Heat transfer plate and cassette

Abstract

The present invention provides a heat transfer plate (8, 8a, 8b, 8c) and a cartridge (57). The heat transfer plate (8, 8a, 8b, 8c) includes an upper portion (26) having one of a first interface hole and a second interface hole (40, 42), a central portion (28) having a heat transfer area (46), and a lower portion (30) having a third interface hole and a fourth interface hole (48, 50). In addition, the heat transfer plate (8, 8a, 8b, 8c) further includes a sealing groove (64), the sealing groove including a sealing groove portion (64a) that surrounds the heat transfer area (46) and two of the first interface hole, the second interface hole, the third interface hole, and the fourth interface hole (40, 42, 48, 50). The heat transfer plate (8, 8a, 8b, 8c) further includes a gasket groove (68), which includes a gasket groove portion (68a) that encloses the heat transfer area (46) and the two of the first interface hole, the second interface hole, the third interface hole, and the fourth interface hole (40, 42, 48, 50) that are not enclosed by the field sealing groove portion (64a). The heat transfer plate (8, 8a, 8b, 8c) is characterized in that the first interface hole (40) and the third interface hole (48) are non-circular, and the second interface hole (42) and the fourth interface hole (50) are circular.

Description

Technical Field

[0001] The present invention relates to a heat transfer plate and a cartridge comprising two such heat transfer plates. Prior Technology

[0002] A plate heat exchanger (PHE) typically comprises two end plates, between which multiple heat transfer plates are arranged in a stacked or encapsulated configuration. The heat transfer plates of a PHE can be of the same or different types and can be stacked in different ways. In some PHEs, the heat transfer plates are stacked such that the front and rear sides of one heat transfer plate face the rear and front sides of other heat transfer plates, respectively, and every other heat transfer plate is inverted relative to the remaining heat transfer plates. This is typically referred to as the heat transfer plates being "rotated" relative to each other. In other PHEs, the heat transfer plates are stacked such that the front and rear sides of one heat transfer plate face the front and rear sides of other heat transfer plates, respectively, and every other heat transfer plate is inverted relative to the remaining heat transfer plates. This is typically referred to as the heat transfer plates being "flipped" relative to each other.

[0003] In a well-known type of PHE (so-called semi-welded PHE), heat transfer plates are typically "flipped" relative to each other and welded in pairs to form tight-fitting cartridges, with gaskets disposed between the cartridges. End plates and thus cartridges are pressed against each other by several fastening members, thereby sealing the cartridges with gaskets. Parallel flow channels are formed between the heat transfer plates, with one channel between each pair of adjacent heat transfer plates. Two fluids, initially fed to / from the PHE at different temperatures via inlets / outlets using a pump-like device, can alternately flow through every other channel to transfer heat from one fluid to the other. These fluids enter / exit the channels through inlet / outlet interface holes in the heat transfer plates, which form inlet / outlet ports communicating with the inlet / outlet of the PHE.

[0004] Therefore, in a semi-welded PHE, there are channels defined by welds and channels defined by gaskets, which typically extend along the outer edge of the heat transfer plate and the inlet / outlet interface holes. Typically, channels defined by welds can and should better withstand much higher pressures than channels defined by gaskets.

[0005] WO2009 / 082336 discloses a PHE comprising heat transfer plates permanently joined in pairs by means of welds to form cartridges, and gaskets sealing between the cartridges, i.e., a semi-welded heat exchanger. Even if this heat exchanger is functioning well, there is still room for improvement.

[0006] WO01 / 67021 discloses a heat transfer plate comprising a heat transfer portion, a sealing portion, and a port. The heat transfer plate has a line of symmetry, and the heat transfer portion, the sealing portion, and the port are symmetrically arranged about the line of symmetry.

[0007] WO03 / 006911 discloses a heat transfer plate comprising a first port portion having at least two ports and a second port portion having at least two ports. The ports within the first port portion are positioned along a first line parallel to the longitudinal direction of the plate. Additionally, the ports within the second port portion are positioned along a second line parallel to the longitudinal direction of the plate.

[0008] FR2967248 relates to a heat exchanger comprising a stack of plates defining end chambers containing channel members. Summary of the Invention

[0009] The objective of this invention is to provide a heat transfer plate that improves upon prior art heat exchangers. The basic concept of this invention is to provide a heat transfer plate with two interface holes, these two interface holes having an off-circular shape; in other words, two non-circular interface holes. This increases the flexibility of the heat transfer plate and allows it to be optimized for different environments. Another objective of this invention is to provide a cartridge comprising two such heat transfer plates. The heat transfer plate (also referred to herein simply as a "plate") and the cartridge are defined in the appended claims and discussed below.

[0010] The heat transfer plate according to the present invention comprises an upper portion, a central portion, and a lower portion arranged sequentially along the longitudinal central axis of the heat transfer plate. The longitudinal central axis is perpendicular to the transverse central axis of the heat transfer plate. The upper portion includes a first interface hole and a second interface hole, and the lower portion includes a third interface hole and a fourth interface hole. The central portion includes a heat transfer area having a heat transfer corrugated pattern, which includes ridges and valleys as seen from a first side of the heat transfer plate. The ridges and valleys extend in and between an imaginary parallel first plane and a second plane. The first side of the heat transfer plate faces the first plane, and the opposite second side of the heat transfer plate faces the second plane. As seen from the first side, the heat transfer plate further includes a sealing groove. The sealing groove includes a field sealing groove portion that encloses the heat transfer area and two of the first interface hole, the second interface hole, the third interface hole, and the fourth interface hole. As seen from the first side, the heat transfer plate further includes a gasket groove. The gasket groove includes the field gasket groove portion that encloses the heat transfer area and the portion of the first, second, third, and fourth interface holes that is not enclosed by the field sealing groove portion. The heat transfer plate is characterized in that the first and third interface holes are non-circular, while the second and fourth interface holes are circular.

[0011] The first and third interface holes can be identical, in other words, have the same shape. The first and third interface holes can also be the same size. Similarly, the second and fourth interface holes can be identical, in other words, have the same shape. Furthermore, the second and fourth interface holes can also be the same size.

[0012] The field sealing groove and the field gasket groove can at least partially overlap.

[0013] Regarding the mechanical strength of heat transfer plates, circular orifices are typically advantageous compared to non-circular orifices. However, regarding other characteristics of heat transfer plates, such as thermal performance, including pressure drop and flow distribution across the plate, non-circular orifices can be advantageous compared to circular orifices. By designing the orifices of heat transfer plates differently, and more specifically, having two circular orifices and two non-circular orifices, heat transfer plates, and therefore cartridges or heat exchangers comprising one or more of these heat transfer plates, can be optimized for certain applications in terms of mechanical strength and other characteristics.

[0014] Typically, the circular second and fourth interface holes are dedicated to the same fluid, while the non-circular first and third interface holes are dedicated to the same different fluid. Just as with the non-circular interface holes, the circular interface holes can be configured on opposite sides of the longitudinal central axis of the heat transfer plate. This arrangement of interface holes enables so-called oblique flow heat transfer plates and heat exchangers comprising heat transfer plates according to the invention that are "rotated" relative to each other. However, such heat exchangers may require two different designs of heat transfer plates. Alternatively, the first and third interface holes are configured on one side of the longitudinal central axis of the heat transfer plate, while the second and fourth interface holes are configured on the other side. This arrangement of interface holes enables so-called parallel flow heat transfer plates and heat exchangers comprising heat transfer plates according to the invention that are "flipped" relative to each other.

[0015] A heat transfer plate can be configured to permanently join another heat transfer plate along a sealing groove (e.g., via a weld extending within the sealing groove) to form a cartridge. The heat transfer plates can be configured such that the field sealing groove portion of the sealing groove encloses circular second and fourth interface holes. This configuration means that the interface holes specifically for the fluid configured to flow within the cartridge are circular. This is advantageous because, as previously mentioned, circular interface holes are optimal from a mechanical strength point of view, and the channels within the cartridge are better suited to withstand relatively high pressures.

[0016] In the configuration described above, the field gasket groove portion of the gasket groove can enclose the first and third interface holes, the gasket groove being configured to accommodate a gasket for sealing against another heat transfer plate. This design means that the interface holes specifically designed for fluids flowing outside the cartridge are non-circular. This is advantageous because, as previously mentioned, non-circular interface holes are optimal in terms of characteristics other than mechanical strength (e.g., thermal efficiency), and the passageway outside the cartridge should preferably withstand relatively low pressure.

[0017] The heat transfer plate is designed such that the bottom of the field sealing groove extends in a second plane for at least half the length of the field sealing groove. This design facilitates permanent bonding between the heat transfer plate and another heat transfer plate.

[0018] The heat transfer plate allows the sealing groove, as seen from a first side of the heat transfer plate, to further include a first annular sealing groove portion enclosing a first interface hole and a third annular sealing groove portion enclosing a third interface hole. The bottom of the first annular sealing groove portion may extend in a second plane for at least half the length of the first annular sealing groove portion. Additionally, the bottom of the third annular sealing groove portion may extend in a second plane for at least half the length of the third annular sealing groove portion. This design facilitates permanent bonding between the heat transfer plate and another heat transfer plate.

[0019] The heat transfer plate can be configured such that, as seen from the first side of the heat transfer plate, the gasket groove further includes a second annular gasket groove portion enclosing the second interface hole and a fourth annular gasket groove portion enclosing the fourth interface hole. The bottom of the second annular gasket groove portion may extend between the first plane and the second plane for at least half the length of the second annular gasket groove portion. The bottom of the fourth annular gasket groove portion may extend between the first plane and the second plane for at least half the length of the fourth annular gasket groove portion. This design enables fluid flow between the second interface hole and the fourth interface hole on the second side of the heat transfer plate.

[0020] The heat transfer plate can be designed such that each of the first and third interface holes has only one axis of symmetry. This facilitates a relatively mechanically simple construction of the plate heat exchanger incorporating the heat transfer plate.

[0021] As mentioned above, equipment such as pumps is required to feed the two fluids through the plate heat exchanger. The smaller the inlet and outlet ports of the heat exchanger, the greater the pressure drop of the fluids inside the PHE, and the greater the power of the equipment required for normal operation of the PHE, and therefore the higher the price. Naturally, the diameters of the inlet and outlet ports can be made larger to reduce the pressure drop of the fluids and to allow the use of less powerful equipment. However, increasing the diameter of the inlet and outlet ports means increasing the diameter of the interface holes in the heat transfer plates of the heat exchanger. Consequently, this can lead to the sacrifice of valuable heat transfer surface area of ​​the heat transfer plates, which is typically associated with a reduction in the heat transfer efficiency of the plate heat exchanger.

[0022] The heat transfer plate allows a first interface hole to be disposed within a portion of the heat transfer plate defined by a first short side, a first long side, a longitudinal central axis, and a transverse central axis, wherein the reference point of the first interface hole coincides with the center point of the largest imaginary circle that can be fitted into the first interface hole. The first interface hole can have different forms. However, according to a specific embodiment of the invention, the form of the first interface hole is defined by a plurality of corner points of an imaginary planar geometry and an equal number of curves, at least one of which is displaced from a circular arc, and the curves do not have straight sections and connect the corner points. A first corner point is configured to be closest to the transition between the first short side and the first long side and is a first distance from the reference point. A second corner point is configured to be closest to the first corner point in a clockwise direction and is a second distance from the reference point. A third corner point is configured to be closest to the first corner point in a counterclockwise direction and is a third distance from the reference point.

[0023] Plane geometric figures can have many different types, such as triangles, quadrilaterals, pentagons, and so on. Therefore, the number of corners or endpoints, and thus the number of curves, can be greater than two.

[0024] A completely curved line means a line without any straight sections. Therefore, the first interface hole will have a profile without any straight sections. This is advantageous because it will result in relatively low bending stress around the interface hole. The fluid flowing through the interface hole attempts to bend the first interface hole into a circle. Therefore, if the interface hole had straight sections, relatively high bending stress would be generated in the heat transfer plate.

[0025] The curves connect the two points at the corners.

[0026] Since at least one of the corner points is displaced from the arc of the imaginary circle, the first interface hole will be non-circular.

[0027] The features of the second and third corner points being closest to the first corner point in the clockwise and counterclockwise directions, respectively, indicate the relative positioning of the first, second, and third corner points along the contour of the first interface hole.

[0028] The first, second, and third distances between the reference point and the first, second, and third corner points are discussed separately; these are the shortest distances within the field of view.

[0029] The first interface hole form described above can be made suitable for the design of the rest of the heat transfer plate and larger than the second and fourth interface holes by sacrificing the surface of the heat transfer plate that does not significantly contribute to the heat transfer efficiency of the heat transfer plate.

[0030] The heat transfer plate allows the first interface hole to have only one axis of symmetry extending through the first corner point and the reference point. This facilitates a relatively mechanically simple construction of the plate heat exchanger incorporating the heat transfer plate.

[0031] According to a specific embodiment of the heat transfer plate of the present invention, the number of corner points and curves is equal to three. Correspondingly, the corresponding planar geometry can be a triangle. This specific embodiment is applicable to many conventional heat transfer plates having a basic rectangular shape and interface holes arranged at the corners of the heat transfer plate.

[0032] As can be seen from the reference point of the first interface hole, the curve can be concave or convex outwards. This type of design achieves a relatively large interface hole area associated with a relatively low voltage drop.

[0033] According to the present invention, the first distance between the first corner point and the reference point may be smaller than the second distance between the second corner point and the reference point and / or the third distance between the third corner point and the reference point. Therefore, the shape of the interface hole can be adapted to the design of the rest of the heat transfer plate. More specifically, depending on the heat transfer plate design, displacing the second and third corner points can provide more space to increase the interface hole area compared to displacing the first corner point.

[0034] The heat transfer plate can be designed such that the first and third interface holes are of the same size, and the second and fourth interface holes are of the same size. Additionally, like the second and fourth interface holes, the first and third interface holes can have the same shape. Furthermore, the first and third interface holes can be symmetrical with respect to the transverse central axis, and / or the second and fourth interface holes can be symmetrical with respect to the transverse central axis.

[0035] Having interface holes of similar shape and / or size (such as symmetrical interface hole pairs) enables the alignment of interface holes in a stack of heat transfer plates containing multiple heat transfer plates of the same type that are "rotated" or "flipped" relative to each other.

[0036] The heat transfer plate is constructed such that two of the first, second, third, and fourth interface holes, which are enclosed by the field sealing groove portion, are disposed outside the field gasket groove portion. Additionally, the two of the first, second, third, and fourth interface holes enclosed by the field gasket groove portion can be disposed outside the field sealing groove portion. This facilitates the formation of two separate flow paths for two fluids configured to be fed through a plate heat exchanger comprising the heat transfer plate according to the invention.

[0037] The heat transfer plate can be divided into a first part, a second part, a third part, and a fourth part by a longitudinal central axis and a transverse central axis. A first interface hole can be configured within the first part, a second interface hole within the second part, a third interface hole within the third part, and a fourth interface hole within the fourth part. Therefore, the longitudinal central axis can extend completely (i.e., only) outside the first, second, third, and fourth interface holes. This configuration allows the interface holes to be positioned close to the periphery of the heat transfer plate, which is advantageous.

[0038] The cartridge according to the invention comprises the two heat transfer plates described above. A second side of one of the heat transfer plates faces a second side of the other heat transfer plate, and the other heat transfer plate is rotated 180 degrees about its normal. In other words, one of the heat transfer plates is rotated 180 degrees about its transverse central axis. The two heat transfer plates are welded to each other along a sealing groove.

[0039] The heat exchanger may include a plurality of aligned cartridges as described above. The heat exchanger may further include gaskets disposed in gasket grooves between every two adjacent cartridges.

[0040] The advantages discussed above for different specific examples of heat transfer plates can be naturally transferred to the cartridge according to the present invention.

[0041] As a general note, in this document, when a portion, part, section, etc., of a heat transfer plate is said to extend in a plane, it is the main extension of the aforementioned portion, part, section, etc. Naturally, a portion, part, section, etc., may, for example, have an extension that deviates from the main extension at the transition to another adjacent portion, part, section, etc.

[0042] It should be emphasized that the advantages discussed above regarding the various specific examples of the heat transfer plate according to the invention first become apparent when the heat transfer plate is configured in a PHE together with other heat transfer plates (which may also be designed according to the invention), gaskets, and other components required for a properly functional PHE.

[0043] Other objects, features, forms and advantages of the present invention will be described in detail below and presented in the figures. Simple Explanation of the Diagram

[0044] The invention will now be described in more detail with reference to the accompanying schematic drawings, in which... [Figure 1] is a schematic front view of the heat exchanger according to the present invention. [Figure 2] is a schematic side view of the heat exchanger in Figure 1. [Figure 3] is a plan view of the heat transfer plate according to the present invention. [Figure 4] is a schematic side view of a portion of the plate assembly included in the heat exchanger shown in Figure 1. [Figure 5] is a plan view of the cartridge according to the present invention, and [Figure 6] is a schematic diagram of the height of a portion of the heat transfer plate in Figure 3. Implementation

[0045] Figures 1 and 2 show a semi-welded plate heat exchanger 2 described in an introductory manner. It includes a frame plate 4, a pressure plate 6, a stack of heat transfer plates 8, a fluid inlet and outlet 10, fastening members 12, an upper rod 14, and a lower rod 16.

[0046] At least most of the heat transfer plates 8 (hereinafter also referred to as "plates") are similar. One of the heat transfer plates (designated 8a) is shown in further detail in Figure 3. Plate 8a is a generally rectangular stainless steel sheet. It includes a first relatively long side 18 and a second relatively long side 20, as well as a first relatively short side 22 and a second relatively short side 24. In addition, plate 8a has a longitudinal central axis L and a transverse central axis T, the longitudinal central axis being parallel to the long sides 18 and 20 and extending in the middle between the long sides 18 and 20, and the transverse central axis being parallel to the short sides 22 and 24 and extending in the middle between the short sides 22 and 24, and therefore perpendicular to the longitudinal central axis L. The longitudinal central axis L and the transverse central axis T divide the heat transfer plate 8a into a first part 1, a second part 3, a third part 5, and a fourth part 7.

[0047] Plate 8a has a first side 30 (shown in Figures 3 and 4) and an opposite second side 32 (shown in Figure 4). Furthermore, plate 8a includes an upper portion 34, a central portion 36, and a lower portion 38 arranged sequentially along the longitudinal central axis L of the heat transfer plate 8a. The upper portion 34 includes a first interface hole 40, a second interface hole 42, a first insulation region 39, a second insulation region 41, and an upper distribution region 44. The central portion 36 includes a heat transfer region 46. The lower portion 38 includes a third interface hole 48, a fourth interface hole 50, a third insulation region 49, a fourth insulation region 51, and a lower distribution region 52. The first interface hole 40 and the second interface hole 42 are respectively disposed within the first portion 1 and the second portion 3 of the heat transfer plate 8a. The third interface hole 48 and the fourth interface hole 50 are respectively disposed within the third portion 5 and the fourth portion 7 of the heat transfer plate 8a. Therefore, the first interface hole 40 and the third interface hole 48 are completely disposed on one side of the longitudinal central axis L, while the second interface hole 42 and the fourth interface hole 50 are completely disposed on the other side of the longitudinal central axis L.

[0048] The heat transfer plate 8a is pressed into a pressing tool in a conventional manner to obtain its desired structure, such as different corrugated patterns in different parts of the heat transfer plate. The corrugated patterns are optimized for the specific function of each plate part. Therefore, the upper distribution area 44 and the lower distribution area 52 each contain a distribution corrugated pattern suitable for the optimized distribution of fluid across the heat transfer plate 8a. In addition, the heat transfer area 46 contains a heat transfer corrugated pattern suitable for the optimized heat transfer between two fluids flowing on opposite sides of the heat transfer plate 8a. Furthermore, the first insulating area 39, the second insulating area 41, the third insulating area 49, and the fourth insulating area 51 each contain a corrugated pattern optimized from an insulating point of view. In addition, the plate 8a includes an outer edge portion 54 extending along the outer edge 56 of the plate. The outer edge portion 54 contains corrugations 58 (FIG. 4) extending in and between an imaginary parallel first plane P1 and a second plane P2, wherein the first plane P1 and the second plane P2 face the first side 30 and the second side 32 of the plate 8a, respectively. These corrugations 58 are configured to abut the corrugations of adjacent plates 8b and 8c in the plate assembly of the plate heat exchanger 2. Similarly, referring to Figures 3 and 4, the heat transfer corrugation pattern includes corrugations, more specifically, as seen from the first side 30 of plate 8a, comprising alternating ridges 60 and valleys 62 extending in and between the first plane P1 and the second plane P2. These ridges 60 and valleys 62 are configured to abut the ridges and valleys of adjacent plates 8b and 8c in the plate assembly of the plate heat exchanger 2. The distribution corrugation pattern also includes corrugations configured to abut the corrugations of adjacent plates in the plate assembly of the plate heat exchanger 2. However, this will not be discussed further herein.

[0049] As seen from the first side 30 of the plate, the sealing groove 64 is also pressed into the plate 8a. This sealing groove includes a field sealing groove portion 64a, a first annular sealing groove portion 64b, and a third annular sealing groove portion 64c. The sealing groove 64 is shown in lines in FIG. 3. The field sealing groove portion 64a encloses the heat transfer area 46 and the second interface hole 42 and the fourth interface hole 50, but does not enclose the first interface hole 40 and the third interface hole 48. The bottom 66a of the field sealing groove portion 64a extends along the entire length of the field sealing groove portion 64a in the second plane P2 (FIG. 4). The first annular sealing groove portion 64b encloses the first interface hole 40. The bottom 66b of the first annular sealing groove portion 64b extends along the entire length of the first annular sealing groove portion 64b in the second plane P2. The third annular sealing groove portion 64c encloses the third interface hole 48. The bottom 66c of the third annular sealing groove portion 64c extends along the entire length of the third annular sealing groove portion 64c in the second plane P2.

[0050] Referring to Figures 3 and 5, as seen from the first side 30 of the plate, the gasket groove 68 is also pressed into the plate 8a to accommodate the gasket 59 (including the field gasket portion and the two ring gasket portions). The gasket groove 68 includes a field gasket groove portion 68a, a second ring gasket groove portion 68b, and a fourth ring gasket groove portion 68c. The field gasket groove portion 68a encloses the heat transfer area 46 and the first interface hole 40 and the third interface hole 48, but does not enclose the second interface hole 42 and the fourth interface hole 50. The field gasket groove portion 68a partially overlaps with the field sealing groove portion 64a. Therefore, the bottom 70a of the field gasket groove portion 68a extends in the second plane P2 (Figure 4), wherein the field gasket groove portion 68a overlaps with the field sealing groove portion 64a. In fact, the bottom 70a of the field washer groove portion 68a extends anywhere in the second plane P2 except at the two diagonal segments 68a' of the field washer groove portion 68a, and the bottom 70a extends along the two diagonal segments 68a' between the first plane P1 and the second plane P2 (in this case, the middle). The second ring washer groove portion 68b encloses the second interface hole 42. The bottom 70b of the second ring washer groove portion 68b extends along the entire length of the second ring washer groove portion 68b between the first plane P1 and the second plane P2 (in this case, the middle). The fourth ring washer groove portion 68c encloses the fourth interface hole 50. The bottom 70c of the fourth ring washer groove portion 68c extends along the entire length of the fourth ring washer groove portion 68c between the first plane P1 and the second plane P2 (in this case, the middle).

[0051] In the plate assembly of the plate heat exchanger 2, plates 8 are configured such that the first side 30 and the second side 32 of one plate 8 face the first side and the second side of the adjacent heat transfer plate, respectively. Furthermore, every other plate 8 is inverted or rotated 180 degrees relative to a reference orientation about a normal direction N, which is perpendicular to the plane of Figure 3. In other words, every other plate 8 is rotated 180 degrees about its transverse central axis. Figure 4 illustrates the contact between the corrugations 58 (Figure 3) of the outer edge portion 54 of plate 8a and two adjacent plates 8b and 8c in the plate assembly of the plate heat exchanger 2.

[0052] In the plate assembly, the plates 8 are welded together in pairs (second side 32 to second side 32) along their respective sealing grooves 64 to form a cartridge 57. Figure 5 shows one of the cartridges 57, which includes the plate 8a shown in Figure 3 and the plate 8c visible in Figure 4 (but not visible in Figure 5). In the plate assembly of the plate heat exchanger 2, the welded cartridges 57 are separated by gaskets 59, at least most of which are similar, one of which is shown in Figure 5. Consistent with the above, the gaskets 59 are received in the gasket grooves 68 of the plates 8, as shown in Figure 5. Therefore, the heat exchanger 2 includes two different types of channels: welded channels inside the cartridges 57 and gasketed channels between the cartridges 57.

[0053] In the following description, referring to Figures 3 and 6, the first interface hole 40 and the second interface hole 42 of the heat transfer plate 8a will be further described. The third interface hole 48 and the fourth interface hole 50 are mirror images of the first interface hole 40 and the second interface hole 42, respectively. Therefore, the first interface hole 40 and the third interface hole 48 have the same size and shape and are symmetrical with respect to the transverse central axis T. Similarly, the second interface hole 42 and the fourth interface hole 50 have the same size and shape and are symmetrical with respect to the transverse central axis T. Therefore, the third interface hole 48 and the fourth interface hole 50 will not be described separately.

[0054] The first interface hole 40 is disposed within the portion 72 (i.e., the first portion 1 of the heat transfer plate 8a) defined by the first long side 18, the first short side 22, the longitudinal central axis L, and the transverse central axis T, as mentioned above. The first interface hole 40 is schematically illustrated in Figure 6. It has a form defined by a first corner point 74, a second corner point 76, and a third corner point 78 of an imaginary planar geometric figure 80 in the form of a triangle (dashed line). Furthermore, these corner points 74, 76, and 78 are connected by a first fully curved line 82, a second fully curved line 84, and a third fully curved line 86, respectively, and these curves are concave as seen from within the first interface hole 40. The reference point 88 of the first interface hole 40 coincides with the center point C of the largest imaginary circle 90 (ghost line) that can be disposed within the first interface hole 40. The first corner point 74 is positioned closest to the transition portion 92 between the first short side 22 and the first long side 18 of the heat transfer plate 8a. Furthermore, the first corner point is positioned on a first imaginary straight line 94 extending from the reference point 88 and at a first distance d1 from the reference point 88. The second corner point 76 is positioned to be closest to the first corner point 74 in a clockwise direction. Furthermore, the second corner point is positioned on a second imaginary straight line 96 extending from the reference point 88 and at a second distance d2 from the reference point 88. The third corner point 78 is positioned to be closest to the first corner point 74 in a counterclockwise direction. Furthermore, the third corner point is positioned on a third imaginary straight line 98 extending from the reference point 88 and at a third distance d3 from the reference point 88.

[0055] For the aforementioned first distance d1, second distance d2, and third distance d3, the following relationship is valid: d2 = d3 and d2 > d1. Furthermore, the first angle α1 between the first imaginary line 94 and the second imaginary line 96 is less than the second angle α2 between the second imaginary line 96 and the third imaginary line 98, and is substantially equal to the third angle α3 between the second imaginary line 96 and the first imaginary line 94. In other words, for the first angle α1, the second angle α2, and the third angle α3, the following relationship is valid: α1 = α3 and α1 < α2. In this specific instance, α1 = α3 = 115 degrees. Moreover, the first curve 82 connecting the first corner point 74 and the second corner point 76 is substantially consistent with the third curve 86 connecting the third corner point 78 and the first corner point 74. In summary, this means that the first interface hole 40 is symmetrical about the axis of symmetry s extending through the first corner point 74 and the reference point 88.

[0056] As is evident from the above figures and description, the first interface hole 40 has a non-circular form. More specifically, it has a form defined by a plurality of corner points (three in this case) and the same number of curves (thus, three in this case) connecting these corner points, at least one of which (all in this case) is displaced from arc 100 of circle 90. If the first interface hole 40 were circular, it would preferably have a form corresponding to circle 90. From a pressure drop point of view, referring to the previous discussion in this regard, even a larger first interface hole 40 would be preferable. However, the design of the rest of the heat transfer plate 8a limits the possible size of the first interface hole 40. For example, a larger circular first interface hole 40 would mean that the profile of the first interface hole would be configured closer to the first short side 22 and / or the first long side 18, which could lead to strength problems for the heat transfer plate 8a. Additionally, referring to Figure 5, the larger circular first interface hole 40 also implies that the area between the first interface hole and the upper distribution area 44 can be so narrow that it causes problems when pressing a heat transfer plate with the aforementioned corrugated pattern. Naturally, the upper distribution area 44 of the heat transfer plate 8a can be further displaced downward on the heat transfer plate to create space for the larger first interface hole 40. However, this will typically be associated with a smaller heat transfer area 46, and therefore with a poorer heat transfer capability of the heat transfer plate.

[0057] As described above and illustrated in the figures, the area of ​​the first interface hole 40 can be increased without modifying the design of the rest of the heat transfer plate. By making the first interface hole 40 occupy more of the first insulating region 39 of the heat transfer plate 8a (Figure 3) than a circular first interface hole having a form corresponding to a circle 90, a larger first interface hole associated with a smaller pressure drop can be achieved. Since only the first insulating region 39 is affected by this enlargement, the distribution of the heat transfer plate 8a and the heat transfer capacity remain essentially unaffected. In addition, since the outline of the first interface hole 40 does not have a straight portion, the bending stress around the first interface hole will be relatively low.

[0058] It should be emphasized that the description corresponding to the above description is also valid for the third interface hole 48 of the heat transfer plate 8a.

[0059] The second interface hole 42 is disposed within another portion 102 of the heat transfer plate 8a (i.e., the second portion 3 of the heat transfer plate 8a) defined by the second long side 20, the first short side 22, the longitudinal central axis L, and the transverse central axis T, as mentioned above. The second interface hole 42 is circular. Therefore, the fourth interface hole 50 is also circular.

[0060] Because the heat transfer plate 8 of the heat exchanger 2 contains interface holes of different shapes, the ports of the heat exchanger will have different shapes. More specifically, the ports used to feed fluid into and out of the gasketed channel will have a "rounded triangular" cross-section, which is advantageous in terms of thermal efficiency, such as regarding pressure drop and flow distribution inside the gasketed channel. Additionally, the ports used to feed fluid into and out of the welding channel will have a circular cross-section, which is advantageous in terms of mechanical strength. Therefore, by designing a cartridge with a circular port on the welding side and a non-circular port on the gasketed side, the pressure on the welding side of the cartridge is maximized, and thermal optimization is achieved for the gasketed side.

[0061] The specific examples described above are to be considered merely as examples. Those skilled in the art will recognize that the specific examples discussed can be varied in several ways without departing from the inventive concept.

[0062] The heat transfer plate does not need to be rectangular, but can have other shapes, such as circular or elliptical. The heat transfer plate does not necessarily include two non-circular interface holes in the rounded triangular form described above, but can instead include two non-circular interface holes in another form. The corrugated patterns in the heat transfer area, distribution area, and insulation area do not need to be designed as shown in the diagram.

[0063] In the specific examples above, most of the plates and gaskets between the cartridges are similar, but this is not mandatory. As an example, two or more different types of plates can be combined in a plate assembly.

[0064] The bottom of the field washer groove portion does not necessarily extend in the middle between the first and second planes in the two diagonal sections of the field washer groove portion, but may instead extend closer to one of the first and second planes. Similarly, the bottom of the second ring washer groove portion (as is the bottom of the fourth ring washer groove portion) does not necessarily extend along its entire length in the middle between the first and second planes, but may instead extend along a portion of its length or its entire length in another plane (e.g., closer to the first plane than the second plane). It should be emphasized that the attributes such as front, back, top, bottom, first, second, and third are used herein only to distinguish details and do not indicate any kind of orientation or relative order between such details.

[0065] Furthermore, it should be emphasized that descriptions of details not related to the present invention have been omitted, and the drawings are schematic only and not drawn to scale. It should also be mentioned that some of the drawings are simplified compared to others. Therefore, some components may be shown in one drawing but omitted in another.

[0066] 1: Part One 2: Plate heat exchanger 3: Part Two 4: Frame board 5: Part Three 6: Pressure plate 7: Part Four 8: Heat transfer plate 8a: Heat transfer plate 8b: Heat transfer plate 8c: Heat transfer plate 10: Fluid inlet and outlet 12: Fastening components 14: Upper rod 16: Lower rod 18: First Long Side 20: Second Long Side 22: First short side 24: Second short side 30: First side 32: Second side 34: Upper part 36: Central Part 38: Lower part 39: First Insulation Zone 40: First interface hole 41: Second Insulation Zone 42: Second interface hole 44: Upper distribution area 46: Heat transfer zone 48: Third interface hole 49: Third Insulation Zone 50: Fourth interface hole 51: Fourth Adiabatic Zone 52: Lower distribution area 54: Outer edge portion 56: Outer edge 57: Cartridge 58: Ripples 59: Washer 60: Spine 62: Valley 64: Sealing groove 64a: Field sealing groove section 64b: First ring sealing groove section 64c: Third ring sealing groove section 66a: Bottom 66b: Bottom 66c: Bottom 68: Washer Groove 68a: Washer groove section 68a': Diagonal segment 68b: Second ring washer groove section 68c: Fourth ring washer groove section 70a: Bottom 70b: Bottom 70c: Bottom 72: Part 74: First Corner Point 76: Second corner point 78: Third Corner Point 80: Imaginary plane geometric figures 82: First Curve 84: Second Curve 86: Third Curve 88: Reference Point 90: Maximum Imaginary Circle 92: Transition Section 94: First Imaginary Straight Line 96: Second Imaginary Line 98: Third Imaginary Line 100: Arc 102: Part α1: First angle α2: Second angle α3: Third angle C: Center point d1: First distance d2: Second distance d3: Third distance L: Longitudinal central axis N: Normal direction P1: First plane P2: Second plane s: axis of symmetry T: Lateral central axis

Claims

1. A heat transfer plate (8, 8a, 8b, 8c) comprising an upper portion (34), a central portion (36), and a lower portion (38) sequentially arranged along a longitudinal central axis (L) of the heat transfer plate (8, 8a, 8b, 8c), the longitudinal central axis (L) being perpendicular to the transverse central axis (T) of the heat transfer plate (8, 8a, 8b, 8c), the upper portion (34) comprising a first interface hole (40) and a second interface hole (42), and the lower portion (38) comprising a third interface hole (43). 8) and the fourth interface hole (50), the central portion (36) includes a heat transfer area (46) having a heat transfer corrugation pattern, as seen from the first side (30) of the heat transfer plate (8, 8a, 8b, 8c), the heat transfer corrugation pattern including ridges (60) and valleys (62), the ridges (60) and the valleys (62) extending in and between an imaginary parallel first plane and a second plane (P1, P2), the first side (30) of the heat transfer plate (8, 8a, 8b, 8c) facing the first plane ( P1), and the opposite second side (32) of the heat transfer plate (8, 8a, 8b, 8c) faces the second plane (P2), as seen from the first side (30), the heat transfer plate (8, 8a, 8b, 8c) further includes a sealing groove (64), the sealing groove including a field sealing groove portion (64a) that encloses the heat transfer area (46) and two of the first interface hole, the second interface hole, the third interface hole and the fourth interface hole (40, 42, 48, 50), the heat transfer plate (8, 8a, 8b, 8c) 8b, 8c) further includes a gasket groove (68), which includes a field gasket groove portion (68a) that encloses the heat transfer area (46) and the two of the first interface hole, the second interface hole, the third interface hole and the fourth interface hole (40, 42, 48, 50) that are not enclosed by the field sealing groove portion (64a), characterized in that the first interface hole (40) and the third interface hole (48) are non-circular, and the second interface hole (42) and the fourth interface hole (50) are circular.

2. The heat transfer plate (8, 8a, 8b, 8c) of claim 1, wherein the first interface hole (40) and the third interface hole (48) are disposed on one side of the longitudinal central axis (L) of the heat transfer plate (8, 8a, 8b, 8c), and the second interface hole (42) and the fourth interface hole (50) are disposed on the other side of the longitudinal central axis (L) of the heat transfer plate (8, 8a, 8b, 8c).

3. The heat transfer plate (8, 8a, 8b, 8c) of request item 1 or 2, wherein the field sealing groove portion (64a) encloses the second interface hole (42) and the fourth interface hole (50).

4. The heat transfer plate (8, 8a, 8b, 8c) of claim 1 or 2, wherein the bottom (66a) of the field sealing groove portion (64a) extends in the second plane (P2) for at least half of the length of the field sealing groove portion (64a).

5. The heat transfer plate (8, 8a, 8b, 8c) of claim 1 or 2, wherein, as seen from the first side (30) of the heat transfer plate, the sealing groove (64) further comprises a first annular sealing groove portion (64b) enclosing the first interface hole (40) and a third annular sealing groove portion (64c) enclosing the third interface hole (48), wherein the bottom (66b) of the first annular sealing groove portion (64b) extends in the second plane (P2) for at least half of the length of the first annular sealing groove portion (64b), and the bottom (66c) of the third annular sealing groove portion (64c) extends in the second plane (P2) for at least half of the length of the third annular sealing groove portion (64c).

6. The heat transfer plate (8, 8a, 8b, 8c) of claim 1 or 2, wherein the gasket groove (68) further comprises a second annular gasket groove portion (68b) enclosing the second interface hole (42) and a fourth annular gasket groove portion (68c) enclosing the fourth interface hole (50), wherein the bottom (70b) of the second annular gasket groove portion (68b) extends between the first plane (P1) and the second plane (P2) for at least half of the length of the second annular gasket groove portion (68b), and the bottom (70c) of the fourth annular gasket groove portion (68c) extends between the first plane (P1) and the second plane (P2) for at least half of the length of the fourth annular gasket groove portion (68c).

7. The heat transfer plate (8, 8a, 8b, 8c) of request item 1 or 2, wherein the first interface hole (40) and the third interface hole (48) each have only one axis of symmetry (s).

8. The heat transfer plate (8, 8a, 8b, 8c) as requested in item 1 or 2, wherein the first interface hole (40) is disposed in the portion (72) of the heat transfer plate (8, 8a, 8b, 8c) defined by the first short side (22), the first long side (18), the longitudinal central axis (L), and the transverse central axis (T) of the heat transfer plate (8, 8a, 8b, 8c), and wherein the reference point (88) of the first interface hole (40) is aligned with the portion of the heat transfer plate (8, 8a, 8b, 8c) that can be fitted to the heat transfer plate (8, 8a, 8b, 8c). The center point (C) of the largest imaginary circle (90) in the first interface hole (40) coincides with the shape of the first interface hole (40) defined by a plurality of corner points (74, 76, 78) of an imaginary planar geometry (80), at least one of which is displaced from the arc (100) of the circle (90), and the same number of curves (82, 84, 86) which do not have a straight portion and connect the corner points (74, 76, 78). The first corner point (74) among the isoangular points (74, 76, 78) is configured to be closest to the transition (92) between the first short side (22) and the first long side (18) and is a first distance (d1) away from the reference point (88). The second corner point (76) among the isoangular points (74, 76, 78) is configured to be closest to the first corner point (74) in the clockwise direction and is a second distance (d2) away from the reference point (88). The third corner point (78) among the isoangular points (74, 76, 78) is configured to be closest to the first corner point (74) in the counterclockwise direction and is a third distance (d3) away from the reference point (88).

9. The heat transfer plate (8, 8a, 8b, 8c) of request item 1 or 2, wherein the first interface hole (40) and the third interface hole (48) are of the same size, and the second interface hole (42) and the fourth interface hole (50) are of the same size.

10. The heat transfer plate (8, 8a, 8b, 8c) of request item 1 or 2, wherein the first interface hole (40) and the third interface hole (48) have the same shape.

11. The heat transfer plate (8, 8a, 8b, 8c) of request item 1 or 2, wherein the first interface hole (40) and the third interface hole (48) are symmetrical with respect to the transverse central axis (T), and / or the second interface hole (42) and the fourth interface hole (50) are symmetrical with respect to the transverse central axis (T).

12. The heat transfer plate (8, 8a, 8b, 8c) of claim 1 or 2, wherein the first interface hole, the second interface hole, the third interface hole and the fourth interface hole (40, 42, 48, 50) enclosed by the field sealing groove portion (64a) are disposed outside the field gasket groove portion (68a), and wherein the first interface hole, the second interface hole, the third interface hole and the fourth interface hole (40, 42, 48, 50) enclosed by the field gasket groove portion (68a) are disposed outside the field sealing groove portion (64a).

13. The heat transfer plate (8, 8a, 8b, 8c) of request item 1 or 2, wherein the longitudinal central axis (L) and the transverse central axis (T) divide the heat transfer plate (8, 8a, 8b, 8c) into a first part, a second part, a third part and a fourth part (1, 3, 5, 7), wherein the first interface hole (40) is disposed in the first part (1), the second interface hole (42) is disposed in the second part (3), the third interface hole (48) is disposed in the third part (5) and the fourth interface hole (50) is disposed in the fourth part (7).

14. The heat transfer plate (8, 8a, 8b, 8c) of request item 1 or 2, wherein the longitudinal central axis (L) extends entirely outside the first interface hole, the second interface hole, the third interface hole and the fourth interface hole (40, 42, 48, 50).

15. A cartridge (57) comprising two heat transfer plates (8, 8a, 8b, 8c) as claimed in any one of claims 1 to 14, wherein a second side (32) of one of the two heat transfer plates (8, 8a, 8b, 8c) faces the second side (32) of the other of the two heat transfer plates (8, 8a, 8b, 8c), and the other of the two heat transfer plates (8, 8a, 8b, 8c) is rotated 180 degrees about the normal (N) of the other of the two heat transfer plates (8, 8a, 8b, 8c), wherein the two heat transfer plates (8, 8a, 8b, 8c) are welded to each other along the sealing groove (64).

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