Channel heat exchanger

Abstract

A plurality of first flow channels and a plurality of second flow channels adjacent to the plurality of first flow channels are provided for exchanging heat energy between a first flow passing through the plurality of first flow channels and a second flow passing through the plurality of second flow channels; a parallel flow region wherein the flow paths and directions of the first flow channels of the plurality of first flow channels and the adjacent flow paths and directions of the second flow channels of the plurality of second flow channels are arranged in a partially or tangentially parallel relationship relative to each other in at least a portion of the parallel flow region and are fluidly separated from each other by wall portions; wherein the cross-section of the wall portions of the parallel flow region orthogonal to the local flow path directions of the parallel flow region is a grid pattern.

Description

Technical Field

[0001] The present invention relates to a heat exchanger for exchanging heat energy between a first flow and a second flow of fluid passing through the heat exchanger. Background Technology

[0002] Channel-type heat exchangers are known.

[0003] EP0720720B1 describes a first typical example of a known channel heat exchanger having a flow channel with a substantially rectangular cross-section.

[0004] A second typical example of a known channel heat exchanger is described in EP0666973B1, which has a flow channel with a substantially triangular cross-section.

[0005] This known channel-type heat exchanger provides satisfactory heat exchange performance, namely, a relatively high amount of heat transfer per unit time between a first flow consisting of a first fluid and a second flow consisting of a second fluid, and relatively low pressure drops along the first and second flows within such a heat exchanger.

[0006] However, there is still room for improvement in this type of channel heat exchanger. Summary of the Invention

[0007] The object of this invention is to provide a novel channel heat exchanger with improved heat exchange performance compared to known channel heat exchangers of the above type.

[0008] Specifically, one object of the present invention is to provide a novel channel heat exchanger that has a significantly increased heat transfer rate per unit time, while the pressure drop along the first and second flows is substantially not increased or increases negligibly.

[0009] This invention provides a heat exchanger comprising:

[0010] A plurality of first flow channels and a plurality of second flow channels adjacent to the plurality of first flow channels are used to exchange heat energy between a first flow of a first fluid passing through the plurality of first flow channels and a second flow of a second fluid passing through the plurality of second flow channels.

[0011] Parallel flow region, wherein the first-order flow paths and directions of a plurality of first flow channels and the adjacent flow paths and directions of a plurality of second flow channels are arranged in a partially or tangentially parallel relationship relative to each other in at least a portion of the parallel flow region and are fluidly separated from each other by wall portions;

[0012] The cross-section of the wall portion of the parallel flow region, orthogonal to the local flow path direction of the parallel flow region, is a grid pattern. The grid pattern includes a first set of m lines spaced apart from each other and a second set of n lines spaced apart from each other. The first set of m lines and the second set of n lines define multiple intersection points and boundary line segments between two intersection points. Each boundary line segment is part of the boundary line of the cross-section of the flow channel that defines multiple first flow channels and multiple second flow channels. At least some or all of the boundary line segments are continuous lines with positive and negative slope portions relative to an imaginary straight line between two intersection points.

[0013] Therefore, due to these positive and negative slope portions, the total length of the boundary line defining the cross-section of the flow channel increases relative to a boundary line consisting only of straight lines between the corner points of the cross-section defining a triangle or rectangle. Similarly, according to the invention, the total surface area of ​​the wall portion defining the flow channel increases relative to a flow channel defined only by the planar surface region between the corners of the flow channel. Thus, improved heat exchange performance is achieved.

[0014] The wall portion is typically a membrane, for example, these membranes may have water vapor transport properties.

[0015] The heat exchanger according to the invention can be manufactured using additive manufacturing for constructing the entire heat exchanger block in a layer-by-layer manner.

[0016] Alternatively, the heat exchanger according to the invention can be produced by first extruding multiple heat exchanger plates, i.e., shaped plates (e.g., membranes) with suitable profiles, and then stacking these heat exchanger plates to form a stack of heat exchanger plates that constitute a heat exchanger. In some embodiments, adjacent plates in the stack are sealed by welding or gluing the contact areas between adjacent plates. Alternatively, each plate may have multiple first-type structures and multiple second-type structures complementary to the first type. For example, such structures may include protrusions, linear protrusions or ridges preferably parallel to the flow path, and corresponding linear recesses or grooves parallel to the flow path. Thus, when these heat exchanger plates are stacked, the first-type and second-type structures will engage, making it easier for the plates to be stacked securely in a defined manner and also improving the seal between adjacent plates and adjacent flow paths, regardless of whether welding or gluing is used.

[0017] Some types of heat exchanger plate geometries do not require the extrusion of the heat exchanger plates to be stacked, and are instead suited to thermoforming / vacuum forming as an alternative plate forming method. These thermoformed / vacuum-formed heat exchanger plates are then stacked in a manner similar to that described in the previous paragraph.

[0018] In some embodiments, the boundary line segment may be planar symmetrical with respect to a plane of symmetry parallel to the direction of the local flow path, or point symmetrical with respect to the center point of the corresponding boundary line between two intersection points.

[0019] In some embodiments, the boundary line segment is a line in which at least a portion is curved. The curvature of the curved portion may be dome-shaped.

[0020] In some embodiments, the boundary line segment is a line having portions of positive curvature (e.g., a left turn) and portions of negative curvature (e.g., a right turn relative to an imaginary straight line between two intersection points). The combined curvature of these curved portions can be at least partially or entirely V-shaped or U-shaped in a cross-section orthogonal to the direction of the local flow path. Alternatively, the boundary line segment can have a bell-shaped curve in a cross-section orthogonal to the direction of the local flow path.

[0021] In some embodiments, a boundary line segment is a line having at least one inflection point. It should be understood that an inflection point refers to a boundary line segment in a cross-section orthogonal to the direction of the local flow path.

[0022] In other words, the boundary segment includes at least one curvature portion with a left turn and one curvature portion with a right turn. The combined curvature of these curved portions can have a bell shape, i.e., the two left-turning portions and the right-turning portion have two inflection points in between. Alternatively, the combined curvature of these curved portions can have a wavy shape, i.e., the left-turning portion and the right-turning portion have one inflection point.

[0023] In some embodiments, the boundary line segment is a line in which at least a portion or only a portion is straight. In some embodiments, the boundary line segment may have a V-shape or a Z-shape in a cross-section orthogonal to the direction of the local flow path.

[0024] In some embodiments, the boundary line segment has at least one intersection point, a so-called "zero point," which has an imaginary straight line between the two intersection points. Thus, a first surface of the pipe wall portion has concave (respectively recessed) portions adjacent to the convex (respectively projecting) portions, and a corresponding second surface of the pipe wall portion has complementary shapes of convex (respectively projecting) portions adjacent to the concave (respectively recessed) portions. The combination of these portions can be wavy or serrated, correspondingly zigzag.

[0025] In some embodiments, the boundary line segments are lines with only one inflection point. Therefore, they may each have a wavy shape, correspondingly a sine curve shape.

[0026] In some embodiments, the boundary line segments are lines with only two inflection points. They may have bell-shaped indentations or protrusions. Typically, the first surface of the pipe wall portion has concave (respectively recessed) portions, and the corresponding second surface of the pipe wall portion has complementary convex (respectively protruding) portions.

[0027] In some embodiments, within a parallel flow region, the flow paths of a plurality of first flow channels and the adjacent flow paths of a plurality of second flow channels are arranged in a partially or tangentially parallel relationship relative to each other in at least a major portion (i.e., at least more than 50%) of the parallel flow region.

[0028] Therefore, most of the flow paths within this parallel flow region, which typically contributes to the majority of the total heat exchange between the first and second flows, maintain good thermal contact with each other. A small portion of the parallel flow region may include local bends and offsets within the flow paths defined by the first and second flow paths.

[0029] In some embodiments, the angle at the intersection point is between 60° and 90°, and its complementary angle is between 120° and 90°. Therefore, there are no interior angles less than 60° in the flow channel. This prevents dead zones in corners, where fluid tends to flow more slowly and / or minimizes the thickness of the boundary layer with stagnant fluid particles, both of which lead to reduced heat exchange between the first and second fluids. Clearly, the angle refers to the angle between the first set of lines and the second set of lines at the intersection point.

[0030] In some embodiments, the angle at the intersection point is between 85° and 90° and its complementary angle is between 95° and 90°.

[0031] In some embodiments, the intersection angle and its complementary intersection angle at the intersection point are 90°.

[0032] In some embodiments, one of the multiple intersections defines a corner of the flow channel profiles of the multiple first flow channels and the multiple second flow channels.

[0033] In some embodiments, one of the multiple intersections defines the inner corners of four adjacent flow channels among the multiple first flow channels and the multiple second flow channels.

[0034] In some embodiments, four adjacent intersections of a plurality of intersections define the four interior angles of the flow channels of a plurality of first flow channels and a plurality of second flow channels, and four boundary line segments collectively define the four wall portions of the flow channels of the plurality of first flow channels and the plurality of second flow channels. In other words, each of the four boundary lines defines a wall portion of the flow channel.

[0035] In some embodiments, these four adjacent intersections define the corner points of the imaginary parallelogram.

[0036] Therefore, the increase in the length of the two sheared imaginary boundary lines of the parallelogram, compared to the length of the two unsheared imaginary boundary lines of the corresponding rectangle before shearing, contributes to an increase in the total length of the flow channel cross-section defined by the boundary lines. As mentioned earlier, this increase is complementary to and independent of the increase achieved by the positive and negative slope portions. Therefore, the total length of the flow channel cross-section defined by the parallelogram boundary lines increases relative to the rectangular boundary lines formed solely by orthogonal lines between the corner points of the cross-section. Similarly, as described above, the total surface area of ​​the wall portion defining the flow channel increases relative to the flow channel defined solely by the planar surface area between the corners of the flow channel. Thus, even greater improvements in heat exchange performance are achieved.

[0037] As mentioned above, heat exchanger plates for this parallelogram geometry can be manufactured at least by extruding irregularly shaped plates.

[0038] In some embodiments, four adjacent intersection points define the corner points of the imaginary rectangle.

[0039] This rectangular geometry of heat exchanger plate can be manufactured at least by profiled plate extrusion or thermoforming / vacuum forming.

[0040] In some embodiments, at least two opposing wall portions have boundary line segments of the same shape. Therefore, the increase in surface area due to the opposing wall portions of the flow channel does not affect the surface area of ​​the cross-section of the flow channel.

[0041] In some embodiments, the first pair of opposing wall portions have boundary line segments with positive and negative slope portions relative to an imaginary straight line between the two intersection points, and the second pair of opposing wall portions have straight boundary line segments.

[0042] Specifically, the first pair of opposing wall portions may have curved boundary line segments and the second pair of opposing wall portions may have straight boundary line segments.

[0043] This type of heat exchanger plate geometry can be manufactured at least by extrusion of shaped plates or thermoforming / vacuum forming. Of course, it is also possible to extrude shaped plates and additively manufacture the entire stack of plates.

[0044] In some embodiments, a first pair of opposing wall portions have boundary line segments having a positive slope portion and a negative slope portion relative to a straight line between two intersection points at the beginning and end of each boundary line segment, and a second pair of opposing wall portions have boundary line segments having a positive slope portion and a negative slope portion relative to a straight line between two intersection points at the beginning and end of each boundary line segment.

[0045] Specifically, the first pair of opposing wall portions have curved boundary line segments and the second pair of opposing wall portions have curved boundary line segments.

[0046] This type of heat exchanger plate geometry can be manufactured at least by extruding irregularly shaped plates. Of course, it can also be additively manufactured from an entire stack of plates.

[0047] In some embodiments, the heat exchanger according to the invention further includes a first cross-flow region, wherein adjacent flow passages of a plurality of first flow paths and a plurality of second flow paths are arranged in a cross relationship relative to each other, the first cross-flow region having a first opening region including an open end of a first flow path and a second opening region including an open end of a second flow path; and a second cross-flow region, wherein adjacent flow passages of a plurality of first flow paths and a plurality of second flow paths are arranged in a cross relationship relative to each other, the second cross-flow region having a first opening region including an opposite open end of a second flow path and a second opening region including an opposite open end of a first flow path; the first cross-flow region, the parallel flow region and the second cross-flow region are arranged in series along the first flow path and along the second flow path, wherein the parallel flow region is fluidly located between the first cross-flow region and the second cross-flow region along the first flow path and along the second flow path.

[0048] At least some or each of the plurality of first flow channels and plurality of second flow channels may have a constant cross-section along its entire length through the parallel flow region.

[0049] Alternatively, at least some of the multiple first flow channels and multiple second flow channels have varying cross-sections along their entire length through the parallel flow region.

[0050] In some embodiments, the wall portion defining the flow conduit and the adjacent flow conduit comprises a polymer material.

[0051] In some embodiments, the wall portion includes a sheet-like support portion with voids and a polymer that allows selective water vapor permeability.

[0052] In some embodiments, the sheet-like support portion with gaps includes at least one layer of woven or nonwoven material, porous material, and perforated material.

[0053] In some embodiments, the voids are filled with a polymer that allows selective water vapor permeability.

[0054] Alternatively, or additionally, the porous sheet-like support portion may be covered with a membrane of a polymer that allows selective water vapor permeability. Attached Figure Description

[0055] The invention described herein will be more fully understood from the detailed description and accompanying drawings given below, and should not be construed as limiting the invention described in the appended claims. The accompanying drawings show:

[0056] Figure 1 This is a cross-sectional view of a first heat exchanger element of a heat exchanger according to an embodiment of the present invention;

[0057] Figure 2 It is based on Figure 1 The heat exchanger in the embodiment and Figure 1 A cross-sectional view of the second heat exchanger element adjacent to the first heat exchanger element;

[0058] Figure 3 This is a cross-sectional view of a section orthogonal to the local flow path direction of the parallel flow region along the wall portion of the parallel flow region of a heat exchanger, according to another embodiment of the present invention.

[0059] Figure 4 This is a cross-sectional view of a section orthogonal to the local flow path direction of the parallel flow region along the wall portion of the parallel flow region of a heat exchanger, according to another embodiment of the present invention.

[0060] Figure 5 This is a cross-sectional view of a section orthogonal to the local flow path direction of the parallel flow region along the wall portion of the parallel flow region of a heat exchanger, according to another embodiment of the present invention.

[0061] Figure 6 This is a cross-sectional view of a section orthogonal to the local flow path direction of the parallel flow region along the wall portion of the parallel flow region of a heat exchanger, according to another embodiment of the present invention.

[0062] Figure 7 This is a cross-sectional view of a section orthogonal to the local flow path direction of the parallel flow region along the wall portion of the parallel flow region of a heat exchanger, according to another embodiment of the present invention.

[0063] Figure 8 This is a cross-sectional view of a section orthogonal to the local flow path direction of the parallel flow region along the wall portion of the parallel flow region of a heat exchanger, according to another embodiment of the present invention.

[0064] Figure 9 This is a cross-sectional view of a section orthogonal to the local flow path direction of the parallel flow region along the wall portion of the parallel flow region of a heat exchanger, according to another embodiment of the present invention.

[0065] Figure 10 This is a cross-sectional view of a section orthogonal to the local flow path direction of the parallel flow region along the wall portion of the parallel flow region of a heat exchanger, according to another embodiment of the present invention.

[0066] Figure 11 This is a perspective view of a heat exchanger according to another embodiment of the present invention;

[0067] Figure 12 yes Figure 11 The diagram shows a cross-sectional view of the heat exchanger. Detailed Implementation

[0068] Figure 1 and Figure 2 A cross-section of a heat exchanger according to the present invention is shown. Figure 1 A view of a first heat exchanger element is shown. This heat exchanger element has a first cross-flow region CF1, wherein the flow passages of the first flow F1 in a plurality of first flow paths are angled relative to the first flow passages in the parallel flow region PF, i.e., an angle between 5° and 85°. Similarly, a second cross-flow region CF2 of the heat exchanger has a plurality of first flow paths of the first flow F1, which are angled relative to the first flow passages in the parallel flow region PF, i.e., an angle between 5° and 85°. Figure 2 It shows the relationship with Figure 1 The first heat exchanger element is directly adjacent to the second heat exchanger element. In the heat exchanger according to the invention, such first and second heat exchanger elements are stacked in series in an alternating manner. It can be seen that the second heat exchanger element defines a second flow path for the second flow F2. This heat exchanger element also has a first cross-flow region CF1, wherein the flow paths of the plurality of first flow paths of the second flow F2 are angled relative to the first flow paths in the parallel flow region PF, i.e., an angle between 5° and 85°. Similarly, the second cross-flow region CF2 of the heat exchanger has a plurality of first flow paths of the second flow F2, which are angled relative to the first flow paths in the parallel flow region PF, i.e., an angle between 5° and 85°. The second heat exchanger element is mirror-symmetric to the first heat exchanger element. Therefore, when they are stacked in an alternating manner, the first flow F1 and the second flow F2 flow parallel or in completely opposite directions in the parallel flow region PF and they cross each other in the first cross-flow region CF1 and the second cross-flow region CF2.

[0069] Figure 3A heat exchanger is shown having a plurality of first flow channels for a first flow F1 and a plurality of second flow channels adjacent to the plurality of first flow channels for a second flow F2, for exchanging heat energy between the first flow F1 passing through the first flow channels and the second flow F2 passing through the plurality of second flow channels.

[0070] In the parallel flow region PF of the heat exchanger, the flow paths and directions of the first flow F1 of the plurality of first flow pipes and the adjacent flow paths and directions of the second flow F2 of the plurality of second flow pipes are arranged relative to each other in a partially or tangentially parallel relationship at least in a part of the parallel flow region or in the fully parallel flow region and are fluidly separated from each other by wall portions WP1, WP2, WP3, WP4.

[0071] The cross-section of the wall portion of the parallel flow region PF in a cross-sectional plane orthogonal to the local flow path direction of the parallel flow region PF is a grid pattern. In other words, in the parallel flow region, there are different units arranged in a grid or matrix manner along this cross-section. The grid pattern in this cross-section includes a first set of m lines E1, E2, E3, and E4 spaced apart from each other and a second set of n lines G1, G2, G3, and G4 spaced apart from each other. It should be understood that the term "line" applies to this cross-section, which is a cross-sectional view, and in such a heat exchanger, these lines define the wall portion and therefore extend in at least two or even three spatial dimensions.

[0072] The first group of m lines and the second group of n lines define multiple intersection points PX between each other. That is, at this point, the first group of lines and the second group of lines intersect each other in the cross-section of the wall portion of the parallel flow region PF in a cross-sectional plane orthogonal to the local flow path direction of the parallel flow region PF.

[0073] Furthermore, the first set of m lines and the second set of n lines define the boundary line segment BLS between the two intersection points PX. Each boundary line segment BLS1, BLS2, BLS3, and BLS4 is part of the boundary line of a cross section CS of a flow channel that defines a plurality of first flow channels and a plurality of second flow channels.

[0074] At least some boundary line segments BLS1, BLS2, BLS3, and BLS4 are continuous lines with a positive slope portion PS and a negative slope portion NS relative to an imaginary straight line between two intersection points PX. These boundary line segments define the shape of the wall portion of each flow channel, which is the cross-sectional shape. In the illustrated embodiment, only the boundary line segments defined by the first set of lines E1, E2, E3, and E4 each have such a positive slope, while the second set of lines are straight lines between the corresponding two intersection points. In a cross-section orthogonal to the direction of the local flow path parallel to the flow region, the first set of m lines E1, E2, E3, and E4 and the corresponding boundary line segments are substantially V-shaped, wherein a portion of the boundary line segment is straight, i.e., has a slope of 0, which is the portion parallel to the imaginary straight line between the intersection points.

[0075] Typically, the first flow channel used for the first flow F1 is always adjacent to the second flow channel used for the second flow F2, and vice versa.

[0076] from Figure 3 It can be seen that the first group of m lines E1 to E4 all have the same shape and extend parallel to each other at any given position. The same applies to all lines in the second group of n lines G1 to G4. This can be applied to this embodiment and all other embodiments described herein and is used to distinguish the first group of lines from the second group of lines. Furthermore, none of the first group of m lines E1 to E4 intersects. Conversely, none of the second group of n lines G1 to G4 intersects. This can be applied to this embodiment and all other embodiments described herein and is used to distinguish the first group of lines from the second group of lines.

[0077] Figure 3 The angle AX, defined by the first set of lines E2 and the second set of lines G1 at their intersection, is further shown. The complementary angle CAX is also shown.

[0078] Figure 4 Another embodiment of the heat exchanger according to the present invention is shown. Figure 3 Conversely, the cross-sections of the wall portion of the parallel flow region PF, which are orthogonal to the local flow path direction of the parallel flow region, have different shapes. When the shapes of the second set of lines G1 to G4 are... Figure 3The shapes of the first set of lines E1 to G4 are different, but they still define boundary line segments that are continuous lines with a positive slope portion PS and a negative slope portion NS relative to the straight line between the two intersection points PX. However, in this embodiment, a portion of the line is curved. When the first portion of each boundary line segment defined by the first set of lines G1 to G4 forms a left curve, the second portion forms a right curve. It can be seen that the boundary line segments defined by the first set of lines G1 to G4 are symmetrical with respect to the plane of symmetry perpendicular to the cross-section shown (i.e., the plane extending along the direction of the local flow path).

[0079] Figure 5 Another embodiment of the invention is shown. (Compared to...) Figure 3 Conversely, the cross-sections of the wall portion of the parallel flow region PF, which are orthogonal to the local flow path direction of the parallel flow region, have different shapes. Although the shapes of the second set of lines G1 to G4 are similar to... Figure 3 The shapes of the first set of lines E1 to E4 are different, though they are the same. They still define boundary line segments that are continuous lines with a positive slope portion PS and a negative slope portion NS relative to the straight line between the two intersection points PX, but in this embodiment, a portion of the line is curved. Furthermore, each boundary segment defined by the first set of lines includes two inflection points, resulting in a bell-shaped curve.

[0080] Figure 6 Another embodiment of the heat exchanger according to the present invention is shown. Figure 3 Conversely, the cross-sections of the wall portion of the parallel flow region PF, which are orthogonal to the local flow path direction of the parallel flow region, have different shapes. Although the shapes of the second set of lines G1 to G4 are similar to... Figure 3 The shapes of the first group of lines, E1 to E4, are different, though they are the same. They still define boundary line segments that are continuous lines with a positive slope portion PS and a negative slope portion NS relative to the straight line between the two intersection points PX, but in this embodiment, a portion of the line is curved. However, compared to... Figure 4 Conversely, each boundary line segment defined by the first set of lines E1 to E4 forms only a right curve.

[0081] Figure 7 Another embodiment of the heat exchanger according to the present invention is shown. Figures 3 to 6The illustrated embodiment, conversely, not only do the first set of lines E1 to E4 define boundary line segments that are continuous lines with a positive slope portion PS and a negative slope portion NS relative to the straight line between the two intersection points PX, but the second set of lines G1 to G5 also do so. This results in the fact that the wall portions WP1 to WP4 of each flow channel are inclined (i.e., not straight). In this particular embodiment, the boundary line segments defined by the first set of lines E1 to E4 and the boundary line segments defined by the second set of lines G1 to G5 are zigzag-shaped. Furthermore, each of these boundary line segments has at least one intersection point PX0 with the straight line between the two intersection points (see, for example, the hypothetical straight line L1 or L2).

[0082] Figure 8 Another embodiment of the heat exchanger according to the present invention is shown. Figure 3 Conversely, the cross-sections of the wall portion of the parallel flow region PF, which are orthogonal to the local flow path direction of the parallel flow region, have different shapes. Although the shapes of the second set of lines G1 to G4 are similar to... Figure 3 The shapes of the first set of lines E1 to E4 are different, though they are the same. They still define boundary line segments that are continuous lines with a positive slope portion PS and a negative slope portion NS relative to a straight line between two intersection points PX. However, in this embodiment, a portion of the line is curved only within a portion (particularly the middle portion) of each boundary line segment defined by the first set of lines E1 to E4. Within each of these boundary line segments, the curved portion is arranged between two straight portions. Thus, the curved portion forms a convex (i.e., protruding) portion of the first surface of the wall portion WP3 in the corresponding flow channel for the second flow F2, while simultaneously forming a concave (i.e., recessed) portion of the second surface of the wall portion in the corresponding flow channel for the first flow F1.

[0083] Figure 9 Another embodiment of the heat exchanger according to the present invention is shown. Figure 3 The illustrated embodiment differs in that not only do the first set of lines E1 to E4 define boundary line segments that are continuous lines with a positive slope portion PS and a negative slope portion NS relative to the straight line between the two intersection points PX, but the second set of lines G1 to G5 also do the same. The shapes of the boundary line segments defined by the first set of lines E1 to E4 and the shapes of the second set of lines G1 to G5 are similar to... Figure 3 The boundary line segments defined by the first set of lines E1 to E4 have the same shape.

[0084] Figure 10 It shows something similar to Figure 9In this embodiment, not only do the first set of lines E1 to E4 define boundary line segments that are continuous lines with a positive slope portion PS and a negative slope portion NS relative to the straight line between the two intersection points PX, but the second set of lines G1 to G5 are also like this. However, compared with Figure 9 Conversely, each boundary line segment defined by the first set of lines and also by the second set of lines is curved and wavy, resembling a sine curve. Each boundary line segment includes only a single inflection point. In this particular embodiment, the inflection point is also a single point in each boundary line segment where the boundary line segment intersects the straight line between the two corresponding intersection points (see, for example, line L1 or line L2).

[0085] Figure 11 A perspective view of a partially cut-out heat exchanger is shown.

[0086] Figure 12 It shows Figure 11 A cross-sectional view of the parallel flow region PF of the heat exchanger.

[0087] List of reference numerals

[0088] FD1 First Flow Pipe

[0089] FD2 Second Flow Pipe

[0090] F1 First Class

[0091] F2 Second Stream

[0092] PF parallel flow region

[0093] CF1 First Cross Flow Region

[0094] CF2 Second Cross Flow Region

[0095] WP1 wall section

[0096] WP2 wall section

[0097] WP3 wall section

[0098] WP4 wall section

[0099] E1...Em are the first set of lines spaced apart from each other.

[0100] G1...Gn are the second set of lines spaced apart from each other.

[0101] EF grid pattern

[0102] PX intersection

[0103] PI1 inflection point

[0104] PI2 inflection point

[0105] BLS1 boundary section

[0106] BLS2 boundary section

[0107] BLS3 boundary section

[0108] BLS4 boundary section

[0109] CS flow pipe cross section

[0110] The positive slope portion of the PS boundary line segment

[0111] The negative slope portion of the NS boundary section

[0112] The intersection of PX0 and the straight line between the intersection points.

[0113] AX angle

[0114] CAX complementary angles

Claims

1. A heat exchanger comprising: A plurality of first flow channels (FD1) and a plurality of second flow channels (FD2) adjacent to the plurality of first flow channels are provided for exchanging heat energy between a first flow (F1) passing through the plurality of first flow channels (FD1) and a second flow (F2) passing through the plurality of second flow channels (FD2); Parallel flow region (PF), wherein the flow path and direction of the first flow (F1) of the plurality of first flow channels (FD1) are arranged in a partially or tangentially parallel relationship with the adjacent flow path and direction of the second flow (F2) of the plurality of second flow channels (FD2) at least in a portion of the parallel flow region and are fluidly separated from each other by wall portions (WP1, WP2, WP3, WP4). The cross-section of the wall portion of the parallel flow region (PF) orthogonal to the local flow path direction of the parallel flow region (PF) is a grid pattern (EF). The grid pattern (EF) includes a first set of m lines (E1, E2...Em) spaced apart from each other and a second set of n lines (G1, G2...Gn) spaced apart from each other. The first set of m lines and the second set of n lines define a plurality of intersection points (PX) and boundary line segments (BLS) between two intersection points (PX). Each boundary line segment (BLS1, BLS2, BLS3, BLS4) is part of the boundary line of the cross-section (CS) of the flow channels (FD1, FD2) that define the plurality of first flow channels (FD1) and the plurality of second flow channels (FD2). At least some of the boundary line segments (BLS1, BLS2, BLS3, BLS4) are continuous lines with a positive slope portion (PS) and a negative slope portion (NS) relative to the straight line between the two intersection points (PX), wherein at least two opposing wall portions have boundary line segments (BLS1, BLS3 and / or BLS2, BLS4) of the same shape.

2. The heat exchanger according to claim 1, wherein the boundary line segment (BLS) is a line in which at least a portion of the line is curved.

3. The heat exchanger according to claim 2, wherein the boundary line segment (BLS) is a line having a portion with positive curvature and a portion with negative curvature.

4. The heat exchanger according to claim 3, wherein the boundary line segment (BLS) is a line having at least one inflection point (PI1, PI2).

5. The heat exchanger according to claim 1, wherein the boundary line segment (BLS) is a line in which at least a portion of the line is straight.

6. The heat exchanger according to claim 1, wherein the straight line between the boundary line segment (BLS) and the two intersection points (PX) has at least one intersection point (PX0).

7. The heat exchanger according to any one of claims 4 to 6, wherein the boundary line segment (BLS) is a line having only one inflection point (PI1).

8. The heat exchanger according to any one of claims 4 to 6, wherein the boundary line segment (BLS) is a line having only two inflection points (PI1, PI2).

9. The heat exchanger according to any one of claims 1 to 6, wherein within the parallel flow region (PF), the flow passages of the plurality of first flow channels (FD1) and the adjacent flow passages of the plurality of second flow channels (FD2) are arranged in a partially or tangentially parallel relationship relative to each other, at least in the main portion of the parallel flow region.

10. The heat exchanger according to any one of claims 1 to 6, wherein the angle (AX) at the intersection point (PX) is between 60° and 90°, and its complementary angle (CAX) is between 120° and 90°.

11. The heat exchanger of claim 10, wherein the angle (AX) at the intersection (PX) is between 85° and 90°, and its complementary angle (CAX) is between 95° and 90°.

12. The heat exchanger according to claim 11, wherein the angle (AX) at the intersection (PX) and its complementary angle (CAX) are 90°.

13. The heat exchanger according to any one of claims 1 to 6, wherein one of the plurality of intersections (PX) defines a corner of the flow channel (FD1, FD2) profiles of the plurality of first flow channels (FD1) and the plurality of second flow channels (FD2).

14. The heat exchanger according to any one of claims 1 to 6, wherein one of the plurality of intersections (PX) defines the corners of four adjacent flow channels (FD1, FD2) of the plurality of first flow channels (FD1) and the plurality of second flow channels (FD2).

15. The heat exchanger according to any one of claims 1 to 6, wherein four adjacent intersections (PX) of the plurality of intersections define four corners of the flow channels (FD1, FD2) of the plurality of first flow channels (FD1) and the plurality of second flow channels (FD2), and four boundary line segments (BLS1, BLS2, BLS3, BLS4) define four wall portions of the flow channels (FD1, FD2) of the plurality of first flow channels (FD1) and the plurality of second flow channels (FD2).

16. The heat exchanger according to any one of claims 1 to 6, wherein the first pair of opposing wall portions (WP1, WP3) have boundary line segments (BLS1, BLS3) with a positive slope portion (PS) and a negative slope portion (NS) relative to the straight line between the two intersection points (PX), and the second pair of opposing wall portions (WP2, WP4) have straight boundary line segments (BLS2, BLS4).

17. The heat exchanger of claim 16, wherein the first pair of opposing wall portions (WP1, WP3) have curved boundary line segments (BLS1, BLS3) and the second pair of opposing wall portions (WP2, WP4) have straight boundary line segments (BLS2, BLS4).

18. The heat exchanger according to any one of claims 1 to 6, wherein a first pair of opposing wall portions (WP1, WP3) have boundary line segments (BLS1, BLS3) having a positive slope portion (PS) and a negative slope portion (NS) relative to the straight line between the two intersection points (PX) at the beginning and end of each of the boundary line segments, and wherein a second pair of opposing wall portions (WP2, WP4) have boundary line segments (BLS2, BLS4) having a positive slope portion (PS) and a negative slope portion (NS) relative to the straight line between the two intersection points (PX) at the beginning and end of each of the boundary line segments.

19. The heat exchanger of claim 18, wherein the first pair of opposing wall portions (WP1, WP3) have curved boundary line sections (BLS1, BLS3), and the second pair of opposing wall portions (WP2, WP4) have curved boundary line sections (BLS2, BLS4).

20. The heat exchanger according to any one of claims 1 to 6, further comprising a first cross-flow region (CF1), in which flow passages of a plurality of first flow paths (FP1) are arranged in a cross relationship with adjacent flow passages of a plurality of second flow paths (FP2) relative to each other, the first cross-flow region (CF1) having a first opening region including the opening ends of the first flow paths (FP1) and a second opening region including the opening ends of the second flow paths (FP2); and The second cross flow region (CF2) is in which the flow paths of the plurality of first flow paths (FP1) and the adjacent flow paths of the plurality of second flow paths (FP2) are arranged in a cross relationship relative to each other. The second cross flow region (CF2) has a first opening region including the opposite opening end of the second flow path (FP2) and a second opening region including the opposite opening end of the first flow path (FP1). The first cross-flow region (CF1), the parallel flow region (PF), and the second cross-flow region (CF2) are arranged in series along the first flow path (FP1) and the second flow path (FP2), wherein the parallel flow region (PF) is fluidly located between the first cross-flow region (CF1) and the second cross-flow region (CF2) along the first flow path (FP1) and the second flow path (FP2).

21. The heat exchanger according to any one of claims 1 to 6, wherein at least some of the plurality of first flow channels (FD1) and the plurality of second flow channels (FD2), or each flow channel, has a constant or varying cross-section along its entire length through the parallel flow region (PF).

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