heat exchanger

Abstract

The present disclosure relates to a heat exchanger (100) comprising a stack (105) of heat exchanger plates, a first set of channels (401) and a second set of channels (402), in each of the channels within each set of channels (401, 402), a fin structure (210) positioned between the heat exchanger plates (107) and formed at each corner of each heat exchanger plate (107) and extending through the stack (105), providing a first inlet port (201), a first outlet port (211), a second inlet port (202), and a second outlet port (212) for each heat exchanger plate. The plate (107) is provided, and the heat exchanger (100) further comprises a distribution structure (220) at each inlet port (201, 202) and a collecting structure (230) at each outlet port (211, 212), the distribution structure (220) and the collecting structure (230) being positioned between the ports (201, 202, 211, 212) and the respective fin structure (210), and the port interface between the inlet ports (201, 202) and the distribution structure (220), and the port interface between the outlet ports (211, 212) and the collecting structure (230) are inclined relative to the fin direction (FD).

Description

[Technical Field]

[0001] The present invention relates to a heat exchanger comprising a stack of heat exchanger plates stacked one above the other along a stacking direction. [Background technology]

[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 comprise a stack of multiple heat exchanger plates stacked one on top of the other between two end plates. A first set of channels may be formed in every second gap between the heat exchanger plates, and a second set of channels may be formed in every other gap between the heat exchanger plates. Plate heat exchanger components, particularly the heat exchanger plates, are typically made of metal but may be made of any other material as long as it is sufficiently strong and has sufficient heat-conducting properties. Plate heat exchanger components may be assembled by clamping between the end plates or, for example, by brazing, gluing, or welding. Plate heat exchangers provide efficient heat transfer because the media are in contact with a large surface area on each side of each heat exchanger plate. The plate heat exchanger may be of a type often referred to as a plate-fin heat exchanger. Plate fin heat exchangers typically comprise a stack of heat exchanger plates having a corrugated structure sandwiched between them.

[0003] In order to efficiently use the available surface area of ​​the heat exchanger plates, it is usually desirable to design a heat exchanger to exhibit efficient distribution, and typically also efficient collection, of the flow of the medium across the width of the heat exchanger plates. Furthermore, it is usually desirable to design the heat exchanger to be mechanically stable with respect to material consumption, manufacturing cost, and / or final weight.

[0004] In an attempt to address this, Chinese Utility Model Application No. 207963578 discloses a plate and fin heat exchanger with guided distribution fins and replacing fins.

[0005] However, as explained below, the prior art documents do not disclose heat exchangers that adequately address a set of design criteria that result in an efficient distribution, and preferably also an efficient concentration, of the flow of the medium across the entire width of the heat exchanger plates, while also taking into account that the heat exchanger should preferably be mechanically stable with respect to material consumption, manufacturing costs, and / or final weight. [Prior art documents] [Patent documents]

[0006] [Patent Document 1] China Utility Model Application No. 207963578 Summary of the Invention [Problem to be solved by the invention]

[0007] The object of the present invention is to provide a heat exchanger that adequately addresses a set of design criteria that result in an efficient distribution, and preferably also an efficient concentration, of the flow of the medium across the entire width of the heat exchanger plates, while preferably taking into account that the heat exchanger should be mechanically stable with respect to material consumption, manufacturing costs and / or final weight. [Means for solving the problem]

[0008] The object of the present invention is to provide a stack of heat exchanger plates stacked one above the other along a stacking direction, a first set of channels formed in all first second gaps between the heat exchanger plates; a second set of channels formed in every second gap between the heat exchanger plates; In each of the channels in the first and second sets of channels, a fin structure formed from a sheet folded back and forth is positioned between the heat exchanger plates so that each fin structure abuts the heat exchanger plate along a plurality of contact lines having main extensions extending parallel to a longitudinally extending fin direction, thereby defining a plurality of fluid channels forming said first and second sets of channels; each heat exchanger plate comprises four through openings formed in respective corners of the respective heat exchanger plate and 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 are fluidly connected to each other via a first set of channels, and the second inlet port and the second outlet port are fluidly connected to each other via a second set of channels; the heat exchanger further comprising, in each gap between the heat exchanger plates, a distribution structure at each inlet port and a collection structure at each outlet port; each distribution structure and each collection structure is positioned between a respective port and a respective fin structure within each of the first and second sets of channels; The port interfaces between each inlet port and each distribution structure, and between each outlet port and each collection structure, are each inclined with respect to the fin direction, such that the distance between the port interface and the fin structure, when measured along the fin direction, increases with increasing distance from the edge of the respective heat exchanger plate that is closest to the respective port and extends along the longitudinally extending fin direction, when viewed along a line extending across the fin direction.

[0009] The first and second sets of channels are alternately arranged such that every gap between the heat exchanger plates contains 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 and second sets of channels being alternately arranged such that every second gap contains a channel from the first set of channels and other gaps between the heat exchanger plates, i.e., gaps that do not form part of the first set of channels, contain a channel from the second set of channels. In the phrase "every first second gap," the word "first" is primarily a label within the phrase "every second gap." In the phrase "every second second gap," the first instance of the word "second" is primarily a label within the phrase "every second gap." It should be noted that the repeating pattern of either a channel from the first set of channels or a channel from the second set of channels in every gap between the heat exchanger plates may be interrupted by multiple 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 a stack. This latter configuration may be the case, for example, when there are multiple stacks joined together to form a composite heat exchanger. One example where such different configurations may be used is, for example, a so-called multi-pass heat exchanger.

[0010] It should be noted that in a preferred embodiment, one or more fin structures are folded such that all folds have sufficient extension to bridge the distance between adjacent heat exchanger plates so that each fin structure abuts the adjacent heat exchanger plate located between them. In a preferred embodiment, each fin structure abuts the respective heat exchanger plate along multiple contact lines having main extensions extending along the longitudinal fin direction, and the actual abutments form continuous or semi-continuous line contacts. In this regard, it should be noted that the fin structures may be folded along straight lines, such that the contact lines may be straight lines extending along the longitudinal fin direction. However, the fin structures may also be folded along lines having other shapes, such as wavy or curved lines, so that the contact lines become wavy or curved lines that undulate back and forth along the main extensions. Regardless of the shape of the fold lines, it is preferred that the main extensions extend parallel to the longitudinal fin direction.

[0011] In a preferred embodiment, the channels in the first set of channels, preferably each of the channels in the first set of channels, include a respective first fin structure positioned between the heat exchanger plates, and the channels in the second set of channels, preferably each of the channels in the second set of channels, include a respective second fin structure positioned between the heat exchanger plates. However, it is contemplated that the heat exchanger may be designed such that only the channels in the first set of channels include the fin structure. Alternatively, it is contemplated that the heat exchanger may be designed such that only the channels in the first set of channels include the fin structure.

[0012] The stacking direction is preferably perpendicular to the fin direction extending in the longitudinal direction.

[0013] The fin structures can be said to form a portion of the heat transfer area over which heat is transferred to and from the respective heat exchanger plates and the respective media. Because each fin structure is formed to exhibit multiple folds or gapped walls spanning the height of each channel, the media in each channel contacts not only the respective heat exchanger plates but also all of the folds or gapped walls within that channel. Because each fin structure also abuts the heat exchanger plates, heat may be transferred from the media directly to the respective heat exchanger plates or indirectly by being transferred to the fin structures, which transfer heat to the respective heat exchanger plates.

[0014] The fin structure may be in the form of a thin sheet folded back and forth. The fin structure is preferably formed from a thin metal sheet folded back and forth. This may be referred to as a fin structure folded back and forth in a bellows-like design. The folds back and forth may be of different designs. The folds may be shaped, for example, as a repeating triangular wave, a repeating square wave, a repeating curved wave, or a combination thereof. The folds may be, for example, a repeating square wave with a fully rounded top / bottom of each period or with rounded corners on each side of the top / bottom. The rounding may be, for example, in the shape of a curved wave or a radius. The folds may be in the form of a wavy pattern, which may be referred to as a repeating pattern of interconnected Us and s and inverted Us and s.

[0015] An advantage of folding based on a square wave, curved wave, or undulating pattern is that the area of ​​the fin structure that abuts the heat exchanger plate is increased compared to, for example, a folding pattern formed with a repeating triangular wave. This increased abutment area can result in increased heat transfer. In either case, the fact that the fin structure abuts the heat exchanger plate results in improved stability between the fin structure and the heat exchanger plate. This is further advantageous because it allows for a mechanically stable heat exchanger with improved structural support.

[0016] Each fin structure is positioned between a respective distribution structure and a respective collection structure when viewed along the flow direction of each medium. As described above, each distribution structure is positioned within each of the first and second sets of channels between a respective inlet port and a respective fin structure. Each distribution structure is configured to distribute flow from a respective inlet port to a respective fin structure such that the flow of medium is distributed across the entire width of each channel. Each collection structure is configured to collect the flow from each fin structure and direct the flow to a respective outlet port. In this regard, the following should be noted.

[0017] The disclosed designs are advantageous because they allow for improved distribution of media in a first set of channels. The disclosed designs are further advantageous because they allow for improved distribution of media within a second set of channels. The disclosed designs are advantageous because they allow for improved aggregation of media within a first set of channels. The disclosed designs are further advantageous because they allow for improved aggregation of media within a second set of channels.

[0018] The inclined port interface between each inlet port and each distribution structure relative to the fin direction facilitates optimized flow for improved media distribution within the first and / or second set of channels. The inclined port interface allows for a large interface between each inlet port and each distribution structure. The inclined port interface allows for a design with an inclined, essentially triangular, or at least partially triangular shape such that the inlet ports are relatively large relative to the total surface area of ​​the ports. The inclined port interface also allows for a large interface of the distribution structure in a simple and cost-effective manner. For example, the distribution structure can be manufactured from an essentially triangular or truncated triangular sheet folded back and forth in a manner similar to the fin structure described above. The inclined port interface therefore facilitates distributed flow across the entire width of the distribution structure, thereby facilitating optimized flow across the width of the heat exchanger.

[0019] The inclination of the interface between each outlet port and each collecting structure relative to the fin structure facilitates efficient collection of the medium within the first or second set of channels, thereby facilitating flow optimization across the width of the heat exchanger. The advantages discussed above with respect to the inclined port interface between the inlet port and the distribution structure are correspondingly applicable to the inclined port interface between each outlet port and each collecting structure.

[0020] Each port interface may form an angle α with the fin direction. As mentioned above, the interfaces are inclined relative to the fin direction such that each interface is inclined, i.e., the angle α is greater than 90° but less than 180°. In this context, "greater than" and "less than" may refer to at least 5°, respectively, between 90° and 180°. The angle α is measured between, on the one hand, a line centered in the lateral direction and extending along the fin direction, and, on the other hand, the side of the interface facing the distribution or collection structure. Preferably, the angle α is between 110° and 160°, more preferably between 120° and 150°. This is advantageous because it allows for flow optimization to improve media distribution and / or media collection, as mentioned above. It should be noted that the port interfaces of the distribution structure may, but need not, be inclined at the same angle as the port interfaces of the collection structure.

[0021] Each port interface may extend along a substantially straight line. This is advantageous because it allows for good distribution of the medium from each inlet port to the fin structure. This is advantageous because it allows for good collection of the medium from the fin structure. This is further advantageous because it allows for optimization of fatigue in the heat exchanger. The straight line is preferably straight, in the sense that along at least a central portion forming 75% of its length, any deviation across its extension is less than +-10% of its length.

[0022] Each distribution structure and / or each collection structure extends from a first laterally central corner of the respective port toward a second laterally outer corner of the respective port, leaving a laterally extending gap at the longitudinally extending edge closest to the respective port.

[0023] The term "laterally central" in the phrase "first laterally central corner" refers to the first corner being centrally located when viewed along the width direction. Correspondingly, the "second laterally outer corner" refers to a corner located closer to the outer side when viewed along the width direction compared to the location of the first corner.

[0024] It is noted that in a preferred embodiment, the first corner is positioned a distance from the second corner in both the fin direction and the lateral direction such that the port interface between each inlet port and each distribution structure is sloped.It is noted that in a preferred embodiment, the first corner is positioned a distance from the second corner in both the fin direction and the lateral direction such that the port interface between each outlet port and each collection structure is sloped.

[0025] With reference to preferred embodiments having angled port interfaces, the gaps may also be expressed as the presence of corner pieces of the respective distribution structures and / or the absence of the respective collection structures.

[0026] Providing gaps can be advantageous, for example, with regard to the manufacture of the respective distribution structures and / or respective collecting structures: by allowing the formation of gaps, for example, it is possible for the respective distribution structures and / or respective collecting structures to still terminate, when viewed along the lateral direction, at an end formed from a piece of material that is inclined and has an extension along the fin direction even at the lateral periphery, thereby making such an end significantly stronger compared to when the respective distribution structures and / or respective collecting structures terminate at a sharp corner.

[0027] The open gap can also help distribute the flow across the two lateral outermost channels, thereby reducing the risk that turbulence or other corner effects in the port-to-channel flow within the fin structure will cause undesirable imbalances in the flow in the channels closest to the longitudinal edges.

[0028] Preferably, the gap has a lateral extension at least equal to three channels formed from the folding of the fin-shaped structures of each distribution structure and / or each collection structure.

[0029] A majority of the flow from each inlet port is preferably distributed to the fin structure via a distribution structure, and a majority of the flow from the fin structure is preferably collected to the respective outlet port via a collection structure, and a minor portion of the flow from each inlet port may be transferred to the fin structure via the gap, and a minor portion of the flow from the fin structure may be transferred to the respective outlet port via the gap.

[0030] This is advantageous because it allows for flow distribution along the entire width of each heat exchanger plate, as viewed along the transverse direction, with a majority of the flow being distributed via the distribution structures and a minority of the flow being distributed to the fin structures via the gaps. This is further advantageous because it allows for flow collection from the entire width of each heat exchanger plate, as viewed along the transverse direction, with a majority of the flow being collected via the collecting structures and a minority of the flow being collected from the fin structures via the gaps. The disclosed design, which introduces gaps, is advantageous because it allows for improved, efficient flow distribution and collection along the entire width of the heat exchanger plate. Preferably, at least 80%, more preferably at least 90%, of the flow is distributed and / or collected via each distribution structure and / or each collecting structure.

[0031] The discontinuities in each plate forming each port may be arcuate along at least a majority of the lateral extension of the gap. The arcuate design of each port within the gap may facilitate smoothly directing a small portion of the flow into the fin structure without the need to be distributed through a distribution structure. This helps improve flow distribution throughout the fin structure, thus optimizing flow distribution. The design of each port and distribution structure may cooperate to direct and distribute the medium to the fin structure in an efficient manner. The arcuate design of each port within the gap may further facilitate smoothly collecting a small portion of the flow from the fin structure without the need to be collected through a collection structure. The design of each port and collection structure may cooperate to direct and collect the medium from the fin structure in an efficient manner. Furthermore, this type of arcuate shape results in reduced local mechanical stress, which is particularly beneficial with regard to the plate's ability to withstand fatigue.

[0032] The distribution structures may be formed by a fin structure that is essentially triangular or truncated triangular. The shape is essentially triangular or truncated triangular, with the normal to the triangular surface extending in the stacking direction. It should be noted that in a preferred embodiment, the fin structure of the distribution structure, i.e., the front-to-back folds, may have a structure similar to the fin structure described above. In that case, the distribution structure typically has fins that extend diagonally, obliquely to the fin direction. This is advantageous because it allows for full lateral distribution of the flow from ports located at the corners of the plate and also allows for the manufacture of each distribution structure and / or each collecting structure by folding a sheet of material back and forth. The fin structure of each distribution structure and / or each collecting structure helps to maintain the intended mutual distance between the heat exchanger plates when viewed along the stacking direction. Multiple contact lines formed by the fin structure of each distribution structure and / or each collecting structure also contribute to providing heat transfer. It should be noted that in a preferred embodiment, the fin structure of each distribution structure and / or each collecting structure has vertical fins or folds when viewed along the fin direction.

[0033] The collecting structures may be formed by essentially triangular or truncated triangular fin structures. The shape is essentially triangular or truncated triangular, with the normals of the triangular surfaces extending in the stacking direction. It should be noted that in preferred embodiments, the fin structures of the collecting structures, i.e. the front and back folds, may have a structure similar to the fin structures described above. In that case, the collecting structures typically have fins that extend obliquely when viewed relative to the fin direction. The advantages have been described above with reference to the corresponding structures of the respective distribution structures.

[0034] Each port may be formed as a substantially triangular port, with each triangular inlet port facilitating easy and efficient matching of each triangular distribution area, and each triangular outlet port facilitating easy and efficient matching of each triangular collection area.

[0035] The dimensions of the first inlet and outlet ports may be different from the dimensions of the second inlet and outlet ports.

[0036] In this context, the term "dimension" should be interpreted as meaning that the total area of ​​the first port is different from the total area of ​​the second port. In one preferred embodiment, the first and second ports are asymmetric with respect to each other. This allows for a difference in the total flow rate of the first medium relative to the total flow rate of the second medium.

[0037] However, it should also be noted that in other preferred embodiments, the first and second ports have the same size and shape, which is typically the case when the total flow rate of the first medium is intended to be approximately the same as the total flow rate of the second medium.

[0038] Note that it is also possible to have an asymmetry in the size of the inlet port of one medium relative to the outlet port of the same medium. This allows for efficient flow of that medium even if its properties change significantly as it flows through the heat exchanger. Such changes may include, for example, a full or partial phase change of the medium between liquid and gas phases.

[0039] The internal interface between each distribution structure and the fin structure in each channel of the first set of channels and / or each channel of the second set of channels and / or the internal interface between each collection structure and the fin structure may be inclined with respect to the longitudinally extending fin direction and with respect to the lateral direction.

[0040] Designing the internal interfaces between the respective distribution structures and fin structures, and / or between the respective collection structures and fin structures, in each channel of the first set of channels and / or each channel of the second set of channels to be inclined relative to the longitudinal fin direction and also inclined relative to the transverse direction facilitates the design of heat exchangers with various port shapes and sizes and facilitates the use of distribution and / or collection structures formed with fin structures formed from materials that can be folded back and forth. Such distribution or collection fin structures must have multiple channels extending along their own or local fin direction, and must have one edge extending along the local fin direction, one side interfacing with the port, and one side interfacing with the main fin structure. Allowing for a sloped interface between the distribution or collection structure and the main fin structure allows for a greater variety in the shape of the interface with the port and also allows the distribution or collection structure to be essentially triangular or truncated triangular, which facilitates manufacturing and assembly.

[0041] Each internal interface may form an angle β with the fin direction, the angle β being between 95° and 130°, preferably between 95° and 120°, or between 50° and 85°, preferably between 60° and 85°.

[0042] In this regard, it should be noted that the angle β may be inclined so that there are two options available to the designer to use, depending, for example, on the desired relative shape and size of the ports on the same laterally extending side, i.e., ports at the same longitudinal position, the desired thickness of the pressure panel portion closing the ports, and the desired size and shape of the ports relative to the lateral width of the heat exchanger.

[0043] Note that in some cases, the internal interface may be inclined in the same direction on both major surfaces of the same port, as shown in FIG. 6. For example, if there is a significant difference in port size between a large port and a small port arranged side by side, the internal interface typically slopes closer to the heat exchanger's transverse centerline on the longitudinal side closest to the large port on both major surfaces of the heat exchanger plate, and further away from the transverse centerline on the longitudinal side closest to the small port on both major surfaces of the heat exchanger plate. However, the angle β on one major surface may be slightly different from the angle β on the other major surface, since the available area is primarily determined by the port size and the indentations that selectively close one or the other port. In FIG. 6, the large port on the left opens to the channel in front of the plate, while the small port on the right closes off from the channel in front of the plate. On the other side, the general direction of the slope is the same, but on the left side, or right side when viewed from the opposite side, there is a depression along the underside of the large port, which closes off the channel on the other side of the plate, so that the left-hand side of the interface, or right-hand side when viewed from the opposite side, needs to be slightly lower than in FIG. 6, while on the right-hand side, or left-hand side when viewed from the opposite side, the interface may extend to the lower corner of the small port, since that port opens into the channel on the other side of the plate. Thus, the slope is slightly greater on the other side of the plate, where the large port is closed off from the channel on that side of the plate.

[0044] Note that, in some cases, the internal interface may be inclined in opposite directions on the two major surfaces of the same port, as shown in FIG. 7. For example, if there is no significant difference in port size, the internal interface typically is inclined so that the interface on the first major surface is closer to the transverse centerline of the heat exchanger on the longitudinal side closest to the port that is closed off from the channel on that major surface, and further away from that transverse centerline on the longitudinal side closest to the port that opens to the channel on that major surface. Since the ports are the same or approximately the same size, the available area varies primarily depending on the presence or absence of a depression on each major surface that closes off 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 the other major surface, since the available area is primarily determined by the port size and the depression that selectively closes off one or the other port. In FIG. 7, the port to the left opens to the channel in front of the plate, while the port to the right closes off from the channel in front of the plate. On the other side of the plate, the general direction of inclination of the internal interface is opposite, since there is a depression on the left side, or on the right side when viewed from the other side, along the underside of the port. On the right-hand side, or left-hand side when viewed from the other side, the interface may extend to the lower corner of the right-hand port, or left-hand port when viewed from the other side, because that port opens into a channel on the other side of the plate. Thus, the inclination is essentially opposite on the other side of the plate. It should also be noted that one of the interfaces may be inclined at an angle β between 95° and 130°, preferably between 95° and 120°, or between 50° and 85°, preferably between 60° and 85°, while the opposite interface on the other major side of the plate may be inclined at 90° relative to the fin direction. It should also be noted that both interfaces on both major sides of the plate are considered to be inclined at 90° relative to the fin direction. Similarly, it should be noted that one of the interfaces, such as the interface in the distribution structure or the collection structure, may be inclined at an angle β between 95° and 130°, preferably between 95° and 120°, or between 50° and 85°, preferably between 60° and 85°, and the interface in the other of the distribution structure or the collection structure may be inclined at 90° relative to the fin direction.It should also be noted that both interfaces in both the distribution and collecting structures are considered to be inclined at 90° to the fin direction. Thus, there are four internal interfaces per plate, which can be selected to be at various angles. Each internal interface may extend along a substantially straight line. This is advantageous because it facilitates the manufacture of the distribution and / or collecting structures, as well as the fin structure, while also allowing for various port designs and smooth distribution of the medium flow across the width of the heat exchanger. The straight line is preferably straight, in the sense that any deviation across its extension is less than ±10% of its length, at least along its central portion, which forms 75% of its length.

[0045] Preferably, the interior interface of each inlet port and the interior interface of each outlet port are inclined in the same general direction relative to the lateral direction.

[0046] Thus, the internal interface of the first inlet port and the internal interface of the first outlet port are preferably inclined in a first direction, which is the same general direction relative to the lateral direction. Furthermore, the internal interface of the second inlet port and the internal interface of the second outlet port are preferably inclined in a second direction, which is the same general direction relative to the lateral direction. However, as noted above, the general directions of inclination on the opposing major surfaces may be the same or opposite. Thus, the first general direction may be the same or opposite to the second direction. Inclining in the same general direction may refer to both directions being within an angular range of less than 90° or both directions being within an angular range of greater than 90° relative to the fin direction. Inclining in opposite general directions may refer to one direction being within an angular range of less than 90° and the other direction being within an angular range of greater than 90°. Thus, the phrase "preferably, the internal interfaces of each inlet port and each outlet port are inclined in the same general direction relative to the lateral direction" is intended to refer to the fact that, at the first inlet port, each of the internal interfaces of the first set of channels has the same general orientation as the internal interfaces of the first set of channels have at the first outlet port. Similarly, at the second inlet port, each of the second set of channels has the same general orientation as the internal interfaces of the second set of channels have at the second outlet port. In this regard, it should also be noted that the interfaces are only said to be inclined in the same general direction relative to the lateral direction; that is, the interfaces do not necessarily have the same angle β, but rather both have an angle greater than 90° or both have an angle less than 90° relative to the fin direction. However, the internal interface closer to the first inlet port is preferably inclined by the same angle β as the angle β of the inclination of the internal interface closer to the first outlet port. Similarly, the internal interface closer to the second inlet port is inclined by the same angle β as the angle β of the inclination of the internal interface closer to the second outlet port.However, as discussed in detail above, the angle β on the first major side may or may not be the same as the angle β on the other major side, depending, for example, on whether the ports are of significantly different sizes or whether the ports are the same or approximately the same size.

[0047] The first inlet port may be located on a first longitudinally extending side of the stack of heat exchanger plates and the first outlet port may be located on a second longitudinally extending side of the stack of heat exchanger plates, the second longitudinally extending side being opposite the first longitudinally extending side.

[0048] The second inlet port may be located on a first longitudinally extending side of the stack of heat exchanger plates and the second outlet port may be located on a second longitudinally extending side of the stack of heat exchanger plates, the first longitudinally extending side being opposite the second longitudinally extending side.

[0049] In this context, "opposite" refers to the opposite of the transverse direction. This arrangement creates a flow path that extends diagonally between the first inlet and outlet, and preferably also between the second inlet and outlet. The disclosed design facilitates improved distribution and collection of the medium within the heat exchanger. Providing a diagonal flow can result in good heat transfer.

[0050] In an alternative embodiment, the inlet and outlet ports for the first medium are both located on a first longitudinally extending side of the stack of heat exchanger plates, and the inlet and outlet ports for the second medium are both located on a second longitudinally extending side of the stack of heat exchanger plates, the second longitudinally extending side being opposite the first longitudinally extending side.

[0051] According to one embodiment, the inlet port of the first medium is located on the same laterally extending side as the outlet port of the second medium, and the outlet port of the first medium is located on the same laterally extending side as the inlet port of the second medium. This results in the two media flowing in opposite directions when viewed along the longitudinally extending fin direction. This may be referred to as counterflow. Alternatively, the inlet ports of both media are located on the same laterally extending side, and the outlet port of one medium is located on the other laterally extending side. This may be referred to as parallel flow. Both counterflow and parallel flow may be combined with diagonal flow, or with flow in which both the inlet and outlet ports of the first medium are located on the first longitudinally extending side of the stack. In this regard, it should be noted that the heat exchanger may be designed to allow for changing the flow direction of one or both of the media between various operating conditions. For example, a first medium may flow in a first flow direction in a first operating state and in the opposite direction in a second operating state. In such a case, what we call an inlet port becomes an outlet port, and vice versa. Similarly, what we call a distribution structure becomes a collection structure, and vice versa.

[0052] Each fin structure in each of the channels of the first and second sets of channels may have at least first and second portions that are alternating along the fin direction. Typically, there are manufacturability constraints on the maximum length of the fin structure along the flow direction. Such manufacturability constraints include, for example, the difficulty of cost-effectively manufacturing and transporting sheet metal on a sheet metal roll across a certain width. It is also often difficult to cost-effectively fold the sheet back and forth when the sheet is larger than a certain width. A typical maximum fin length is 500 mm. To manufacture a heat exchanger with dimensions with channels longer than this, several fin structures must be arranged in series and alternating along the flow direction. Therefore, an advantage of this design is that the heat exchanger can be configured with long channels without being limited by manufacturability constraints.

[0053] The interface between the first and second portions of each of the fin structures is defined by a laterally extending edge of the first portion opposite a laterally extending edge of the second portion. In some embodiments, the laterally extending sides of the opposite first and second portions may abut each other. In some embodiments, the laterally extending sides of the opposite first and second portions may be separated from each other by a gap. The interface between the first and second portions of the first fin structure is located at a first position along the fin direction. If a gap exists, the position is defined as the midpoint of the gap. The interface between the first and second portions of the second fin structure is located at a second position along the fin direction. The first and second positions are determined by selecting the dimensions of the first and second portions of each of the fin structures, respectively. For ease of assembly, the dimensions, or at least the tolerances, of the first and second portions are typically selected so that the actual overall length is slightly shorter than the nominal available space. This often results in a small longitudinal gap between the first and second portions. In this regard, it should be noted that such a gap may also be intentionally provided. Regardless of whether a gap is undesirable but unavoidable or intentionally provided, it is advantageous to select the dimensions of the first and second portions of the first fin structure relative to the dimensions of the first and second portions of the second fin structure so that the interface between the first and second portions of the first fin structure is separated by a longitudinal distance from the interface between the first and second portions of the second fin structure. This design ensures that any gap between the first and second portions of the first fin structure will not be perfectly aligned with any interface between the first and second portions of the second fin structure. That is, it ensures that a gap on a first side of a heat exchanger plate will not be perfectly aligned with a gap on a second side of the same heat exchanger plate.

[0054] It has been found that if there are gaps on either side of the heat exchanger plate, there is a risk of deformation of the heat exchanger plate, which can occur during manufacture or during use.

[0055] By positioning the interfaces of the first and second fin structures at the first and second positions, respectively, and spaced apart by a longitudinal distance, the heat exchanger plate undergoes minimal deformation. Deformation of the heat exchanger plate affects the flow of media through the channels, risking inconsistent and suboptimal flow in each channel. In the worst case, the deformation can be so sudden that there is a risk of complete disruption of flow in some channels. Plate deformation can also cause turbulence in the flow across the deformation. Therefore, channel deformation can cause the heat exchanger to function inefficiently. The disclosed design is advantageous in that it facilitates the provision of channels that are mechanically strong and resistant to deformation, thereby enabling optimized flow so that the intended efficiency of the heat exchanger is achieved. The disclosed design is also advantageous in that large heat exchangers can be manufactured cost-effectively. In this regard, it should also be noted that the gap may be formed from parallel edges of the first and second portions, or from edges of the first and second portions that are inclined relative to one another, thereby forming a triangular shape or a parallel-sided trapezoidal shape formed from the longitudinal sides of the plate. It should also be noted that the gap may be formed as a void or omission or material that penetrates the entire width of the plate, or the gap may be formed by one or both portions having multiple protrusions that form intermittent abutments and discontinuous gaps between portions of the fin structure. The protrusions may be formed as rods, small rectangular pieces, etc. Alternatively, the protrusions may be formed by non-linearly cutting one or more edges of one or more portions, such as in a wave-like pattern, e.g., a sawtooth pattern, a curved wave pattern, or a square wave pattern, so that the teeth or wave ridges of one portion abut the edges of the other portion. The intermittent abutments may be used to provide a controlled size for any gap.

[0056] The dimensions of the first and second portions of the first and second fin structures are preferably selected such that the distance between the first and second locations does not overlap the centerline of any longitudinal gap at the center interface between the first and second portions in a first channel of the first set of channels, or vice versa, which may also be referred to as "any gap between the first and second portions in a first channel of the first set of channels does not exceed the centerline of any gap between the first and second portions in a first channel of the second set of channels, or vice versa."

[0057] This is advantageous as it provides a channel that is mechanically strong and resistant to deformation, and allows the flow within the channel to be optimized so that the efficiency of the heat exchanger is improved.

[0058] It has been found that the strength of the heat exchanger is improved when the gap overlap is limited so that the gap does not extend beyond the centerline of the gap on the opposite side of the same heat exchanger plate. The centerline refers to an imaginary line or location that is positioned at an equal distance from the respective edges of the opposing first and second portions as measured along the fin direction. The term "exceeding" refers to the extension of the gap along the fin direction.

[0059] It is preferred that the dimensions of the first and second portions of the first and second fin structures are selected such that there is a distance between the first and second locations such that any longitudinal gap at the central interface between the first and second portions in a first channel of the first set of channels does not overlap with any longitudinal gap at the central interface between the first and second portions in a first channel of the second set of channels, and vice versa.

[0060] It has been found that by ensuring that all of the gaps on opposite sides of the same heat exchanger plate are free of overlap, the strength of the heat exchanger is improved.

[0061] The interface between the first and second portions of the first fin structure may be defined by an edge of the first portion and an edge of the second portion of the first fin structure, the edge of the first portion may have an extension with a lateral component and may be opposite an edge of the second portion, the second edge may have an extension with a lateral component and may be opposite that edge of the first portion, and the edge of the first portion may be disposed parallel to the edge of the second portion.

[0062] As mentioned above, the edges may abut each other or may be positioned across a gap. The abutment or gap at the interface, as measured along the fin direction, is preferably constant between any given point on the laterally extending edge of the first portion and any directly opposite point on the laterally extending edge of the second portion. Directly opposite points refer to points aligned along the fin direction. This is advantageous because it facilitates manufacturing. It is also advantageous because parallel edges generally provide uniform flow characteristics across the lateral width of the interface as the medium transitions from the respective fluid channels of the first portion to the respective fluid channels of the second portion, thereby facilitating balanced flow across the lateral width of the heat exchanger plate.

[0063] The edges of each of the first and second portions of the first fin structure may extend at an angle γ relative to the fin direction, with the angle γ preferably being between 95 and 130°, more preferably between 95 and 120°, or 90°. Thus, the interface is oriented such that the angle γ is preferably 90°, or is inclined at an angle such that the angle γ is preferably between 95 and 130°, more preferably between 95 and 120°.

[0064] In this regard, it should be noted that angle γ may be selected independently of the other angles, or angle γ may be related to angle β formed by the interface between each portion of the fin structure and a distribution or collection structure provided near each of the inlet and outlet ports.

[0065] The angle β may be inclined at 90° relative to the fin direction. In such cases, the edges of the first and second portions may extend at an angle γ of 90° relative to the fin direction, thereby allowing each first and second portion to be formed from a rectangular piece of material folded back and forth perpendicular to its side edges. However, even when the angle β is inclined at 90° relative to the fin direction, it is contemplated that the edges of each of the first and second portions of the first fin structure may extend at an angle γ relative to the fin direction other than 90°. In such cases, 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 inclined so that they extend parallel to each other. In such cases, it is advantageous to consider various discussions regarding separation along the fin direction and the impact of any gaps thus formed on any overlap. In such cases, various arguments are applicable and relate to lines slightly inclined relative to the transverse direction, i.e., the above-mentioned angle γ minus 90°. However, it is also possible 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 inclined so that they extend in the transverse direction. It should be noted that, while the two angles are preferably selected to be the same but in opposite directions, this is not required. In this regard, it should be noted that it may be advantageous to consider various arguments regarding the separation of positions along the fin direction and their impact on any overlap of any gaps thus formed, especially if one or both gaps have a significant length along the fin direction. A significant length along the fin direction may, for example, mean that the gap along the fin direction is greater than a complete repeat of the fold measured across the fin direction.However, particularly if at least one or both of the gaps do not have a significant length along the fin direction, central interfaces extending in a cross direction may alternatively be used so that the gaps may actually intersect each other, since the overlap in such cases has a limited lateral extension compared to when the central interfaces extend parallel to each other. In this regard, it should be noted that a design in which the angle γ is between 95° and 130°, more preferably between 95° and 120°, and the central interfaces intersect each other, may alternatively be expressed as the angle γ being 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.

[0066] 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, the angle γ is preferably the same as the angle β. In such cases, it is possible to manufacture the fin structure from a rectangular piece of material extending substantially transversely with a slight inclination relative to the transverse direction at an angle β minus 90°. The leading and trailing edges of the sheet, i.e., the edges that would extend along the longitudinal edges of the heat exchanger, are then trimmed in each direction at the angle β minus 90°. If the angles β in 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 there are three or more portions of the fin structure, each angle γ may be selected to be the same as each angle β. Then, for one or more central interfaces formed by portions of the collecting structure that do not share an interface with the distribution structure, the angle γ is selected, for example, as one of the angles β, or, for example, 90° relative to the fin direction. In this regard, it should be noted that the discussion regarding the angle γ being selected to be the same on both sides so that the interfaces on the different sides are parallel, or being selected to be different on different sides so that the interfaces on the different sides intersect each other, is equally applicable when the angle β is between 95° and 130°, more preferably between 95° and 120°, or between 50° and 85°, preferably between 60° and 85°.

[0067] The present design is advantageous because it allows for a smooth transition of the medium flow at the interface, which makes the fin structure easier to manufacture even for specific design choices that differ with respect to other parts of the heat exchanger, and results in a mechanically strong heat exchanger.

[0068] The interface between the first and second portions of the second fin structure may be defined by an edge of the first portion and an edge of the second portion of the second fin structure, the edge of the first portion having an extension with a lateral component and facing the edge of the second portion, the second edge having an extension with a lateral component and facing the edge of the first portion, and the edge of the first portion may be disposed parallel to the edge of the second portion. Advantages and variations of this have been discussed in relation to corresponding features regarding the first fin structure, and that discussion is equally applicable to the second fin structure.

[0069] The edges of each of the first and second portions of the second fin structure may extend at an angle γ relative to the fin direction, with angle γ preferably being between 95 and 130°, more preferably between 95 and 120°, or 90°. Thus, the interface is oriented such that angle γ is preferably 90°, or is inclined at an angle such that angle γ is preferably between 95 and 130°, more preferably between 95 and 120°. Advantages and variations of this have been discussed in relation to corresponding features relating to the first fin structure, and that discussion is equally applicable to the second fin structure.

[0070] In some embodiments, the geometry, such as the height, width, shape, and / or thickness of the fin structures of the channels of each of the first and second sets of channels, may be different from one another, thereby enabling heat exchange between two different media having different properties, such as different phases, different densities, different flows, etc.

[0071] However, it should also be noted that the first and second sets of channels may be designed to be equal to each other.

[0072] It should be noted that the use of first, second, third, fourth, fifth, etc. should be viewed primarily as labels for ease of reading, and does not necessarily mean that all intervening numbers of portions must be present. For example, it should be noted that it may be contemplated to have a design in which there is a first portion, a second portion, a third portion, and a fifth portion, with the fourth portion omitted. However, for ease of reading, the inventors have consistently used the numbering of first, second, third, fourth, etc. as labels, and in a sense, based on an embodiment that includes all possible portions.

[0073] In general, all terms used in the claims should be interpreted according to their ordinary meaning in the art unless otherwise expressly defined herein. All references to "a / an / [element, device, component, means, step, etc.]" should be interpreted broadly as referring to at least one instance of that element, device, component, means, step, etc., unless otherwise stated. The steps of any method disclosed herein do not have to be performed in the exact order disclosed, unless explicitly stated.

[0074] The present invention may also be summarized as relating to a heat exchanger comprising a stack of heat exchanger plates, a first set of channels, and a second set of channels, wherein each of the channels in each set of channels has a fin structure positioned between the heat exchanger plates, each heat exchanger plate having a first inlet port, a first outlet port, a second inlet port, and a second outlet port formed at a respective corner of the respective heat exchanger plate and extending through the stack, the heat exchanger further comprising a distribution structure at each inlet port and a collecting structure at each outlet port, the distribution structure and the collecting structure being respectively positioned between the ports and the respective fin structure, and the port interfaces between the inlet ports and the distribution structure and the port interfaces between the outlet ports and the collecting structure being respectively inclined with respect to the fin direction.

[0075] The above, as well as additional objects, features, and advantages of the present disclosure, will be better understood through the following illustrative and non-limiting detailed description of preferred embodiments of the invention, with reference to the accompanying drawings, in which like reference numerals will be used for like elements, in which: [Brief explanation of the drawings]

[0076] [Figure 1] FIG. 1 is a diagram of a heat exchanger. [Figure 2] FIG. 2 discloses a heat exchanger plate of the heat exchanger of FIG. 1. [Figure 3] FIG. 3 discloses the heat exchanger plate of FIG. 2 with fin structures disposed on the plate. [Figure 4] 2 is a first cross-sectional side view of a stack of heat exchanger plates of the heat exchanger of FIG. 1. [Figure 5] 2 is a second cross-sectional side view of a stack of heat exchanger plates of the heat exchanger of FIG. 1. [Figure 6] FIG. 4 discloses a portion of the plate of FIGS. 2 and 3. [Figure 7] 7A and 7B are views corresponding to FIG. 6 and disclosing a portion of a plate according to another embodiment. [Figure 8] FIG. 8 is a view disclosing the entire plate according to the embodiment of FIG. 7. DETAILED DESCRIPTION OF THE INVENTION

[0077] The invention will now be described more fully hereinafter with reference to the accompanying drawings, in which presently preferred embodiments of the invention are shown. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided for thoroughness and completeness, and will fully convey the scope of the invention to those skilled in the art.

[0078] FIG. 1 illustrates an example heat exchanger 100. The heat exchanger 100 includes a stack of heat exchanger plates 105. The stack of heat exchanger plates 105 is formed by stacking one heat exchanger plate 107 on top of the other heat exchanger plate 107 along a stacking direction SD. The stack of heat exchanger plates 105 is disposed between two end plates 109 (only one of the two end plates is shown). Note that the various embodiments disclosed herein are general terms useful for various combinations of fluids, such as gas-liquid, liquid-gas, gas-gas, and liquid-liquid, in each of the first and second sets of channels. However, those skilled in the art will understand that some embodiments are more suitable for certain combinations of fluids than others.

[0079] The heat exchanger 100 comprises a first inlet 101 along the first longitudinal side LES1 and a first outlet 111 along the second longitudinal side LES2. The heat exchanger 100 further comprises a second inlet 102 along the first longitudinal side LES1 and a second outlet 112 along the second longitudinal side LES2. However, it should be noted that the first inlet 101 may also be disposed along the second longitudinal side LES2 and the first outlet 111 may also be disposed along the first longitudinal side LES1. It should further be noted that the second inlet 102 may also be disposed along the second longitudinal side LES2 and the second outlet 112 may also be disposed along the first longitudinal side LES1. However, it should be noted that in a preferred embodiment, the first and second inlets 101, 102 are arranged along the same longitudinally extending side, and the first and second outlets 111, 112 are arranged along the same longitudinally extending side, and the first and second longitudinally extending sides LES1, LES2 are arranged opposite each other.

[0080] 4, the heat exchanger 100 further comprises a first set of channels 401 and a second set of channels 402. The first set of channels 401 is formed in all second gaps between the heat exchanger plates 107 of the stack of heat exchanger plates 105. The second set of channels 402 is formed in all other gaps between the heat exchanger plates 107 of the stack of heat exchanger plates 105.

[0081] In each channel of the first and second channel sets 401, 402, a fin structure 210 is positioned between the heat exchanger plates 107. Each fin structure 210 abuts against the heat exchanger plate 107 along a plurality of contact lines 415. The fin structure 210 may be folded along a straight line so that the contact lines 415 extend parallel to the longitudinal fin direction FD. However, as shown in FIG. 6, the fin structure 210 may alternatively be folded along lines having other shapes. In the example of FIG. 6, the contact lines are shown as wavy or curved lines that undulate back and forth along their main extensions. Regardless of the shape of the fold lines, the main extensions preferably extend parallel to the longitudinal fin direction. This defines a plurality of fluid channels that form the first and second channel sets 401, 402. The fin structure 210 is preferably formed from a sheet that is folded back and forth. For example, as shown in FIG. 4 , the folds of each fin structure 210 are essentially shaped as curved waves with elongated legs or along the stacking direction SD. The type of structure of each fin structure 210 may vary. For example, the folds of each fin structure 210 may be shaped as a square wave, a triangular wave, a sawtooth wave, or a combination thereof. The extension of the fin structures 210 of the first set of channels 401 along the stacking direction SD is longer than the extension of the fin structures 210 of the second set of channels 402 along the stacking direction SD. The folds of the fin structures 210 of the first set of channels 401 are wider than the folds of the fin structures 210 of the second set of channels 402 when measured along the transverse direction TD. However, it should be noted that the geometric shape of each of the respective fin structures 210 of each of the channels may vary. For example, in some embodiments, the folds of each of the fin structures 210 of each channel of each of the first set of channels 401 and the second set of channels 402 may be identical. In some embodiments, the extension of the fin structures 210 of the first set of channels 401 along the stacking direction may be shorter than the extension of the fin structures 210 of the second set of channels 402.In some embodiments, the folds of the fin structures 210 in the first set of channels 401 may be narrower than the folds of the fin structures 210 in the second set of channels 402. In some embodiments, the folds of the fin structures 210 in the first set of channels 401 may be shaped as a square wave, while the folds of the fin structures 210 in the second set of channels 401 may be shaped as a sawtooth wave. It should be appreciated that each individual fin structure 210 in each channel of the first set of channels 401 may not be identical and may have different shapes. It should be appreciated that each individual fin structure 210 in each channel of the second set of channels 402 may not be identical and may have different shapes.

[0082] 2, a heat exchanger plate 107 of a stack 105 of heat exchanger plates is shown as an example. The heat exchanger plate 107 has four through-openings. The through-openings are formed at each corner 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 that extend through the stack along the stacking direction SD.

[0083] It should be noted that each heat exchanger plate 107 of 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 located on a first longitudinally extending side surface LES1 of the heat exchanger plate 107. The first outlet port 211 is located on a second longitudinally extending side surface LES2 of the heat exchanger plate 107. The second inlet port 202 is located on the first longitudinally extending side surface LES1 of the heat exchanger plate 107. The second outlet port 212 is located on a second longitudinally extending side surface LES2 of the heat exchanger plate 107. Thus, the first inlet port 201 coincides with the first inlet 101, and 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 the first set of channels 401 formed in all of the second gaps. The first set of channels 401 thereby forms an obliquely extending flow path by having the first inlet 101, the first outlet 111, the first inlet port 201, and the first outlet port 211 arranged as described 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 set of channels 402 formed in all of the other second gaps. The second set of channels 402 has the second inlet 102, second outlet 112, second inlet port 202, and second outlet port 212 arranged as described above, thereby forming an obliquely extending flow path.

[0084] The heat exchanger 100 further comprises, in each space between the heat exchanger plates 107, a distribution structure 220 at each inlet port 201, 202 and a collecting structure 230 at each outlet port 211, 212. Each distribution structure 220 is positioned between each inlet port 201, 202 and each fin structure 210 in each first and second set of channels 401, 402. Each collecting structure 230 is positioned between each outlet port 211, 212 and each fin structure 210 in each first and second set of channels 401, 402.

[0085] The interface 227, also referred to as the port interface 227, between each inlet port 201, 202 and each distribution structure 220 is inclined with respect to the fin direction FD. As a result, when measured along the fin direction FD, the distance between the interface 227 and the fin structure 210 increases with increasing distance when viewed along an imaginary line extending across the fin direction FD. The distance along the fin direction FD increases as one moves along the imaginary line from the edge 121 of each heat exchanger plate 107, which is closest to each inlet port 201, 202 and extends along the fin direction FD. The interface 237, also referred to as the port interface 237, between each outlet port 211, 212 and each collection structure 230 is inclined with respect to the fin direction FD. As a result, when measured along the fin direction FD, the distance between the interface 227 and the fin structure 210 increases with increasing distance when viewed along an imaginary line extending across the fin direction FD. As one proceeds along an imaginary line from the edge 122 of each heat exchanger plate 107 that is closest to the respective outlet port 211, 212 and extends along the fin direction FD, the distance along the fin direction FD increases.

[0086] 2 only shows the port interface 227 between the first inlet port 201 and the distribution structure 220, it should be clear to those skilled in the art that in practice the port interface between the second inlet port 202 and the distribution structure 220 is designed in a similar manner as described above. Furthermore, while FIG. 2 only shows the port interface 237 between the first outlet port 211 and the collecting structure 230, it should be clear to those skilled in the art that in practice the port interface between the second outlet port 212 and the collecting structure 230 is designed in a similar manner as described above.

[0087] Each port interface forms an angle α with the fin direction FD. Note that in a preferred embodiment, the angle α is between 110° and 160°, preferably between 120° and 150°.

[0088] 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 an internal fin direction that is disposed obliquely relative to the fin direction FD of the fin structure 210. Essentially, the fins or folds of the distribution structure 220 extend along said internal fin direction between the respective inlet ports and the fin structure 210. The fins or folds themselves may be disposed vertically when viewed along their oblique extension. Essentially, the fins or folds of the distribution structure 220 may be of any type as described above with respect to the fin structure 210, with the fin direction referring to their obliquely extending internal fin direction.

[0089] The collecting structure 230 is formed as a triangular or truncated triangular collecting structure. Preferably, the collecting structure 230 is formed with a triangular or truncated triangular fin structure so that the collecting structure 230 has a similar design to the distribution structure 220. It should be noted that in the collecting structure 230, the fins or folds extend along an internal fin direction that is diagonally arranged relative to the fin direction FD of the fin structure 210. The fins or folds of the collecting structure 230 may essentially be of any type as described above with respect to the fin structure 210, with the fin direction referring to the diagonally extending internal fin direction. Depending on the positioning of the various ports, the internal diagonally extending fin directions of the distribution structure 220 and the collecting structure 230 may essentially be in the same direction or in intersecting directions. The fins or folds themselves may be arranged vertically when viewed along their diagonal extension. The fins or folds of the collecting structure 230 may essentially be of any type as described above with respect to the fin structure 210, with the fin direction referring to the diagonally extending internal fin direction. Depending on the positioning of the various ports, the diagonally extending fin directions within the distribution structure 220 and the collecting structure 230 may be essentially in the same direction or in intersecting directions.

[0090] One edge of the distribution structure 220 extends from a first corner 223 of the first inlet port 201 toward a second corner 224 of the inlet port 201. The first corner 223 may be referred to as the lateral center corner, and the second corner 224 may be referred to as the lateral outer corner. For example, as shown in FIGS. 3, 5, and 6, the distribution structure 220 extends toward but does not extend all the way to the second corner 224. This leaves a lateral gap 225 at the longitudinally extending edge 121 closest to the first inlet port 201. With this design, a majority of the flow from the first inlet port 201 is distributed through the distribution structure 220 to the fin structure 210. Furthermore, with this design, a small portion of the flow from the first inlet port 201 is transferred to the fin structure 210 through the gap 225. However, it should be noted that the distribution structure 220 may extend to the second corner 224 .

[0091] One edge of the collecting structure 230 extends from a first corner 233 of the first outlet port 211 toward a second corner 234 of the outlet port 211. The first corner 233 may be referred to as the lateral center corner of the first outlet port 211, and the second corner 234 may be referred to as the lateral outer corner of the first outlet port 211. As shown, the collecting structure 230 extends toward but does not extend all the way to the second corner 234. This leaves a laterally extending gap 235 at the longitudinally extending edge 122 closest to the first outlet port 211. With this design, the majority of the flow is collected through the collecting structure 230 and into the first outlet port 211. Furthermore, with this design, a small portion of the flow from the fin structure 210 is transferred through the gap 235 to the first outlet port 211. However, it should be noted that the collection structure 230 may extend to the second corner 234 .

[0092] The second inlet port 202 is preferably designed in a similar manner to the first inlet port 201 as described above, and the second outlet port 212 is preferably designed in a similar manner to the first outlet port 202 as described above.

[0093] As further shown in FIG. 2 , each inlet port 201, 202 is designed as an asymmetric inlet port, i.e., the first inlet port 201 and the second inlet port 202 have different dimensions. This is because each inlet port 201, 202 is designed to supply different media flows to its respective distribution structure 220 and to its respective fin structure 210. Note that in a preferred embodiment, as shown in the figure, the first inlet port 201 and the second inlet port 202 have a triangular shape. This is for easy and efficient alignment of the inlet ports 201, 202 with their respective distribution structures. Each outlet port 211, 212 is designed as an asymmetric outlet port, i.e., the first outlet port 211 and the second outlet port 212 have different dimensions. This is because each outlet port 211, 212 is designed to accept different media flows from its respective collection structure 230. It should be noted that in a preferred embodiment, as shown, the first outlet port 211 and the second outlet port 212 have a triangular shape. This is to facilitate and efficiently align the outlet ports 211, 212 with their respective distribution structures. It should be noted that in a preferred embodiment, as shown, each port 201, 202, 211, 212 is arc-shaped along at least a majority of the lateral extension of the gap.

[0094] As also shown in Figures 3 and 6-8, the internal interface 228 between each distribution structure 220 and fin structure 210 in each channel of the first set of channels 401 is inclined with respect to the longitudinally extending fin direction FD and also with respect 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°. Figures 3 and 6 disclose designs in which the angle β is between 95° and 130°, preferably between 95° and 120°. Figures 7 and 8 disclose designs in which the angle β is between 50° and 85°, preferably between 60° and 85°.

[0095] As shown in FIGS. 3 and 8, within each channel of the first set of channels 401, the internal interface 238 between each collection structure 230 and fin structure 210 is inclined with respect to the longitudinal fin direction FD and also with respect 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°. FIGS. 3 and 6 disclose designs in which the angle β is between 95° and 130°, preferably between 95° and 120°. FIG. 8 discloses a design in which the angle β is between 50° and 85°, preferably between 60° and 85°.

[0096] On the opposite side of the plate 107, within each channel of the second set of channels 402, the internal interface 228 between each distribution structure 220 and fin structure 210 is inclined with respect to the longitudinally extending fin direction FD and also with respect 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°.

[0097] 3 and 6 disclose designs in which the angle β on the opposite side is also between 95° and 130°, preferably between 95° and 120°. That is, in the designs of FIGS. 3 and 6, the internal interface 228 on the side shown in the figures and the internal interface on the opposite side have similar slopes. FIGS. 7 and 8 disclose designs in which the angle β on the side shown in the figures is between 50° and 85°, preferably between 60° and 85°, and the angle β is between 95° and 130°, preferably between 95° and 120°. That is, in the designs of FIGS. 7 and 8, the internal interface 228 on the side shown in the figures and the internal interface 228 on the opposite side have opposite slopes.

[0098] The above discussion regarding the orientation of the opposing internal interface 228 is equally applicable to the opposing internal interface 238 .

[0099] As shown in Figures 3 and 6-8, each of the internal interfaces 228, 238 preferably extends along a substantially straight line.

[0100] In the embodiment shown in FIGS. 3 and 6-8, the internal interface 228 of the first inlet port 201 and the internal interface 238 of 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 of the second inlet port 202 and the internal interface 238 of the second outlet port 212 are also inclined in the same direction relative to the transverse direction TD. As noted above, this "same direction" refers to the direction of the internal interfaces 228, 238 of the same channel, which may be on opposite sides of the plate 107 or may be different. In a preferred embodiment, the angle β is also the same for the two internal interfaces 228, 238 of the second channel 402.

[0101] For example, as shown in FIGS. 3 and 5, the first fin structure 210a in the first channel of the first channel set 401 includes a first portion 210a1 and a second portion 210a2. The first and second portions 210a1-2 are alternately arranged along the fin direction FD. Thus, an interface is formed between the first and second portions 210a1-2 by the laterally extending side or edge of the first portion 210a1 being directly opposite the laterally extending side or edge of the second portion 210a2. This interface may be referred to as a central interface. In this regard, it should be noted that the word "central" is a label that facilitates distinction from other interfaces, and that a word used as a label may also be, for example, a "third interface." The laterally extending side or edge portions are arranged parallel to each other. The interface extends across the fin direction. The laterally extending side of each of the first and second portions 210a1-2 extends at an angle γ with respect to the fin direction. In a preferred embodiment, the laterally extending sides or edges of each of the first and second portions 210a1-2 extend at 90° relative to the fin direction. The interface is located at a first position P1 along the fin direction. The interface is located by selecting the dimensions of the first and second portions 210a1-2. Note that the edges of each of the first and second portions 210a1-2 of the first fin structure 210a may alternatively extend at an angle γ relative to the fin direction FD, with the angle γ being between 95 and 130°, preferably between 95 and 120°. The interface may be formed from abutting edges, and the interface may include a gap.

[0102] For example, as shown in FIG. 5 , the second fin structure 210b in the first channel of the second set of channels 402 includes first and second portions 210b1-2. The first and second portions 210b1-2 are alternately arranged along the fin direction. Thus, an interface is formed between the first and second portions 210b1-2 by the laterally extending side or edge of the first portion 210b1 being diametrically opposed to the laterally extending side or edge of the second portion 210b2. The laterally extending sides or edges are arranged parallel to each other. The interface extends across the fin direction. The laterally extending side or edge of each of the first and second portions 210b1-2 extends at an angle γ with respect to the fin direction FD. In a preferred embodiment, the laterally extending side of each of the first and second portions 210b1-2 extends at a 90° angle with respect to the fin direction. The interface is located at a second position P2 along the fin direction. The interface is located by selecting the dimensions of the first and second portions 210b1-2. It should be noted that the edges of each of the first and second portions 210b1-2 of the second fin structure 210b may alternatively extend at an angle γ relative to the fin direction FD, the angle γ being between 95 and 130°, preferably between 95 and 120°. The interface may be formed from edges abutting each other, and the interface may include a gap.

[0103] 5 illustrates the stack 105 of heat exchanger plates and the stack of the first set 401 and the second set 402 of channels. The first and second interface locations P1, P2 are spaced apart from each other by a distance DP along the fin direction. The distance DP between the first and second locations P1, P2 is such that any longitudinal gap G1 at the central interface 239a between the first and second portions 210a1-2 in the first channels of the first set 401 of channels does not overlap with the centerline of any longitudinal gap G2 at the central interface 239b between the first and second portions 210b1-2 in the first channels of the second set 402 of channels, and vice versa.

[0104] Preferably, any gaps between the first and second portions 210a1-2 in the first channels of the first set of channels 401 do not overlap with any gaps between the first and second portions 210b1-2 in the first channels of the second set of channels 402. In FIG. 4 , the dimensions of the first and second portions 210a1-2 in the first channels of the first set of channels 401 are selected so that the gaps therebetween do not overlap with the gaps between the first and second portions 210b1-2 in the first channels of the second set of channels 402. Note that fin structures 210 that are not adjacent fin structures 210 may have portions 210a1-2, 210b1-2 having identical dimensions. That is, gaps may overlap with each other as long as the gaps are not formed on opposite sides of the same heat exchanger plate.

[0105] Those skilled in the art will understand 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. Moreover, variations to the disclosed embodiments can be understood and effected by those skilled in the art in practicing the claimed invention, from a study of the drawings, the disclosure, and the appended claims. [Explanation of symbols]

[0106] 100 heat exchanger 101 First Entrance 102 Second Entrance 105 Heat exchanger plate stack 107 Heat Exchanger Plate 109 End Plate 111 Exit 1 112 Second Exit 121 Edge 122 Edge 201 First inlet port 202 Second Inlet Port 210 fin structure 210a first fin structure 210a1 First part 210a2 Second part 210b second fin structure 210b1 First part 210b2 Second part 211 First Exit Port 212 Second Exit Port 220 Distribution structure 223 First corner 224 Second Corner 225 Gap 227 port interface 228 Internal interface 230 Set structure 233 First corner 234 Second Corner 235 Gap 237 Port Interface 238 Internal interface 239a Central interface 239b Central interface 401 First set of channels 402 Second set of channels 415 Contact Line DP Distance FD fin direction G1 Longitudinal Gap G2 longitudinal gap LES1 first longitudinally extending side LES2 second longitudinally extending side P1 First position of the interface P2 Second position of the interface SD stacking direction TD Lateral

Claims

1. a stack (105) of heat exchanger plates stacked one above the other along a stacking direction (SD); a first set of channels (401) formed in all first and second gaps between the heat exchanger plates (107); a second set of channels (402) formed in every second gap between the heat exchanger plates (107); A heat exchanger (100) comprising: In each of the channels within the first and second sets of channels (401, 402), a fin structure (210) formed from a sheet folded back and forth is positioned between the heat exchanger plates (107) so that each fin structure (210) abuts the heat exchanger plate (107) along a plurality of contact lines (415) having main extensions extending parallel to a longitudinal fin direction (FD), thereby defining a plurality of fluid channels forming the first and second sets of channels (401, 402); Each heat exchanger plate (107) has four through openings (201, 202, 211, 212), the four through openings (201, 202, 211, 212) are formed at respective corners of the respective heat exchanger plate (107), and 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), and a second outlet port (212) extending through the stack (105) along the stacking direction (SD). configured to form a second inlet port (202) extending through the stack (105) and a second outlet port (212) extending through the stack (105) along the stacking direction (SD), wherein the first inlet port (201) and the first outlet port (211) are fluidly connected to each other via the first set of channels (401), and the second inlet port (202) and the second outlet port (212) are fluidly connected to each other via the second set of channels (402); the heat exchanger (100) further comprises, in each gap between the heat exchanger plates (107), a distribution structure (220) at each of the inlet ports (201, 202) and a collection structure (230) at each of the outlet ports (211, 212); each of the distribution structures (220) and each of the collection structures (230) is positioned between each of the ports (201, 202, 211, 212) and each of the fin structures (210) within each of the first and second sets of channels (401, 402); a port interface (227) between each of the inlet ports (201, 202) and each of the distribution structures (220), and a port interface (237) between each of the outlet ports (211, 212) and each of the collection structures (230), each inclined with respect to the fin direction (FD), such that, when measured along the fin direction (FD), the distance between the port interface (227, 237) and the fin structure (210) increases with increasing distance from an edge (121, 122) of each of the heat exchanger plates (107) that is closest to the respective port (201, 202, 211, 212) and extends along the longitudinally extending fin direction (FD), when viewed along an imaginary line extending transversely of the fin direction (FD).

2. 2. The heat exchanger (100) of claim 1, wherein each port interface forms an angle α with the fin direction (FD), the angle α being between 110° and 160°, preferably between 120° and 150°.

3. The heat exchanger (100) of claim 1 or 2, wherein each of the port interfaces extends substantially along a straight line.

4. 4. A heat exchanger (100) according to claim 1, wherein each of the distribution structures (220) and / or each of the collecting structures (230) extends from a first lateral central corner (223, 233) of each of the ports (201, 202, 211, 212) towards a second lateral outer corner (224, 234) of each of the ports (201, 202, 211, 212), leaving a lateral extending gap (225, 235) at the longitudinally extending edge (121, 122) closest to each of the ports (201, 202, 211, 212).

5. a majority of the flow from each of the inlet ports (201, 202) is distributed to the fin structure (210) via the distribution structure (220), and a majority of the flow from the fin structure (210) is collected to each of the outlet ports (211, 212) via the collecting structure (230); 5. The heat exchanger (100) of claim 4, wherein a small portion of the flow from each of the inlet ports (201, 202) is transferred to the fin structure (210) through the gap (235), and a small portion of the flow from the fin structure (210) is transferred to each of the outlet ports (211, 212) through the gap (235).

6. 6. A heat exchanger (100) according to claim 4 or 5, wherein the cuts in each of the heat exchanger plates (107) forming each of the ports (201, 202, 211, 212) are arc-shaped along at least most of the lateral extension of the gaps (225, 235).

7. 7. The heat exchanger (100) of any one of claims 1 to 6, wherein the distribution structure (220) is formed by an essentially triangular or truncated triangular fin structure.

8. 8. The heat exchanger (100) of any one of claims 1 to 7, wherein the collection structure (230) is formed by an essentially triangular or truncated triangular fin structure.

9. The heat exchanger (100) of any one of claims 1 to 8, wherein each of the ports (201, 202, 211, 212) is formed as a substantially triangular port.

10. 10. The heat exchanger (100) of any one of claims 1 to 9, wherein the first inlet and outlet ports (201, 211) have dimensions different from the second inlet and outlet ports (202, 212).

11. 8. A heat exchanger (100) according to any one of claims 1 to 7, wherein in each channel of the first set of channels (401) and / or in each channel of the second set of channels (402), the internal interface (228) between each of the distribution structures (220) and the fin structure (210) and / or the internal interface (238) between each of the collecting structures (230) and the fin structure (210) is inclined with respect to a longitudinal fin direction (FD) and also with respect to a transverse direction (TD).

12. 12. The heat exchanger (100) of claim 11, wherein each of the internal interfaces (228, 238) forms an angle β with the fin direction (FD), the angle β being between 95° and 130°, preferably between 95° and 120°, or between 50° and 85°, preferably between 60° and 85°.

13. 13. The heat exchanger (100) of claim 11 or 12, wherein each of the internal interfaces (228, 238) extends substantially along a straight line.

14. the first inlet port (201) is arranged on a first longitudinally extending side (LES1) of the stack of heat exchanger plates (105), the first outlet port (211) is arranged on a second longitudinally extending side (LES2) of the stack of heat exchanger plates (105), the second longitudinally extending side (LES2) being opposite the first longitudinally extending side (LES1); 11. The heat exchanger (100) according to claim 1, wherein the second inlet port (202) is arranged on the first longitudinally extending side (LES1) of the stack of heat exchanger plates (105) and the second outlet port (212) is arranged on the second longitudinally extending side (LES2) of the stack of heat exchanger plates (105), the first longitudinally extending side (LES1) being opposite the second longitudinally extending side (LES2).

15. In a first channel of the first set of channels (401), a first fin structure (210a) comprises at least first and second portions (210a1-2) alternately arranged along the fin direction (FD); In a first channel of the second set of channels (402), the first channel of the second set of channels (402) is a channel adjacent to the first channel of the first set of channels (401), and a second fin structure (210b) comprises at least first and second portions (210b1-2) alternately arranged along the fin direction (FD); a central interface (239a) between the first and second portions (210a1-2) of the first fin structure (210a) extends across the fin direction (FD) and is positioned at a first position (P1) along the fin direction (FD); a central interface (239b) between the first and second portions (210b1-2) of the second fin structure (210b) extends in the fin direction (FD) and is located at a second position (P2) along the fin direction (FD); 14. The heat exchanger (100) of any one of claims 1 to 13, wherein the first and second locations (P1, P2) are spaced apart from each other by a longitudinal distance (DP).

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