from the channel. The angle β on one major surface may be the same as or slightly different from the angle β on another major surface because the available area is essentially determined by the port size and the pressurized portion that selectively isolates one or the other port. Figure 7In the embodiment of the present invention, the port on the left side leads to the channel in front of the plate, while the port on the right side is isolated from the channel in front of the plate. On the other side of the plate, the overall direction of the inclination of the internal interface is opposite, because there is a compressed portion along the lower side of the port on the left side (if viewed from the other side, the right side), while on the right-hand side (if viewed from the other side, the left-hand side), the interface may extend all the way to the lower corner of the right-hand port (if viewed from the other opposite side, the left-hand port) because the port leads to the channel on the other side of the plate. Therefore, the inclination is basically opposite on the other side of the plate. It can also be noted that one interface can be angled at an angle β, which is between 95° and 130°, preferably between 95° and 120°, or between 50° and 85°, preferably between 60° and 85°, while the directly opposite interface on the other main side of the plate can be at a 90° angle to the fin direction. It can also be noted that it is conceivable that both interfaces on the two main sides of the plate are at a 90° angle to the fin direction. Similarly, it can also be noted that one interface, such as the interface at the distribution structure or the collection structure, can be angled at an angle β, which is between 95° and 130°, preferably between 95° and 120°, or between 50° and 85°, preferably between 60° and 85°, while the interface at the other of the distribution structure or the collection structure can be at an angle of 90° to the fin direction. It can also be noted that it is conceivable that both interfaces at the distribution structure and the collection structure are at an angle of 90° to the fin direction. Therefore, each plate has four internal interfaces, which can be selected to be at different angles.

[0029] The respective internal interface may extend along a substantially straight line. This is advantageous because it facilitates the production of the distribution and / or collection structures and the fin structures, while still allowing different designs of the ports, and while still allowing a smooth distribution of the medium flow across the width of the heat exchanger. Preferably, the straight line is straight in the sense that along a central portion forming at least 75% of its length, any deviation transversely to its extension is less than +-10% of its length.

[0030] The internal interface at the respective inlet port and the internal interface at the respective outlet port are preferably inclined in the same general direction relative to the transverse direction.

[0031] Therefore, the internal interface at the first inlet port and the internal interface at the first outlet port are preferably inclined in the same general direction (first direction) relative to the transverse direction. In addition, the internal interface at the second inlet port and the internal interface at the second outlet port are preferably inclined in the same general direction (second direction) relative to the transverse direction. However, as mentioned above, the general direction of the inclination on the relative main surface can be the same or opposite. Therefore, the first general direction can be the same or opposite to the second direction. Inclination in the same general direction can be said to be that both directions are within an angle range of less than 90° relative to the fin direction, or both directions are within an angle range of greater than 90°. Inclination in the opposite general direction can be said to be that one direction is within an angle range of less than 90°, and the other direction is within an angle range of greater than 90°. Therefore, the phrase "the internal interface at the corresponding inlet port and the internal interface at the corresponding outlet port are preferably inclined in the same general direction relative to the transverse direction" is intended to refer to the fact that the corresponding internal interface of the first group of channels has the same general direction at the first inlet port as the internal interface of the first group of channels at the first outlet port. Similarly, the corresponding internal interface of the second group of channels has the same general direction at the second inlet port as the internal interface of the second group of channels at the second outlet port. It may also be noted in this context that the interfaces are only said to be inclined in the same general direction relative to the transverse direction, i.e., they are not necessarily at the same angle β, but only that both have an angle greater than 90° relative to the fin direction or both have an angle less than 90° relative to the fin direction. However, the angle β at which the internal interface near the first inlet port is inclined is preferably the same as the angle β at which the internal interface near the first outlet port is inclined. Similarly, the angle β at which the internal interface near the second inlet port is inclined is the same as the angle β at which the internal interface near the second outlet port is inclined. However, as discussed in detail above, the angle β on the first main side may be the same as the angle β on the other main side, or may be different, for example, depending on whether the ports have significantly different sizes, or whether they have the same or approximately the same size.

[0032] The port interface between the corresponding inlet port and the corresponding distribution structure, and the port interface between the corresponding outlet port and the collecting structure can be inclined relative to the fin direction, so that the distance between the port interface and the fin structure as measured along the fin direction increases with the distance from the edge of the corresponding heat exchanger plate closest to the corresponding port and extending along the longitudinally extending fin direction as seen along a line extending across the fin direction.

[0033] As seen along the flow direction of the corresponding medium, the corresponding fin structure is positioned between the corresponding distribution structure and the corresponding collection structure. As mentioned above, the corresponding distribution structure is positioned between the corresponding inlet port and the corresponding fin structure in the first group of channels and the second group of channels. The corresponding distribution structure is configured to distribute the flow from the corresponding inlet port to the corresponding fin structure so that the flow of the medium is distributed over the entire width of the corresponding channel. The corresponding collection structure is configured to collect the flow from the corresponding fin structure and guide the flow to the corresponding outlet port.

[0034] The disclosed design is advantageous because it allows for improved distribution of the medium in the first set of channels. The disclosed design is further advantageous because it allows for improved distribution of the medium in the second set of channels. The disclosed design is advantageous because it allows for improved collection of the medium in the first set of channels. The disclosed design is further advantageous because it allows for improved collection of the medium in the second set of channels.

[0035] By making the port interface between the corresponding inlet port and the corresponding distribution structure tilted relative to the fin direction, it is convenient to provide an optimized flow, so that the distribution of the medium in the first and / or second group of channels is improved. The tilted port interface allows a larger interface to be provided between the corresponding inlet port and the corresponding distribution structure. The tilted port interface allows the inlet port to be designed to be tilted or substantially triangular, or at least partially triangular, so that the interface is relatively large relative to the total surface area of ​​the port. The tilted port interface also allows a large interface of the distribution structure to be provided in a simple and cost-effective manner. For example, it is possible to manufacture the distribution structure by folding back and forth with a substantially triangular or truncated triangular sheet, in a manner similar to the fin structure discussed above. Therefore, the tilted port interface facilitates the flow distributed over the entire width of the distribution structure, thereby facilitating the flow optimized over the width of the heat exchanger.

[0036] By tilting the interface between the respective outlet ports and the respective collecting structure relative to the fin structure, efficient collection of the medium in the first set of channels or the second set of channels is facilitated, and thereby in turn optimization of the flow across the width of the heat exchanger is facilitated. The advantages discussed above with respect to the tilted port interface between the inlet port and the distribution structure are correspondingly applicable to the tilted port interface between the respective outlet port and the respective collecting structure.

[0037] The corresponding port interface can form an angle α with the fin direction. As mentioned above, the interface is inclined relative to the fin direction, that is, the angle α is greater than 90° but less than 180°, so that the corresponding interface is inclined. In this context, greater than and less than can refer to at least 5° different from 90°, respectively 180°. The angle α is measured between a line positioned in the center (as seen in the transverse direction) and extending along the fin direction on the one hand and the interface side facing the distribution or collection structure on the other hand. Preferably, the angle α is between 110° and 160°, more preferably between 120° and 150°. This is advantageous because it allows the flow to be optimized, so that the distribution of the medium and / or the collection of the medium as discussed above is improved. It can be noted that the port interface of the distribution structure can (but does not have to) be inclined at the same angle as the port interface of the collection structure.

[0038] The respective port interface may extend along a substantially straight line. This is advantageous because it allows a good distribution of the medium from the respective inlet port to the fin structure. This is advantageous because it allows a good collection of the medium from the fin structure. This is further advantageous because it allows fatigue optimization in the heat exchanger. Preferably, the straight line is straight in the sense that along a central portion forming at least 75% of its length, any deviation transversely to its extension is less than +-10% of its length.

[0039] The respective distribution structure and / or the respective collection structure extends from a first transverse center corner of the respective port to a second transverse outer corner of the respective port and leaves a transversely extending gap at a longitudinally extending edge closest to the respective port.

[0040] The term "lateral center" in the phrase "first lateral center corner" means that the first corner is centrally located as seen in the lateral direction. Correspondingly, "second lateral outer corner" refers to a corner that is located closer to the outer portion as seen in the lateral direction than the position of the first corner.

[0041] It may be noted that in a preferred embodiment, the first corner is positioned at a distance from the second corner in both the fin direction and the transverse direction, such that the port interface between the respective inlet port and the respective distribution structure is inclined. It may be noted that in a preferred embodiment, the first corner is positioned at a distance from the second corner in both the fin direction and the transverse direction, such that the port interface between the respective outlet port and the respective collecting structure is inclined.

[0042] With reference to the preferred embodiment with an inclined port interface, the gap may also be expressed as a missing corner piece of a corresponding distribution structure and / or a corresponding collection structure.

[0043] Providing a gap is advantageous, for example, for manufacturing the respective distribution structure and / or the respective collecting structure. By allowing the formation of a gap, for example, it is possible to allow the respective distribution structure and / or the respective collecting structure to be inclined and still end with an end portion as seen in the transverse direction, which is formed by a material piece which also has an extension in the direction of the fin at the transverse periphery, which makes such an end portion significantly more robust than if the respective distribution structure and / or the respective collecting structure ended with a sharp corner.

[0044] The open gaps may also help distribute the flow over a few laterally outermost channels, thereby reducing the risk of turbulence or other cornering effects in the flow from the ports to the channels in the fin structure causing any undesirable imbalance in the flow in the channels closest to the longitudinal edges.

[0045] The gap preferably has a lateral extension which is at least equal to three channels formed by the folds of the fin-like structure of the respective distribution structure and / or of the respective collecting structure.

[0046] Most of the flow from the corresponding inlet port is preferably distributed to the fin structure via the distribution structure, and correspondingly most of the flow from the fin structure is preferably collected to the corresponding outlet port via the collection structure; and

[0047] Therein, a small portion of the flow from the corresponding inlet port can be transferred to the fin structure via the gap, and correspondingly a small portion of the flow from the fin structure can be transferred to the corresponding outlet port via the gap.

[0048] This is advantageous because it allows to distribute the flow along the entire width of the individual heat exchanger plates seen in the transverse direction, wherein the majority of the flow is distributed via the distribution structure and a small portion of the flow is distributed to the fin structure via the gaps. This is further advantageous because it allows to collect the flow from the entire width of the individual heat exchanger plates seen in the transverse direction, wherein the majority of the flow is collected via the collecting structure and a small portion of the flow is collected from the fin structure via the gaps. The disclosed design introducing the gaps is advantageous because it allows an improved and efficient flow distribution and flow collection along the entire width of the heat exchanger plates. Preferably, at least 80%, more preferably at least 90% of the flow is distributed and / or collected via the respective distribution structure and / or the respective collecting structure.

[0049] The cutout in the corresponding plate forming the corresponding port can be arc-shaped along at least the main part of the lateral extension of the gap. The arc-shaped design of the corresponding port in the gap can facilitate the provision of a small portion of the flow smoothly guided into the fin structure without the need for distribution via the distribution structure. This helps to improve the flow distribution of the entire fin structure, thereby optimizing the flow distribution. The design of the corresponding port and the distribution structure can cooperate to guide and distribute the medium to the fin structure in an efficient manner. The arc-shaped design of the corresponding port in the gap can further facilitate the provision of a small portion of the flow smoothly collected from the fin structure without the need for collection via the collection structure. The design of the corresponding port and the collection structure can cooperate to guide and collect the medium from the fin structure in an efficient manner. In addition, this arc-shaped portion will lead to a reduction in local mechanical stress, which is particularly beneficial for the possibility of the plate being subjected to fatigue.

[0050] The distribution structure can be formed by a substantially triangular or truncated triangular fin structure. The shape is substantially triangular or truncated triangle, wherein the normal of the triangular surface extends in the stacking direction. It can be noted that in a preferred embodiment, the fin structure of the distribution structure, i.e. the folded portion back and forth, can have a structure similar to the fin structure discussed above. In this case, the distribution structure typically has diagonally extending fins; extending diagonally relative to the fin direction. This is advantageous because it allows the flow from the port positioned in the corner of the plate to be distributed over the entire lateral width, and still allows the corresponding distribution structure and / or the corresponding collection structure to be manufactured by folding the material sheet back and forth. The fin structure of the corresponding distribution structure and / or the corresponding collection structure helps to keep the heat exchanger plate at its intended mutual distance as seen along the stacking direction. The multiple contact lines formed by the fin structure at the corresponding distribution structure and / or the corresponding collection structure also participate in providing heat transfer. It can be noted that in a preferred embodiment, the fin structure of the corresponding distribution structure and / or the corresponding collection structure has vertical fins or folded portions as seen along the fin direction.

[0051] The collecting structure may be formed by a substantially triangular or truncated triangular fin structure. The shape is substantially triangular or truncated triangular, wherein the normal to the triangular surface extends along the stacking direction. It may be noted that in a preferred embodiment, the fin structure of the collecting structure, i.e. the back and forth folds, may have a similar structure to the fin structure discussed above. In this case, the collecting structure typically has fins extending diagonally as seen relative to the fin direction. The advantages have been discussed above with reference to the corresponding structure of the corresponding distribution structure.

[0052] The respective ports may be formed as substantially triangular ports. The respective triangular inlet ports help match the respective triangular distribution areas in a simple and efficient manner. The respective triangular outlet ports help match the respective triangular collection areas in a simple and efficient manner.

[0053] The first inlet and outlet ports may have different sizes than the second inlet and outlet ports.

[0054] In this context, the term "size" is to be understood as the total area of ​​the first port being different from the total area of ​​the second port. In a preferred embodiment, the first port and the second port are asymmetrical to each other. This allows the total flow of the first medium to differ from the total flow of the second medium.

[0055] However, it may also be noted that in other preferred embodiments the first port and the second port have the same size and shape. This is typically the case if the total flow rate of the first medium is intended to be approximately the same as the total flow rate of the second medium.

[0056] It may be noted that it is also conceivable that the inlet port of one medium has an asymmetrical size relative to the outlet port of the same medium. This allows efficient flow of the medium even in the case of significant changes in properties of the medium as it flows through the heat exchanger. Such changes may, for example, involve a phase change of all or part of the medium between a liquid phase and a gaseous phase.

[0057] The first inlet port may be arranged on a first longitudinally extending side of the stack of heat exchanger plates and the first outlet port may be arranged on a second longitudinally extending side of the stack of heat exchanger plates, the second longitudinally extending side being opposite to the first longitudinally extending side.

[0058] The second inlet port may be arranged on a first longitudinally extending side of the stack of heat exchanger plates and the second outlet port may be arranged on a second longitudinally extending side of the stack of heat exchanger plates, the first longitudinally extending side being opposite to the second longitudinally extending side.

[0059] In this context, "opposite" means opposite to the transverse direction. By this arrangement, a diagonally extending flow path is formed between the first inlet and the outlet and preferably also between the second inlet and the outlet. By the disclosed design, it is convenient to provide an improved distribution and collection of the medium in the heat exchanger. Providing a diagonally extending flow can provide good heat transfer.

[0060] In an alternative embodiment, the inlet port and the outlet port of the first medium are arranged on a first longitudinally extending side of the stack of heat exchanger plates, and the inlet port and the outlet port of the second medium are arranged on a second longitudinally extending side of the stack of heat exchanger plates, the second longitudinally extending side being opposite to the first longitudinally extending side.

[0061] According to one embodiment, the inlet port of the first medium is positioned on the same transverse extension side as the outlet port of the second medium, and the outlet port of the first medium is positioned on the same transverse extension side as the inlet port of the second medium. Therefore, as seen along the longitudinally extending fin direction, the two media flow in opposite directions. This can be called counterflow. Alternatively, the inlet ports of the two media are positioned on the same transverse extension side, and the outlet ports of the media are positioned on the other transverse extension side. This can be called parallel flow. Both counterflow and parallel flow can be combined with diagonal flow or flow in which both the inlet port and the outlet port of the first medium are arranged on the first longitudinal extension side of the stack. It can also be noted in this context that it is conceivable that the heat exchanger is designed so that it allows the flow direction of one or both media to be changed between different operating states. For example, it is conceivable that the first medium flows in a first flow direction in a first operating state and flows in an opposite direction in a second operating state. In this case, the port called the inlet port will become the outlet port, and vice versa. Similarly, the structure called the distribution structure will become the collection structure, and vice versa.

[0062] The individual fin structures of the individual channels in the first group of channels and the second group of channels may comprise at least a first and a second component arranged successively along the fin direction. Typically, there are manufacturability constraints on the maximum length of the fin structure along the flow direction. Such manufacturability constraints are caused, for example, by the fact that it is difficult to manufacture and transport rolls of sheet metal stacked on sheet metal over a certain width in a cost-effective manner. If the sheet is larger than a certain width, it is also generally difficult to fold the sheet back and forth in a cost-effective manner. A common maximum fin length is 500 mm. In order to manufacture a heat exchanger having a size of channels longer than this, it is necessary to arrange several fin structures in series successively along the flow direction. Therefore, an advantage of this design is that a heat exchanger can be provided with longer channels without being limited by manufacturability constraints.

[0063] The interface between the first and second components of each fin structure will be defined by the transversely extending edge of the first component opposite to the transversely extending edge of the second component and facing the transversely extending edge of the second component. In some embodiments, the transversely extending sides of the first and second components opposite to each other may abut against each other. In some embodiments, the transversely extending sides of the first and second components opposite to each other may be separated by a gap. The interface between the first and second components of the first fin structure is positioned at a first position along the fin direction. If there is a gap, the position is defined as the midpoint of the gap. The interface between the first and second components of the second fin structure is positioned at a second position along the fin direction. The first position, respectively the second position, is determined by selecting the size of the first and second components in each fin structure. For ease of assembly, the size or at least the tolerance of the first and second components is typically selected so that the actual total length is slightly shorter than the available nominal space. This generally results in a small longitudinal gap between the first and second components. It can be noted in this context that such a gap may also be provided intentionally. Whether the gap is undesirable but unavoidable or is intentionally provided, it is advantageous to select the dimensions of the first and second components of the first fin structure relative to the dimensions of the first and second components of the second fin structure such that the interface between the first and second components of the first fin structure becomes separated by a longitudinal distance from the interface between the first and second components of the second fin structure. By this design, it is ensured that any gap between the first and second components of the first fin structure will not be completely aligned with any interface between the first and second components of the second fin structure. In other words, it is ensured that any gap on the first side of the heat exchanger plate will not be completely aligned with any gap on the second side of the same heat exchanger plate.

[0064] It has been found that if there is a gap on both sides of a heat exchanger plate, there is a risk that the heat exchanger plate becomes deformed. Such deformation may occur during manufacture or during use.

[0065] By positioning the interface of the first and second fin structures at the first and second positions, respectively, and separating them by a longitudinal distance from each other, the heat exchanger plate will be subjected to a minimum amount of deformation. The deformation of the heat exchanger plate affects the flow of the medium through the channels, because there is a risk that the flow in the various channels will be inconsistent and not optimized. In the worst case, the deformation may be so severe that the flow may be completely interrupted in some channels. The deformation of the plate may also cause turbulence in the flow after or after the deformation. Therefore, the deformation of the channel may cause the heat exchanger to not function efficiently. The disclosed design is advantageous because it facilitates the provision of mechanically strong and deformation-resistant channels, thereby allowing the flow to be optimized so that the intended efficiency of the heat exchanger is achieved. The disclosed design is advantageous because it allows large heat exchangers to be manufactured in a cost-effective manner. It can also be noted in this context that the gap can be formed by the parallel edges of the first and second components, or the gap can be formed by the edges of the first and second components being angled relative to each other and thereby forming a triangular shape or a trapezoidal shape, wherein the parallel sides are formed by the longitudinal sides of the plate. It may also be noted that the gap may be formed as a void or absence of material across the entire width of the plate, or alternatively the gap may be formed by one or both components having a plurality of protrusions forming intermittent abutments and a discontinuous gap between the components of the fin structure. The protrusions may be formed as rods, small rectangular pieces, etc. Alternatively, the protrusions may be formed by cutting the edges of the components in a non-linear manner, such as, for example, in a sawtooth pattern, a wavy pattern, such as a sine wave or square wave pattern, so that the teeth or ridges of the waves of one component abut the edge of another component. Intermittent abutments may be used to provide a controlled size of any gap.

[0066] The dimensions of the first and second components of the first and second fin structures are preferably selected such that the distance between the first and second positions is such that any longitudinal gap at the center interface between the first and second components in the first channel of the first set of channels at least does not overlap with the center line of any longitudinal gap at the center interface between the first and second components in the first channel of the second set of channels, and vice versa. This can also be simply stated as any gap between the first and second components in the first channel of the first set of channels does not exceed the center line of any gap between the first and second components in the first channel of the second set of channels, or vice versa.

[0067] This is advantageous as it provides a channel that is mechanically strong and resistant to deformation, which allows the flow in the channel to be optimized, resulting in an improved efficiency of the heat exchanger.

[0068] It has been found that the strength of the heat exchanger is improved if any overlap of the gaps is limited so that the gaps do not exceed the midline of any gap on opposite sides of the same heat exchanger plate. Midline refers to an imaginary line or position located equidistant from the respective edges of the first and second parts facing each other as measured in the fin direction. Exceeding refers to the extension of the gap in the fin direction.

[0069] The dimensions of the first and second components of the first and second fin structures are preferably selected so that the distance between the first and second positions is such that any longitudinal gap at the central interface between the first and second components in the first channel of the first group of channels does not overlap with any longitudinal gap at the central interface between the first and second components in the first channel of the second group of channels, and vice versa.

[0070] It has been found that by ensuring that gaps on opposite sides of the same heat exchanger plate do not overlap at all, the strength of the heat exchanger is improved.

[0071] The interface between the first and second parts of the first fin structure can be defined by an edge of the first part and an edge of the second part of the first fin structure, wherein the edge of the first part can have an extension with a lateral component and face the edge of the second part, and the second edge can have an extension with a lateral component and face the edge of the first part, and wherein the edge of the first part can be arranged parallel to the edge of the second part.

[0072] As mentioned above, the edges may abut one another, or may be positioned with a gap therebetween. Preferably, the abutment or gap at the interface as measured along the fin direction is constant between any given point on the transversely extending edge of the first component and any directly opposite point on the transversely extending edge of the second component. Directly opposite points are points that are aligned along the fin direction. This is advantageous because it facilitates manufacturing. This is also advantageous because it facilitates providing balanced flow across the transverse width of the heat exchanger plate, because the parallel edges typically provide uniform flow characteristics across the transverse width of the interface as the medium transitions from the corresponding fluid channels in the first component to the corresponding fluid channels in the second component.

[0073] The edges of the first and second parts of the first fin structure may respectively extend at an angle γ relative to the fin direction, the angle γ preferably being between 95° and 130°, more preferably between 95° and 120°, or being 90°. Thus, the interface is either oriented such that the angle γ is preferably 90°, or is tilted such that the angle γ is preferably between 95° and 130°, more preferably between 95° and 120°.

[0074] In this context it may be noted that the angle γ may be selected independently of the other angles or it may be related to the angle β formed by the interface between the respective part of the fin structure and a distribution structure or a collecting structure provided near the inlet, respectively outlet port.

[0075] The angle β may be at an angle of 90° relative to the fin direction. In this case, the edges of the first and second components may extend at an angle γ of 90° relative to the fin direction, thereby allowing each first and second component to be formed by a rectangular piece of material that is folded back and forth perpendicular to its side edges. However, it is conceivable that even in the case where the angle β is at an angle of 90° relative to the fin direction, the edges of the edges of the first and second components of the first fin structure may respectively extend at an angle γ different from 90° relative to the fin direction. In this case, the angle γ is preferably between 95° and 130°, more preferably between 95° and 120°. The central interface of the first fin structure on the first side of the heat exchanger plate and the central interface of the second fin structure on the second side of the same heat exchanger plate may be angled so that they extend parallel to each other. In this case, it is advantageous to consider various discussions about the spacing of positions along the fin direction and the effects of any overlap of any gaps formed thereby. In this case, various discussions are applicable and relate to a line slightly inclined relative to the transverse direction; that is, the angle γ minus 90°. However, it is also conceivable that the central interface of the first fin structure on the first side of the heat exchanger plate and the central interface of the second fin structure on the second side of the same heat exchanger plate are angled so that they extend in the cross direction. It can be noted that the two angles are preferably but not necessarily selected to be the same but in opposite directions. It can be noted in this context that it may be advantageous to consider various discussions about the effects of the separation of positions along the fin direction and any overlap of any gaps formed thereby, especially if any or both gaps have a significant length along the fin direction. A significant length along the fin direction can, for example, be that the gap along the fin direction is greater than the complete repetition of the fold as measured across the fin direction. However, the central interfaces extending in the cross direction can alternatively be used to allow the gaps to actually cross each other, especially if at least one or both gaps do not have a significant length along the fin direction, because in this case the overlap will have a limited lateral extension compared to the case where the central interfaces extend parallel to each other. In this context it may be noted that the angle γ is between 95° and 130°, more preferably between 95° and 120°, and that the design in which the central interfaces cross each other may alternatively be expressed as an angle γ between 95° and 130°, more preferably between 95° and 120°, on one side of the heat exchanger plate, and between 50° and 85°, preferably between 60° and 85°, on the other side of the heat exchanger plate.

[0076] The angle β may be between 95° and 130°, more preferably between 95° and 120°, or between 50° and 85°, preferably between 60° and 85°. In one embodiment, it is preferred that the angle γ is the same as the angle β. In this case, it is possible to manufacture the fin structure from a rectangular piece of material that extends substantially transversely at an angle slightly inclined relative to the transverse direction, the angle being the angle β minus 90°. In this case, the leading and trailing edges of the sheet (the edges that will extend along the longitudinal edges of the heat exchanger) are trimmed in the respective directions at said angles, which are the angle β minus 90°. If the angles β at the distribution structure and the collecting structure are different, the angle γ may be selected to be the same as one of the angles β, or if the fin structure has more than two components, the respective angle γ may be selected to be the same as the respective angle β, and then one or more central interfaces formed by components that do not share an interface with the distribution structure or the collecting structure have an angle γ, for example, the angle γ is selected to be one of the angles β, or, for example, 90° relative to the fin direction. In this context it may be noted that the discussion about the angle γ being selected to be the same on both sides so that the interfaces on different sides are parallel or being selected to be different on different sides so that the interfaces on different sides intersect each other also applies to the case where the angle β is between 95° and 130°, more preferably between 95° and 120°, or between 50° and 85°, preferably between 60° and 85°.

[0077] This design is advantageous because it allows for a smooth flow transition of the media at the interface, because it facilitates manufacturing of the fin structure even with different specific design choices for other components of the heat exchanger, and because it produces a mechanically robust heat exchanger.

[0078] The interface between the first and second parts of the second fin structure can be defined by an edge of the first part and an edge of the second part of the second fin structure, wherein the edge of the first part can have an extension with a lateral component and face the edge of the second part, and the second edge can have an extension with a lateral component and face the edge of the first part, and wherein the edge of the first part can be arranged parallel to the edge of the second part. The advantages and variations thereof have been discussed with respect to corresponding features for the first fin structure, and this discussion is equally applicable to the second fin structure.

[0079] The edges of the first and second parts of the second fin structure can extend at an angle γ relative to the fin direction, preferably between 95° and 130°, more preferably between 95° and 120°, or 90°. Therefore, the interface is either oriented so that the angle γ is preferably 90°, or tilted at an angle so that the angle γ is preferably between 95° and 130°, more preferably between 95° and 120°. The advantages and variations thereof have been discussed with respect to the corresponding features for the first fin structure, and this discussion is equally applicable to the second fin structure.

[0080] In some embodiments, the geometry (such as height, width, shape and / or thickness) of the folded portions of the fin structures of the channels in the corresponding first and second groups of channels may be different from each other, thereby making it possible to perform heat exchange between two different media with different properties (such as different phases, different densities, different flow rates, etc.).

[0081] However, it may also be noted that the first set of channels and the second set of channels may be designed identically to each other.

[0082] Preferred embodiments appear in the dependent claims and in the description. It may be noted that the use of first, second, third, fourth, fifth, etc. should be considered primarily as labels for ease of reading and does not necessarily imply that all intermediate parts need to be numbered. For example, it may be noted that it is envisaged to have a design in which there are first, second, third, and fifth parts, while the fourth part is omitted. However, for ease of reading, we have been using first, second, third, fourth, etc. numbers as labels and in a sense based on embodiments that include all conceivable parts.

[0083] In general, unless otherwise expressly defined herein, all terms used in the claims should be interpreted according to their ordinary meaning in the technical field. Unless otherwise expressly stated, all references to "a / an / the [element, device, component, device, step, etc.]" should be openly interpreted as referring to at least one instance of the element, device, component, device, step, etc. Unless otherwise expressly stated, the steps of any method disclosed herein do not have to be performed in the exact order disclosed. BRIEF DESCRIPTION OF THE DRAWINGS

[0084] The above and other objects, features and advantages of the present disclosure will be better understood from the following illustrative and non-limiting detailed description of preferred embodiments of the present invention made with reference to the accompanying drawings, wherein like reference numerals are used to represent similar elements, and wherein:

[0085] Figure 1 A heat exchanger is disclosed.

[0086] Figure 2 Public Figure 1 Heat exchanger plates in a heat exchanger.

[0087] Figure 3 Public Figure 2 A heat exchanger plate having a fin structure arranged on the plate.

[0088] Figure 4 Shows Figure 1 First cross-sectional side view of stacked heat exchanger plates of a heat exchanger in FIG.

[0089] Figure 5 Shows Figure 1 Second cross-sectional side view of the stacked heat exchanger plates of the heat exchanger in FIG.

[0090] Figure 6 Public Figure 2 and Figure 3 part of the board.

[0091] Figure 7 A board according to another embodiment is disclosed. Figure 6 The corresponding part.

[0092] Figure 8 Disclosed based on Figure 7 The entire board of embodiment. DETAILED DESCRIPTION

[0093] The present invention will now be described more fully below with reference to the accompanying drawings, in which currently preferred embodiments of the present invention are shown. However, the present invention may be implemented in many different forms and should not be construed as limited to the embodiments set forth herein; on the contrary, these embodiments are provided to be comprehensive and complete and to fully convey the scope of the present invention to the skilled person.

[0094] Figure 1 A heat exchanger 100 is shown by way of example. The heat exchanger 100 comprises a stack 105 of heat exchanger plates. The stack 105 of heat exchanger plates is formed by stacking one heat exchanger plate 107 on top of another heat exchanger plate 107 along a stacking direction SD. The stack 105 of heat exchanger plates is arranged between two end plates 109 (only one of the two end plates is shown in the figure). It can be noted that the different embodiments disclosed herein are generally applicable to different fluid combinations in the first set of channels, respectively the second set of channels, such as gas-liquid, liquid-gas, gas-gas and liquid-liquid. However, the skilled person will appreciate that some embodiments are more suitable for some specific fluid combinations than for other fluid combinations.

[0095] The heat exchanger 100 comprises a first inlet 101 along a first longitudinally extending side LES1 and a first outlet 111 along a second longitudinally extending side LES2. The heat exchanger 100 further comprises a second inlet 102 along the first longitudinally extending side LES1 and a second outlet 112 along the second longitudinally extending side LES2. However, it should be noted that the first inlet 101 may be arranged along the second longitudinally extending side LES2 and the first outlet 111 may be arranged along the first longitudinally extending side LES1. It should also be noted that the second inlet 102 may be arranged along the second longitudinally extending side LES2 and the second outlet 112 may be arranged along the first longitudinally extending side LES1. However, it may be noted that in a preferred embodiment, the first inlet 101 and the second inlet 102 are arranged along the same longitudinally extending side and the first outlet 111 and the second outlet 112 are arranged along the same longitudinally extending side. The first longitudinally extending side LES1 and the second longitudinally extending side LES2 are arranged opposite to each other.

[0096] like Figure 4 , the heat exchanger 100 further includes a first set of channels 401 and a second set of channels 402. The first set of channels 401 is formed in each second interstices between the heat exchanger plates 107 in the stack 105 of heat exchanger plates. The second set of channels 402 is formed in each other interstices between the heat exchanger plates 107 in the stack 105 of heat exchanger plates.

[0097] In each channel of the first set of channels 401 and the second set of channels 402, the fin structure 210 is positioned between the heat exchanger plates 107. The respective fin structure 210 abuts the heat exchanger plates 107 along a plurality of contact lines 415. The fin structure 210 may be folded along a straight line such that the contact lines 415 extend parallel to the longitudinally extending fin direction FD. Figure 6 As indicated in , the fin structure 210 may alternatively be folded along lines having other shapes. Figure 6 In the example of , a wavy line or curve is shown, causing the contact line to become a wavy line or curve that fluctuates back and forth along the main extension. Regardless of the shape of the fold line, the main extension preferably extends parallel to the longitudinally extending fin direction. Thus, a plurality of fluid channels forming the first set of channels 401 and the second set of channels 402 are defined. The fin structure 210 is preferably formed by a sheet folded back and forth. For example Figure 4In the embodiment of the present invention, the folded portion of the corresponding fin structure 210 is substantially shaped as a sine wave with elongated legs or along the stacking direction SD. The structural type of the corresponding fin structure 210 can be different. For example, the folded portion of the corresponding fin structure 210 can be shaped as a square wave, a triangular wave, a sawtooth wave or a combination thereof. The fin structure 210 of the first group of channels 401 is longer than the fin structure 210 of the second group of channels 402 along the stacking direction SD. The folded portion of the fin structure 210 of the first group of channels 401 is wider than the folded portion of the fin structure 210 of the second group of channels 402 as measured along the transverse TD. However, it should be noted that the geometric shapes of the respective corresponding fin structures 210 of the respective channels may be different. For example, in some embodiments, the folded portion of the respective fin structures 210 of the respective channels in the corresponding first group of channels 401 and the second group of channels 402 may be the same. In some embodiments, the extension of the fin structure 210 of the first group of channels 401 along the stacking direction may be shorter than the extension of the fin structure 210 of the second group of channels 402. In some embodiments, the folded portion of the fin structure 210 of the first group of channels 401 may be narrower than the folded portion of the fin structure 210 of the second group of channels 402. In some embodiments, the folded portion of the fin structure 210 of the first group of channels 401 may be shaped as a square wave, while the folded portion of the fin structure 210 of the second group of channels 401 may be shaped as a sawtooth wave. It should be conceivable that the individual fin structures 210 of the individual channels in the first group of channels 401 may not be the same, but may differ in geometry. It should be conceivable that the individual fin structures 210 of the individual channels in the second group of channels 402 may not be the same, but may differ in geometry.

[0098] refer to Figure 2 , a heat exchanger plate 107 of the heat exchanger plates in the stack 105 is shown by way of example. The heat exchanger plate 107 comprises four through openings. The through openings are formed at respective corner portions of the heat exchanger plate 107. The through openings are configured to form a first inlet port 201, a first outlet port 211, a second inlet port 202 and a second outlet port 212 extending through the stack along the stacking direction SD.

[0099] It should be noted that each heat exchanger plate 107 in the stack 105 of heat exchanger plates comprises a first inlet port 201, a first outlet port 211, a second inlet port 202 and a second outlet port 212. Each port 201, 202, 211, 212 extends through the stack 105 along the stacking direction SD. The first inlet port 201 is arranged on a first longitudinally extending side LES1 of the heat exchanger plate 107. The first outlet port 211 is arranged on a second longitudinally extending side LES2 of the heat exchanger plate 107. The second inlet port 202 is arranged on the first longitudinally extending side LES1 of the heat exchanger plate 107. The second outlet port 212 is arranged on the second longitudinally extending side LES2 of the heat exchanger plate 107. Thus, the first inlet port 201 coincides with the first inlet 101, while the first outlet port 211 coincides with the first outlet 111. The first inlet port 201 and the first outlet port 211 are fluidly connected to each other via a first set of channels 401 formed in each second interspace. Thus, the first group of channels 401 forms a diagonally extending flow path by arranging the first inlet 101, the first outlet 111, the first inlet port 201, and the first outlet port 211 as discussed above. The second inlet port 202 coincides with the second inlet 102, and the second outlet port 212 coincides with the second outlet 112. The second inlet port 202 and the second outlet port 212 are fluidly connected to each other via the second group of channels 402 formed in each of the other second voids. The second group of channels 402 forms a diagonally extending flow path by arranging the second inlet 102, the second outlet 112, the second inlet port 202, and the second outlet port 212 as discussed above.

[0100] The heat exchanger 100 further comprises, in respective spaces between the heat exchanger plates 107, distribution structures 220° at respective inlet ports 201, 202 and collecting structures 230 at respective outlet ports 211, 212. The respective distribution structures 220 are positioned between respective inlet ports 201, 202 and respective fin structures 210 in respective first and second groups of channels 401, 402. The respective collecting structures 230 are positioned between respective outlet ports 211, 212 and respective fin structures 210 in respective first and second groups of channels 401, 402.

[0101] The interface 227 (also referred to as the port interface 227) between the respective inlet ports 201, 202 and the respective distribution structure 220 is inclined relative to the fin direction FD. Therefore, the distance between the interface 227 and the fin structure 210 as measured along the fin direction FD increases with increasing distance as seen along an imaginary line extending across the fin direction FD. The distance along the fin direction FD increases as the imaginary line is followed from the edge 121 of the respective heat exchanger plate 107 closest to the respective inlet port 201, 202 and extending along the fin direction FD. The interface 237 (also referred to as the port interface 237) between the respective outlet ports 211, 212 and the respective collecting structure 230 is inclined relative to the fin direction FD. Therefore, the distance between the interface and the fin structure 210 as measured along the fin direction FD increases with increasing distance as seen along an imaginary line extending across the fin direction FD. The distance along the fin direction FD increases as one follows an imaginary line from the edge 122 of the respective heat exchanger plate 107 which is closest to the respective outlet port 211 , 212 and which extends along the fin direction FD.

[0102] although Figure 2 Only the port interface 227 between the first inlet port 201 and the distribution structure 220 is shown, but it should be clearly understood by a skilled person that in practice, the port interface between the second inlet port 202 and the distribution structure 220 is designed in a similar manner as discussed above. Figure 2 Only the port interface 237 between the first outlet port 211 and the collecting structure 230 is shown, but it should be clearly understood by the skilled person that in practice, the port interface between the second outlet port 212 and the collecting structure 230 is designed in a similar manner as discussed above.

[0103] The respective port interface forms an angle α with the fin direction FD. It may be noted that in a preferred embodiment the angle α is between 110° and 160°, preferably between 120° and 150°.

[0104] The distribution structure 220 is formed as a triangular or truncated triangular distribution structure. It should be noted that in the distribution structure, the fins or folds extend along the internal fin direction arranged diagonally relative to the fin direction FD of the fin structure 210. Basically, the fins or folds of the distribution structure 220 extend between the corresponding inlet port and the fin structure 210 along the internal fin direction. Such fins or folds can be arranged vertically as viewed along their diagonal extension. The fins or folds of the distribution structure 220 can basically be any type discussed above with respect to the fin structure 210, wherein the fin direction refers to the internal fin direction of its diagonal extension.

[0105] The collecting structure 230 is formed as a triangular or truncated triangular collecting structure. Preferably, the collecting structure 230 is formed by a triangular or truncated triangular fin structure, so that the collecting structure 230 has a design similar to the distribution structure 220. It should be noted that in the collecting structure 230, the fins or folds extend along the internal fin direction diagonally arranged relative to the fin direction FD of the fin structure 210. The fins or folds of the collecting structure 230 can be substantially any type discussed above about the fin structure 210, wherein the fin direction refers to the internal fin direction of its diagonal extension. Depending on the positioning of different ports, the internal diagonally extending fin direction of the distribution structure 220° and the collecting structure 230 can be substantially in the same orientation or cross direction. Such fins or folds can be arranged vertically as viewed along their diagonal extension. The fins or folds of the collecting structure 230 can be substantially any type discussed above about the fin structure 210, wherein the fin direction refers to the internal fin direction of its diagonal extension. Depending on the positioning of the various ports, the internal diagonally extending fin directions of the distribution structure 220° and the collection structure 230 may be in substantially the same orientation or in a cross direction.

[0106] One edge of the distribution structure 220 extends from a first corner 223 of the first inlet port 201 to a second corner 224 of the inlet port 201. The first corner 223 may be referred to as a lateral center corner, and the second corner 224 may be referred to as a lateral outer corner. Figure 3 , 5 As shown in FIGS. 6 and 7 , the distribution structure 220 extends toward the second corner 224, but does not extend all the way to the second corner 223. This leaves a transversely extending gap 225 at the longitudinally extending edge 121 closest to the first inlet port 201. With this design, most of the flow from the first inlet port 201 is distributed to the fin structure 210 via the distribution structure 220. In addition, with this design, a small portion of the flow from the first inlet port 201 is transferred to the fin structure 210 via the gap 225. However, it can be noted that the distribution structure 220 can extend all the way to the second corner 223.

[0107] One edge of the collecting structure 230 extends from a first corner 233 of the first outlet port 211 to a second corner 234 of the outlet port 211. The first corner 233 may be referred to as a transverse center corner of the first outlet port 211, and the second corner 234 may be referred to as a transverse outer corner of the first outlet port 211. As shown, the collecting structure 230 extends toward the second corner 234, but does not extend all the way to the second corner 234. This leaves a transversely extending gap 235 at the longitudinally extending edge 122 closest to the first outlet port 211. With this design, most of the flow is collected to the first outlet port 211 via the collecting structure 230. In addition, with this design, a small portion of the flow from the fin structure 210 is transferred to the first outlet port 211 via the gap 235. However, it can be noted that the collecting structure 230 can extend all the way to the second corner 234.

[0108] The second inlet port 202 is preferably designed in a similar manner as the first inlet port 201 as discussed above, and the second outlet port 212 is preferably designed in a similar manner as the first outlet port 202 as discussed above.

[0109] like Figure 2 As further depicted in FIG, the respective inlet ports 201, 202 are designed as asymmetric inlet ports, i.e., the first inlet port 201, respectively, the second inlet port 202 has different sizes. This is because the respective inlet ports 201, 202 are designed to supply different media flows to their respective distribution structures 220 and their respective fin structures 210. It can be noted that in a preferred embodiment, and as shown in the figure, the first inlet port 201 and the second inlet port 202 have a triangular shape. This is to match the inlet ports 201, 202 with the respective distribution structures in a simple and efficient manner. The respective outlet ports 211, 212 are designed as asymmetric outlet ports, i.e., the first outlet port 211, respectively, the second outlet port 212 has different sizes. This is because the respective outlet ports 211, 212 are designed to receive different media flows from their respective collection structures 230. It can be noted that in a preferred embodiment, and as shown in the figure, the first outlet port 211 and the second outlet port 212 have a triangular shape. This is to match the outlet ports 211, 212 to the respective dispensing structures in a simple and efficient manner.It may be noted that in a preferred embodiment, and as shown, at least a large part of the lateral extension of the gap along the respective ports 201, 202, 211, 212 is arcuate.

[0110] like Figure 3 as well as Figure 6-8As shown in , the internal interface 228 between the corresponding distribution structure 220 and the fin structure 210 in the corresponding channel of the first group of channels 401 is inclined relative to the longitudinally extending fin direction FD and also inclined relative to the transverse direction TD. The internal interface 228 forms an angle β with the fin direction FD. The angle β is between 95° and 130°, preferably between 95° and 120°, or between 50° and 85°, preferably between 60° and 85°. Figure 3 and Figure 6 In, a design is disclosed, wherein the angle β is between 95° and 130°, preferably between 95° and 120°. Figure 7 and Figure 8 In , a design is disclosed, wherein the angle β is between 50° and 85°, preferably between 60° and 85°.

[0111] like Figure 3 and Figure 8 As shown in , the internal interface 238 between the corresponding collecting structure 230 and the fin structure 210 in the corresponding channel of the first set of channels 401 is inclined relative to the longitudinally extending fin direction FD and also inclined relative to the transverse direction TD. The internal interface 238 forms an angle β with the fin direction FD. The angle β is between 95° and 130°, preferably between 95° and 120°, or between 50° and 85°, preferably between 60° and 85°. Figure 3 and Figure 6 In, a design is disclosed, wherein the angle β is between 95° and 130°, preferably between 95° and 120°. Figure 8 In , a design is disclosed, wherein the angle β is between 50° and 85°, preferably between 60° and 85°.

[0112] On the opposite side of the plate 107, the internal interface 228 between the respective distribution structure 220 and the fin structure 210 in the respective channel of the second set of channels 402 is inclined relative to the longitudinally extending fin direction FD and also inclined relative to the transverse direction TD. The internal interface 228 forms an angle β with the fin direction FD. The angle β is between 95° and 130°, preferably between 95° and 120°, or between 50° and 85°, preferably between 60° and 85°.

[0113] exist Figure 3 and Figure 6 In , a design is disclosed, wherein the angle β on the opposite side is also between 95° and 130°, preferably between 95° and 120°. Figure 3 and Figure 6In the design, the internal interface 228 on the side shown in the figure and the internal interface on the opposite side have similar inclinations. Figure 7 and Figure 8 In the invention, a design is disclosed, wherein the angle β on the visible side of the figure is between 50° and 85°, preferably between 60° and 85°, and wherein the angle β is between 95° and 130°, preferably between 95° and 120°. That is, in Figure 7 and Figure 8 In the design of FIG. 4 , the internal interface 228 on the side shown in the figure and the internal interface 228 on the opposite side have opposite inclinations.

[0114] The above discussion regarding the direction of the interior interface 228 on the opposite side applies equally to the interior interface 238 on the opposite side.

[0115] like Figure 3 and Figure 6-8 As shown in , the respective internal interfaces 228, 238 preferably extend along a substantially straight line.

[0116] exist Figure 3 , 6 -8, the internal interface 228 at the first inlet port 201 and the internal interface 238 at the first outlet port 211 are inclined in the same direction relative to the transverse direction TD. In a preferred embodiment, the angle β is also the same for the two internal interfaces 228, 238 of the first channel 401. In a preferred embodiment, the internal interface 228 at the second inlet port 202 and the internal interface 238 at the second outlet port 212 are also inclined in the same direction relative to the transverse direction TD. As mentioned above, this "same direction" refers to the direction of the internal interfaces 228, 238 of the same channel, and the direction can be the same or different on opposite sides of the plate 107. In a preferred embodiment, the angle β is also the same for the two internal interfaces 228, 238 of the second channel 402.

[0117] For example Figure 3 and Figure 5As shown in FIG. 4 , the first fin structure 210a in the first channel of the first set of channels 401 includes a first component 210a1 and a second component 210a2. The first and second components 210a1-2 are arranged successively along the fin direction FD. Therefore, an interface is formed between the first and second components 210a1-2 by directly opposing the transversely extending side or edge of the first component 210a1 to the transversely extending side or edge of the second component 210a2. The interface may also be referred to as a center interface. It may be noted in this context that the word "center" is a label for easy distinction from other interfaces, and the word used as a label may also be, for example, a third interface. The transversely extending sides or edges are arranged parallel to each other. The interface extends across the fin direction. The transversely extending sides of the corresponding first and second components 210a1-2 extend at an angle γ relative to the fin direction. In a preferred embodiment, the transversely extending sides or edges of the corresponding first and second components 210a1-2 extend at 90° relative to the fin direction. The interface is positioned at a first position P1 along the fin direction. The interface is positioned by selecting the dimensions of the first and second components 210a1-2. It can be noted that the edges of the first and second parts 210a1-2 of the first fin structure 210a can respectively alternatively extend at an angle γ relative to the fin direction FD, wherein the angle γ is between 95° and 130°, preferably between 95° and 120°. It can be envisaged that the interface is formed by edges abutting each other, and it can be envisaged that the interface includes a gap.

[0118] For example Figure 5 As shown in , the second fin structure 210b in the first channel of the second group of channels 402 includes a first and a second component 210b1-2. The first and second components 210b1-2 are arranged successively along the fin direction. Therefore, an interface is formed between the first and second components 210b1-2 by directly opposing the transversely extending side or edge of the first component 210b1 and the transversely extending side or edge of the second component 210b2. The transversely extending sides or edges are arranged parallel to each other. The interface extends across the fin direction. The transversely extending sides or edges of the corresponding first and second components 210b1-2 extend at an angle γ relative to the fin direction FD. In a preferred embodiment, the transversely extending sides of the corresponding first and second components 210b1-2 extend at 90° relative to the fin direction. The interface is positioned at a second position P2 along the fin direction. The interface is positioned by selecting the size of the first and second components 210b1-2. It can be noted that the edges of the first and second parts 210b1-2 of the second fin structure 210b can respectively alternatively extend at an angle γ relative to the fin direction FD, wherein the angle γ is between 95° and 130°, preferably between 95° and 120°. It is conceivable that the interface is formed by edges abutting each other, and it is conceivable that the interface includes a gap.

[0119] Figure 5A stack 105 of heat exchanger plates and a stack of first and second groups of channels 401 and 402 are shown. The first and second positions P1 and P2 of the interface are spaced a distance DP from each other along the fin direction. The distance DP between the first and second positions P1 and P2 is such that any longitudinal gap G1 at the center interface 239a between the first and second parts 210a1-2 in the first channels of the first group of channels 401 does not overlap at least the centerline of any longitudinal gap G2 at the center interface 239b between the first and second parts 210b1-2 in the first channels of the second group of channels 402, and vice versa.

[0120] Preferably, any gaps between first and second components 210a1-2 in a first channel in the first set of channels 401 do not overlap with any gaps between first and second components 210b1-2 in a first channel in the second set of channels 402. Figure 4 , the dimensions of the first and second components 210a1-2 in the first channels in the first set of channels 401 have been selected so that the gap therebetween does not overlap with any gap between the first and second components 210b1-2 in the first channels in the second set of channels 402. It may be noted that fin structures 210 that are not adjacent fin structures 210 may include components 210a1-2, 210b1-2 having the same dimensions. That is, there may be gaps that overlap each other as long as the gaps are not formed on opposite sides of the same heat exchanger plate.

[0121] Those skilled in the art will recognize that the present invention is by no means limited to the preferred embodiments described above. On the contrary, many modifications and variations are possible within the scope of the appended claims. In addition, variations to the disclosed embodiments may be understood and implemented by those skilled in the art who practice the claimed invention by studying the drawings, the disclosure, and the appended claims.

Claims

1. A heat exchanger (100), comprising: a stack (105) of heat exchanger plates stacked one on top of the other in a stacking direction (SD), a first set of channels (401) formed in each first and second interspace between the heat exchanger plates (107), a second set of channels (402) formed in each second gap between the heat exchanger plates (107), wherein, in each of the first set of channels (401) and the second set of channels (402), a fin structure (210) formed by a sheet material folded back and forth is positioned between the heat exchanger plates (107) such that the respective fin structure (210) abuts the heat exchanger plates (107) along a plurality of contact lines (415) having a main extension extending parallel to a longitudinally extending fin direction (FD), thereby defining a plurality of fluid channels forming the first set of channels (401) and the second set of channels (402), wherein each heat exchanger plate (107) comprises four through openings (201, 202, 211, 212), the four through openings being formed at respective corner portions of the respective heat exchanger plate (107) and being configured to form a first inlet port (201) extending through the stack (105) along the stacking direction (SD), a first outlet port (211) extending through the stack (105) along the stacking direction (SD), a second inlet port (202) extending through the stack (105) along the stacking direction (SD), and a second outlet port (212) extending through the stack (105) along the stacking direction (SD), the first inlet port (201) and the first outlet port (211) being fluidly connected to each other via the first set of channels (401), and the second inlet port (202) and the second outlet port (212) being fluidly connected to each other via the second set of channels (402), The heat exchanger (100) further comprises a distribution structure (220) at the corresponding inlet ports (201, 202) and a collection structure (230) at the corresponding outlet ports (211, 212) in each gap between the heat exchanger plates (107), wherein the corresponding distribution structure (220) and the corresponding collection structure (230) are positioned between the corresponding ports (201, 202, 211, 212) and the corresponding fin structures (210) in the corresponding first group of channels (401) and the second group of channels (402), Wherein, the internal interface (228) between the corresponding distribution structure (220) and the fin structure (210) in the corresponding channel in the first group of channels (401) and / or in the corresponding channel in the second group of channels (402) and / or the internal interface (238) between the corresponding collecting structure (230) and the fin structure (210) is inclined relative to the longitudinally extending fin direction (FD) and is also inclined relative to the transverse direction (TD).

2. The heat exchanger (100) according to claim 1, wherein: The respective internal interface (228, 238) forms an angle β with the fin direction (FD), wherein the angle β is between 95° and 130°, preferably between 95° and 120°, or between 50° and 85°, preferably between 60° and 85°.

3. The heat exchanger (100) according to any one of the preceding claims, wherein: The respective interior interfaces (228, 238) extend along a generally straight line.

4. The heat exchanger (100) according to any one of the preceding claims, wherein: The internal interface (228) at the respective inlet ports (201, 202) and the internal interface (238) at the respective outlet ports (211, 212) are inclined in the same direction relative to the transverse direction (TD).

5. The heat exchanger (100) according to any one of the preceding claims, wherein: The port interfaces (227) between the respective inlet ports (201, 202) and the respective distribution structure (220), and the port interfaces (235) between the respective outlet ports (211, 212) and the collecting structure (230) are inclined relative to the fin direction (FD) so that the distance between the port interfaces (227, 235) and the fin structure (210) as measured along the fin direction (FD) increases with the distance from the edge (121, 122) of the respective heat exchanger plate (107) closest to the respective port (201, 202, 211, 212) and extending along the longitudinally extending fin direction (FD) as seen along an imaginary line extending transversely across the fin direction (FD).

6. The heat exchanger (100) according to claim 5, wherein: The respective port interface forms an angle (α) with the fin direction (FD), wherein the angle (α) is between 110° and 160°, preferably between 120° and 150°.

7. The heat exchanger (100) according to claim 5 or 6, wherein: The respective port interfaces extend along a substantially straight line.

8. The heat exchanger (100) according to any one of claims 5 to 7, wherein: The corresponding distribution structure (220) and / or the corresponding collection structure (230) extends from a first lateral center corner (223, 233) of the corresponding port (201, 202, 211, 212) to a second lateral outer corner (224, 234) of the corresponding port (201, 202, 211, 212), and leaves a lateral extension gap (225, 235) at the longitudinal extension edge (224, 234) closest to the corresponding port (201, 202, 211, 212).

9. The heat exchanger (100) according to claim 8, in, Most of the flow from the corresponding inlet ports (201, 202) is distributed to the fin structure (310) via the distribution structure (220), and correspondingly most of the flow from the fin structure (310) is collected to the corresponding outlet ports (211, 212) via the collection structure (230); and A small portion of flow from the corresponding inlet ports (201, 202) is transferred to the fin structure (310) via the gap (235), and correspondingly a small portion of flow from the fin structure (310) is transferred to the corresponding outlet ports (211, 212) via the gap (235).

10. The heat exchanger (100) according to claim 8 or 9, wherein: The cutouts in the respective heat exchanger plates (107) forming the respective ports (201, 202, 211, 212) are arc-shaped along at least a major part of the lateral extension of the gaps (225, 235).

11. The heat exchanger (100) according to any one of claims 5 to 10, wherein: The distribution structure (220) and / or the collection structure (230) are formed by a substantially triangular or truncated triangular fin structure.

12. The heat exchanger (100) according to any one of the preceding claims, wherein: The respective ports (201, 202, 211, 212) are formed as substantially triangular ports.

13. The heat exchanger (100) according to any one of the preceding claims, wherein: The first inlet port (201) is arranged on a first longitudinally extending side (LES1) of the stack (105) of heat exchanger plates, and the first outlet port (211) is arranged on a second longitudinally extending side (LES2) of the stack (105) of heat exchanger plates, the second longitudinally extending side (LES2) being opposite to the first longitudinally extending side (LES1), and wherein the second inlet port (202) is arranged on the first longitudinally extending side (LES1) of the stack (105) of heat exchanger plates, and the second outlet port (212) is arranged on the second longitudinally extending side (LES2) of the stack (105) of heat exchanger plates, the first longitudinally extending side (LES1) being opposite to the second longitudinally extending side (LES2).

14. The heat exchanger (100) according to any one of the preceding claims, wherein: In a first channel of the first set of channels (401), a first fin structure (210a) comprises at least a first and a second part (210a1-2) arranged successively along the fin direction (FD), wherein, in a first channel of the second group of channels (402), the first channel of the second group of channels (402) is a channel adjacent to the first channel of the first group of channels (401), the second fin structure (210b) comprises at least first and second components (210b1-2) arranged successively along the fin direction (FD), wherein a central interface (239a) between the first and second parts (210a1-2) of the first fin structure (210a) extends across a longitudinal fin direction (FD) and is positioned at a first position (P1) along the fin direction (FD), wherein a central interface (239b) between the first and second parts (210b1-2) of the second fin structure (210b) extends across the fin direction (FD) and is positioned at a second position (P2) along the fin direction (FD), and Wherein the first position (P1) and the second position (P2) are separated from each other by a longitudinal distance (DP).

15. The heat exchanger (100) according to any one of the preceding claims, wherein: The distance (DP) between the first position (P1) and the second position (P2) is such that any longitudinal gap (G1) at the central interface (239a) between the first and second parts (210a1-2) in the first channel of the first group of channels (401) at least does not overlap with the center line of any longitudinal gap (G2) at the central interface (239b) between the first and second parts (210b1-2) in the first channel of the second group of channels (402), and vice versa, wherein preferably, the distance (DP) between the first position (P1) and the second position (P2) is such that any longitudinal gap (G1) at the central interface (239a) between the first and second parts (210a1-2) in the first channel of the first group of channels (401) does not overlap with any longitudinal gap (G2) at the central interface (239b) between the first and second parts (210b1-2) in the first channel of the second group of channels (402), and vice versa.

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