Heat exchanger with two-piece through fitting

Abstract

A heat exchanger includes: a first plate and a second plate defining a fluid flow passage therebetween; a through-hole defining an inlet port and an outlet port; and a through fitting having a first section and a second section. Each section includes a tube portion extending through one of the through-holes and a flange portion located within the fluid flow passage. The flange portion of each section has opposing first and second surfaces, the first surfaces being fluid-tightly coupled to an inner surface of one of the plates. The second surfaces of the two sections face each other, and at least the second surfaces have one or more channels providing fluid flow from a hollow interior to the fluid flow passage. The second surfaces of these sections are in contact with each other or separated abuttingly, and the flange portions of the first and second sections provide support for the first and second plates in a region surrounding the port.

Description

Technical Field

[0001] The present invention relates to heat exchanger construction, and particularly to heat exchangers having through holes to allow heat transfer fluid to pass through the heat exchanger, and to thermal management systems including such heat exchangers. Background Technology

[0002] A thermal management system for a vehicle may include two or more heat exchangers connected in parallel to a common inlet and outlet manifold. In some configurations, each heat exchanger in the system may include a pair of through-holes serving as inlet and outlet ports, and as part of the inlet and outlet manifolds to distribute heat transfer fluid to other heat exchangers in the system. An example of such a heat exchanger configuration is shown in commonly assigned U.S. Patent No. 10006722. Figure 1 In the text, it is incorporated into the whole through citation.

[0003] US Patent No. 10,006,722 Figure 1 The heat exchanger shown has face seals on both sides of the heat exchanger surrounding through openings to form a sealed fluid connection with the inlet and outlet manifolds within the frame structure. Some configurations use tubular fittings instead of face seals to form the fluid connection. These fittings protrude at right angles from both sides of the heat exchanger and are securely attached to the outer surface of the heat exchanger. In cases where both the inlet and outlet ports of the heat exchanger include through openings, a total of four fittings are required: two at the inlet port and two at the outlet port.

[0004] In some heat exchanger structures, the area of ​​the fluid flow passage near each through-hole lacks internal support, and additional support elements may be required within the fluid flow passage to prevent plate deformation near the through-hole. Such support elements are also disclosed in U.S. Patent No. 10,006,722, mentioned above. Furthermore, when fittings are brazed to the uncovered outer surface of the plates constituting the heat exchanger, brazing filler metal rings may be required between the sealing surface of the fitting and the heat exchanger plate, thereby increasing the number of components required for the assembly.

[0005] An improved fitting construction is needed, including a heat exchanger with through holes. Summary of the Invention

[0006] According to one aspect of this disclosure, a heat exchanger is provided, comprising: (a) a first plate having an inner surface, an outer surface, and at least one first hole; (b) a second plate having an inner surface, an outer surface, and at least one second hole, wherein each of the at least one first hole is opposite and spaced apart from one of the second holes; (c) a fluid flow passage defined between the inner surfaces of the first plate and the second plate; and (d) at least one through fitting, wherein each through fitting comprises a first segment and a second segment, each segment having a first open end located outside the fluid flow passage, a second open end located inside the fluid flow passage, and a hollow interior.

[0007] According to one aspect, each segment includes a tube portion and a flange portion. The flange portion is located within a fluid flow passage, and the tube portion of each segment extends through one of a first or second hole to a first open end of the segment. The flange portion of each segment extends radially outward from the tube portion and engages with the tube portion. The flange portion has opposing first and second surfaces, wherein the first surface is continuous and sealingly engaged with the inner surface of one of a first plate and a second plate to provide a continuous seal between the segment and the first or second plate in the region surrounding the first or second hole.

[0008] According to one aspect, the second surface of the flange portion of the first segment and the second surface of the flange portion of the second segment are facing each other. The second surfaces of one or both of the first and second segments include one or more channels, each channel having a first open end and an opposing second open end, wherein the first open end is in flow communication with the hollow interior of the through fitting, and the second open end is in flow communication with a fluid flow passage.

[0009] According to one aspect, the fluid flow passage extends between an inlet port and an outlet port; and each of the inlet port and the outlet port is in the form of a through opening comprising a pair of opposing first and second orifices.

[0010] According to one aspect, the first and second sections of each through-fitting component are arranged concentrically with each other.

[0011] According to one aspect, the flange portion of each segment is annular and has a thickness that is approximately half the height of the fluid flow passage in the region surrounding the first and second holes.

[0012] According to one aspect, the flange portion has an outer peripheral edge that is separated from the edge of the fluid flow passage.

[0013] According to one aspect, each of the one or more channels extends partially through the thickness of the flange portion and has an open surface coplanar with the second surface.

[0014] According to one aspect, one or more channels include multiple channels spaced apart from each other along the second surface.

[0015] According to one aspect, the second surface of each of the first segment and the second segment is provided with one or more channels.

[0016] According to one aspect, each of the channels in the second surface of the first segment is aligned with one of the channels in the second surface of the second segment to provide one or more combined flow channels.

[0017] According to one aspect, the second surfaces of the two segments are mirror images, such that each channel in the second surface of the first segment is aligned with the corresponding channel in the second surface of the second segment.

[0018] According to one aspect, the orifice is located near the outer edge of the fluid flow passage, such that the fluid flow passage includes a narrow edge channel between each of the through fittings, wherein the narrow edge channel is open at its end; a second open end of at least one of the channels may face the outer edge of the fluid flow passage and flow in communication with the narrow edge channel.

[0019] According to one aspect, the flange portions of the first and second sections have a combined height such that the flange portions extend substantially over the entire height of the fluid flow passage to provide internal support for the fluid flow passage in the region surrounding the first and second holes, while providing flow communication between the hollow interior of each fitting and the fluid flow passage.

[0020] According to one aspect, the combined height of the flange portions of the first segment and the second segment is slightly less than the height of the fluid flow passage; and a narrow gap is provided between the second surfaces of the flange portions of the first segment and the second segment.

[0021] According to one aspect, the primary amount of fluid flow between the hollow interior of each through fitting and the fluid flow passage passes through the channel, and the secondary amount of fluid flow passes through the gap between the second surfaces of the flange portion.

[0022] According to one aspect, the spacing between the second surfaces of the flange portions is less than about 5% of the height of the fluid flow passage.

[0023] According to one aspect, the first plate and the second plate are made of aluminum alloy, wherein the inner surface of the plates is provided with a brazing alloy coating. The first surface of the flange portion is sealed to the inner surface of the first plate and the second plate, and the coating forms a brazed joint between the first surface of the flange and the inner surface of the first plate and the second plate.

[0024] According to one aspect, each hole is surrounded by an upright collar that engages with the outer surface of one of the tube sections.

[0025] According to one aspect, the flange portion of each segment has an annular disc shape with an outer peripheral edge that is circular and concentric with the tube portion.

[0026] According to one aspect, each of the channels is straight and is radially guided between its first open end and second open end.

[0027] According to another aspect of this disclosure, a thermal management system is provided comprising a plurality of heat exchangers as described herein. The heat exchangers of the system are fluidly connected in a parallel flow arrangement and are spaced apart from each other to receive components to be cooled and / or heated between the outer surfaces of adjacent pairs of heat exchangers. Attached Figure Description

[0028] Exemplary embodiments of the present disclosure will now be described by way of example with reference to the accompanying drawings, in which:

[0029] Figure 1 It is a three-dimensional view of multiple heat exchangers arranged in parallel flow.

[0030] Figure 2 It is along Figure 1 A cross-sectional view taken from line 2-2';

[0031] Figure 3 yes Figure 1 A magnified close-up view of a portion;

[0032] Figure 4 It is a perspective view of a two-piece through-fitting accessory, in which the two sections of the accessory are separated;

[0033] Figure 5 Is it through Figure 4 Vertical cross-sectional view of the two-piece through-fitting;

[0034] Figure 6 yes Figure 4 A top view of the two-piece through-fitting fitting;

[0035] Figure 7 This is a close-up view of a portion of a heat exchanger according to one embodiment;

[0036] Figure 8 A through-fitting according to another embodiment is shown;

[0037] Figure 9 A portion of a heat exchanger incorporating a through fitting according to another embodiment is shown; and

[0038] Figure 10 A portion of a heat exchanger incorporating a through fitting according to another embodiment is shown. Detailed Implementation

[0039] Figure 1 Multiple heat exchangers 10 arranged for a parallel flow configuration are shown, while Figure 2 and Figure 3 This is an enlarged view of some parts of a heat exchanger 10. As used herein, the term "parallel flow arrangement" refers to the heat exchanger 10 being combined with or adapted to be combined with common inlet and outlet manifolds that distribute the heat transfer fluid to multiple heat exchangers 10.

[0040] The heat exchanger 10 includes a first plate 12 having inner and outer surfaces 14, 16, and a second plate 18 having inner and outer surfaces 20, 22. The first and second plates 12, 18 may include peripheral flanges 24, 26, which are hermetically joined together along the peripheral flanges, for example by brazing (or "copper welding"). The first and second plates 12, 18 may be made of an aluminum alloy, and the inner surfaces 14, 20 of the plates 12, 18 may be provided with a brazing alloy (not shown) cladding that melts when heated to a sufficiently high temperature to form brazing filler metal, which forms a brazed joint between the peripheral flanges 24, 26.

[0041] The positions of the first plate and the second plate 12, 18 located inside the outer peripheral flanges 24, 26 are partially spaced apart from each other, and a fluid flow passage 28 is defined between the inner surfaces 14, 20 of the first plate and the second plate 12, 18.

[0042] A fluid flow path 28 extends between an inlet port 30 and an outlet port 32. In this embodiment, the inlet and outlet ports 30, 32 are positioned along the same end of the heat exchanger 10, and the fluid flow path 28 is schematically shown as generally U-shaped. However, it is understood that the relative positions of the inlet and outlet ports 30, 32 and the configuration of the fluid flow path 28 are merely exemplary and not significant to this disclosure. In a heat exchanger according to an alternative embodiment, the inlet and outlet ports 30, 32 may be positioned at opposite ends of the heat exchanger 10, or one or both of the ports 30, 32 may be positioned between the ends of the heat exchanger 10. The fluid flow path 28 may include one or more elements to guide the flow of heat transfer fluid between the inlet and outlet ports 30, 32, such as protrusions in the first and / or second plates 12, 18, a separate protruding intermediate plate between the first and second plates 12, 18, and / or corrugated fins or turbulence generators between the first and second plates 12, 18.

[0043] Each of the inlet port 30 and the outlet port 32 is a through opening, meaning that both the inlet port and the outlet port 30, 32 extend through the heat exchanger 10 and are in fluid communication with the fluid flow passage 28. Each of these through openings 30 or 32 includes a first hole 34 formed in the first plate 12 and a second hole 36 formed in the second plate 18, the first hole 34 and the second hole 36 being opposite to and spaced apart from each other. In this embodiment, the first hole and the second hole 34, 36 are substantially the same diameter and substantially concentric circular holes within applicable tolerances.

[0044] like Figure 1 As shown, the inlet and outlet ports 30 and 32, which are provided in a through-opening form, facilitate the connection of multiple heat exchangers 10 arranged in parallel flow, and the inlet ports 30 of adjacent heat exchangers 10 are aligned with each other, while the outlet ports 32 of adjacent heat exchangers 10 are aligned with each other. For example, as Figure 1 As shown, the direction of fluid flow through the aligned inlet and outlet ports 30 and 32 is parallel to the y-axis, while plates 12 and 18 and the fluid flow path can be aligned along the x-axis, which is perpendicular to the y-axis. Figure 1 The heat exchangers 10 are parallel to each other (along the x-axis) and spaced apart to allow components to be cooled and / or heated to be inserted between and in thermal contact with the outer surfaces of adjacent heat exchangers 10. For example, the components to be cooled and / or heated may include battery cells of a rechargeable vehicle battery (not shown). A battery thermal management system for cooling and optionally heating a rechargeable vehicle battery may include a plurality of such heat exchangers 10, i.e., fluidly connected in a parallel flow arrangement, receiving at least one battery cell between adjacent heat exchangers 10, and with the flat side of at least one battery cell in thermal contact with each outer surface of each heat exchanger 10, for example as described in, for example, commonly assigned U.S. Patent Application No. 16 / 688,390, filed November 19, 2019, and U.S. Patent No. 10,006,722 mentioned above. Rigid or flexible tubular fluid connections (not shown) may be formed between the inlet ports 30 and between the outlet ports 32 of adjacent heat exchangers 10. The thermal management system may include separate inlet and outlet manifolds (not shown), to which fittings are connected via fluid connections. Alternatively, fluid connections may directly connect fittings of adjacent heat exchangers together, in which case the inlet and outlet manifolds may consist entirely of through fittings and tubular fluid connections that connect them together.

[0045] Each of the inlet port 30 and outlet port 32 of the heat exchanger 10 is provided with a two-piece through fitting 38, which includes a first section and a second section 40, 42. As shown in this embodiment, the first section and the second section 40, 42 may be identical to each other, and in the following description, the elements of the two sections 40, 42 are given the same reference numerals.

[0046] Each of segments 40 and 42 includes a tube portion 44 and a flange portion 46, which may be integrally formed or sealed together. Each of segments 40 and 42 has a first open end and a second open end 48 and 50 and a hollow interior 52. The first open end 48 is located outside the fluid flow passage 28, while the second open end 50 is located inside the fluid flow passage 28.

[0047] Tube portion 44 extends along the y-axis from the first open end 48 toward the flange portion 46 and the second open end 50. Each tube portion 44 extends through and is tightly received in one of the first holes 34 or the second hole 36 of the plates 12, 18. In this embodiment, each hole 34, 36 is surrounded by a relatively short upright collar 54 that engages the tube portion 44. Figure 2 The collar 54 can be formed by a swaging operation and helps to retain and align segments 40, 42 within the holes 34, 36. However, the collar 54 is not required. Although each collar 54 can seal to the outer surface of the tube segment 44, it is understood that any seal provided by the collar 54 is not necessary for achieving a fluid seal between fitting 38 and plates 12, 18, as will be discussed further below.

[0048] In this embodiment, holes 34, 36 and the optional collar 54 are circular, and the tube portion 44 of fitting 38 is a cylindrical tubular element with a circular cross-section, but other shapes may be used. At the first open end 48 of fitting 38, the tube portion 44 may include a connecting element (not shown) for connecting the tube portion 44 to a flexible or rigid tubular conduit, or to a tube portion 44 of an adjacent heat exchanger 10. Such a connecting element may include a socket, thread, hose barb, quick connector, etc.

[0049] Each fitting 38 has a flange portion 46 that extends radially outward from and engages with the tube portion 44 (along the x-axis), and an outer peripheral edge 56 positioned radially outward from the outer surface of the tube portion 44. In this embodiment, the flange portion 46 has an annular disc shape and the outer peripheral edge 56 is rounded and concentric with the tube portion 44.

[0050] The flange portion 46 has opposing first and second surfaces 58, 60, both extending radially outward from the tube portion 44 to the outer peripheral edge 56. Surfaces 58, 60 are shown as annular, straight, and parallel. In the assembled heat exchanger 10, the first surface 58 contacts the inner surface 14 of the first plate 12 or the inner surface 20 of the second plate 18 and is sealed together using a fluid-tight connection. The first surface 58 of the flange portion 46 can be metallurgically bonded to the inner surfaces 14, 20 of the first or second plate 12, 18, for example, by brazing. Where brazed connections are provided, fitting 38 can be made of a brazable aluminum alloy, and the first and second plates 12, 18 can be formed from brazable sheets of aluminum as described above, and the inner surfaces 14 or 20 include a cladding of brazed filler metal. Alternatively, an annular brazed ring or gasket made of brazed filler metal may be provided between the first surface 58 and the inner surfaces 14, 20 of the first or second plates 12, 18. It is understood that the first surface 58 of the flange portion 46 provides a continuous, uninterrupted seal between the fitting 38 and the plates 12, 18. The width of the first surface 58 is sufficient to reliably provide a fluid seal. Regardless of any additional seals that may be provided between the collar 54 and the tube portion 44, a seal between the first surface 58 of each flange portion 46 and the inner surfaces 14, 20 of the first or second plates 12, 18 provides a fluid seal between the fitting 38 and the plate 12.

[0051] The spacing between the first and second surfaces 58 and 60 (along the y-axis) defines the thickness of the flange portion 46, which is approximately half the height of the fluid flow passage 28.

[0052] The second surface 60 of the flange portion 46 of one segment 40 is facing the second surface 60 of the flange portion 46 of another segment 42. The second surface 60 of one or both of the flange portions 46 of segments 40 and 42 is interrupted by one or more channels 62. Each channel 62 has a first open end 64 and an opposing second open end 66. The first open end 64 is located on the inner surface of the flange portion 46 and / or the tube portion 44 and is in fluid communication with the hollow interior 52 of the fitting 38. The second open end 66 is located at the outer peripheral edge 56 of the flange portion 46 and is in fluid communication with the fluid flow passage 28. Each channel 62 extends partially through the thickness of the flange portion 46 and has an opening surface 68 coplanar with the second surface 60, but each channel 62 is sealed between its first open end and its second open ends 64, 66 by the material of the flange portion 46. In other words, the channel 62 does not open along the first surface 58 of the flange portion 46, thus providing a continuous sealing surface.

[0053] The combined thickness of the flange portions 46 of the two sections 40, 42 allows the flange portions 46 to provide support for the plates 12, 18 in the region surrounding the ports 30, 32 without negatively impacting the seal between the outer peripheral flanges 24, 26, particularly in the region near the ports 30, 32. Where the combined thickness of the flange portions 46 is too large (i.e., relative to the height of the fluid flow passage 28 in the region immediately surrounding the ports 30, 32), this generally does not affect the seal between the flange portions 46 and the inner surfaces 14, 20 of the plates 12, 18. However, excessive thickness of the flange portions 46, for example, where the combined thickness of the flange portions 46 exceeds the height of the fluid flow passage 28, may result in insufficient contact between the outer peripheral flanges 24, 26. This may negatively impact the ability to form a fluid seal between the outer peripheral flanges 24, 26 during the assembly of the heat exchanger 10.

[0054] On the other hand, if the combined thickness of the flange portion 46 is too small relative to the height of the fluid flow passage 28, the sealing of the outer peripheral flanges 24, 26 may not be negatively affected, but insufficient thickness of the flange portion 46 may negatively affect the sealing of the flange portion 46 with the inner surfaces 14, 20 of the plates 12, 18, and / or may negatively affect the support provided by the flange portion 46 to the plate walls 12, 18.

[0055] Due to manufacturing tolerances, it may be difficult to precisely match the combined thickness of the flange portions 46 to the height of the fluid flow passage 28. Therefore, the combined thickness of the flange portions 46 allows the first surface 58 of the flange portions 46 to be sealed to the inner surfaces 14, 20 of the plates 12, 18, while the second surfaces 60 of the flange portions 46 are slightly spaced apart from each other, the spacing being determined by… Figure 9 and Figure 10 The number 76 is indicated in the diagram. This spacing 76 between the second surfaces 60 will ensure adequate contact and sealing between the outer peripheral flanges 24 and 26.

[0056] The spacing 76 between the second surfaces 60 is designed to be small enough that slight deflections of the plates 12, 18 toward each other (e.g., when the heat exchangers 10 are connected together) would allow the second surfaces 60 to engage directly with each other, preventing further deflection and collapse of the fluid flow passage 28.

[0057] In practice, the heat exchanger 10 can be designed with a gap 76 on the order of approximately 0.1 mm between the second surfaces 60 of the flange portions 46, while the first surfaces 58 of the flange portions 46 are sealed to the inner surfaces 14, 20 of the plates 12, 18. This size of gap represents less than approximately 5% of the typical height of the fluid flow passage 28, less than approximately 10% of the typical thickness of the flange portions 46, and / or no more than 10%-20% of the height of the flow passage 62. This gap 76 allows a small amount of fluid to flow between the second surfaces 60 (outside the flow passage 62), which reduces the pressure drop of fluid flowing from the interior 52 of each segment 40, 42 to the fluid flow passage 28. However, the amount of fluid flowing through the gap 76 is typically less than the amount flowing through the flow passage 62.

[0058] Channel 62 can have various constructions, being straight, bent, or curved, and can have various cross-sectional shapes, such as square, rectangular, arc-shaped, triangular, etc. Channel 62 can have a constant or variable cross-sectional area along its entire length. In this embodiment, each channel 62 is straight and extends substantially radially between its first open end and second open ends 64, 66. Each channel 62 is shown as having a constant rectangular cross-sectional shape. Channel 62 can be formed by molding, forging, casting, or machining.

[0059] One or more channels 62 are provided in the second surface 60 of at least one of the segments 40 and 42. In this embodiment, each segment 40 and 42 includes a plurality of channels 62. When a plurality of channels 62 are provided, they can each have any of the above-described configurations independently. The channels 62 can be regularly or irregularly spaced apart from each other along the second surface 60.

[0060] In this embodiment, the second surface 60 has a plurality of straight radial channels 62, each channel 62 having a substantially constant rectangular cross-section. The channels 62 are irregularly spaced along the second surface 60, and four channels 62 with substantially identical constructions are spaced substantially equally apart from each other, with a wider channel 62 separated from the other four channels 62 by a larger interval. For example, as... Figure 6 As shown in the plan view, the group of four narrower channels 62 is centered along axis A, which passes through the wider channel 62. Therefore, the group of four narrower channels 62 faces away from the wider channel 62.

[0061] Although a specific number and configuration of channels 62 are shown in this embodiment, it will be understood that the number and configuration of channels 62 are highly variable and depend on the specific application. Furthermore, at least where the channels 62 are machined into the second surface 60 of each flange portion 46, the pattern of the channels 62 can be customized to meet the requirements of any specific application without altering the basic configuration of each segment 40, 42.

[0062] At least one of the flange portions 46 of segments 40 and 42 is provided with one or more channels 62. In this embodiment, both segments 40 and 42 are provided with multiple channels 62. When both flange portions 46 of segments 40 and 42 are provided with channels 62, the channels 62 of opposite flange portions 46 may be the same or different, and may be aligned or misaligned. For example, in this embodiment, the two segments 40 and 42 are identical and include the same number and arrangement of channels 62. Furthermore, the heat exchanger 10 is assembled such that the channels 62 of opposite flange portions 46 are aligned with each other, and the second surfaces 60 are arranged opposite each other, facing each other, and are mirror images of each other. Thus, as shown in the figures, the corresponding channels 62 of opposite flange portions 46 are combined together in terms of the thickness dimension of opposite flange portions 46. These combined flow channels are labeled with reference numeral 70 in the figures and have a height approximately twice that of a single flow channel 62.

[0063] like Figure 3 As shown, holes 34 and 36 are positioned close to the outer edge of the fluid flow passage 28, similar to fitting 38. Therefore, the fluid flow passage 28 includes narrow edge channels 72 between the outer edges of each fitting 38 and the fluid flow passage 28, adjacent to the outer peripheral flanges 24 and 26. In this embodiment, each narrow edge channel 72 extends about half the circumference of the flange portion 46 of the fitting 38 and opens at both ends where it extends to the remainder of the fluid flow passage 28.

[0064] Each fitting 38 is arranged such that the second end 66 of at least one of the channels 62 faces the outer edge of the fluid flow passage 28 and is in fluid communication with one of the narrow edge channels 72 to facilitate fluid circulation through the narrow edge channel 72 and prevent fluid stagnation in that area. In the illustrated embodiment, the two sections 40, 42 of each fitting 38 are arranged such that the main portion of the fluid flowing through the channel 62 is directed toward or received from the heat transfer area of ​​the heat exchanger 10 (i.e., the central area of ​​the heat exchanger 10), while a secondary portion of the fluid flowing through the channel 62 is directed toward or received from the narrow edge channel 72. In this embodiment, the single wider channel 62 faces the narrow edge channel 72 and the outer peripheral flanges 24, 26, while the remaining channels 62 generally face the heat transfer area of ​​the fluid flow passage 28 and face away from the outer peripheral flanges 24, 26 and the narrow edge channel 72. However, this is not necessary, and the position of the channel 62 relative to the narrow edge channel 72 may differ from that shown in the figures.

[0065] As shown, each hole 34, 36 can be surrounded by an elevated circular protrusion 74, which is sized to tightly receive the flange portion 46 of the fitting 38 without obstructing the second open end 66 of the channel 62.

[0066] In the assembled heat exchanger 10, the two sections 40, 42 of each fitting 38 are arranged such that the second surfaces 60 of opposing flange portions 46 face each other, the first surface 58 of the flange portion 46 of the first section 40 is in sealing contact with the inner surface 14 of the first plate 12, and the first surface 58 of the flange portion 46 of the second section 42 is in sealing contact with the inner surface 20 of the second plate 18. The flange portions 46 of the two sections 40, 42 extend together over the entire height of the fluid flow passage 28, with or without an optional spacing 76, and thus the fitting 38 provides internal support for the fluid flow passage 28 in the area surrounding the holes 34, 36, while providing fluid communication between the hollow interior 52 of each fitting 38 and the surrounding fluid flow passage 28.

[0067] The support provided by the flange portion 46 of sections 40, 42 eliminates the need for additional support structures between the plates 12, 18 near the inlet and outlet ports 30, 32. This allows for a reduction in the number of components constituting the heat exchanger 10 and / or simplification of the structure of the plates 12, 18.

[0068] As described above, the second surfaces 60 of the opposing flange portions 46 of segments 40 and 42 may contact each other or be spaced apart by a gap 76, but they do not necessarily need to be joined together using a fluid seal. However, in some embodiments, the opposing flange portions 46 may be metallurgically joined together, for example, by brazing. In the case of a brazed connection, an annular brazed gasket may be provided between the second surfaces 60 and the opposing flange portions 46 during the assembly of the heat exchanger 10.

[0069] Figure 7 A top plan view is shown of a portion of the heat exchanger 10 in the region immediately surrounding the outlet port 32, particularly of the second section 42 of the fitting 38 received in the second hole 36 of the second plate 18. The heat exchanger 10 includes a fluid flow passage 28, wherein the plate 18 includes a plurality of raised ribs 78 to guide fluid flow across the entire heat transfer region of the heat exchanger 10 to maximize heat transfer and / or temperature uniformity. The raised ribs 78 divide the fluid flow passage 28 into individual flow channels 80, which communicate with at least some of the flow channels 62 of the fitting 38. In the specific example shown, the plurality of channels 62 of the fitting 38 face the open ends of the flow channels 80 and may or may not be directly flush with the channels 80 to receive fluid directly or indirectly from the channels 80, such as... Figure 7 As indicated by the arrow in the diagram. A portion of the fluid discharged from channel 80 will flow into narrow edge channel 72, which partially surrounds the outer peripheral edge 56 of flange portion 46. The fluid will then pass through single channel 62 facing away from channel 80 into outlet port 32.

[0070] Figure 7It is also shown that the channels 62 of accessory 38 do not necessarily have to have the same width. The width of channel 62 can be varied to better control fluid flow in order to maximize heat transfer and / or temperature uniformity.

[0071] As described above, it may be desirable for the segments 40, 42 of the through fitting 38 to have a specific orientation within the fluid flow passage 28, and it may be desirable for the segments 40, 42 to have a specific orientation relative to each other. Therefore, during the assembly of the heat exchanger 10, it may be desirable to ensure the correct orientation of the segments 40, 42 within the first and second holes 34, 36 of the plates 12, 18. This can be at least partially achieved by ensuring a tight fit between the collar 54 surrounding the holes 34, 36 and the tube portion 44 of the segments 40, 42 of the through fitting 38. The fit between the collar 54 and the tube portion 44 is tight enough to prevent rotation of the segments 40, 42 during assembly.

[0072] In some embodiments, it may be desirable to provide alignment features for segments 40, 42 to ensure that they will be combined in a specific orientation. For example, as Figure 8 As shown, the second surface 60 of the flange portion 46 may be provided with interlocking alignment features to facilitate the orientation of the segments 40, 42, aligning their channels 62. These alignment features are shown as including ribs 82 protruding from the second surface 60 of the second segment 42, which are received in grooves 84 recessed in the second surface 60 of the first segment 40. With the alignment features incorporated into the segments 40, 42, they can have any desired configuration.

[0073] Figure 9 A portion of the heat exchanger 10 is shown, in which all channels 62 are located in the first section 40 of the through fitting 38, while the second section has no channels.

[0074] Figure 10 A portion of the heat exchanger 10 is shown, and many additional characteristics are described, most of which have already been mentioned above. Figure 10 In the process, the first segment and the second segments 40, 42 of the through-fitting 38 each include a plurality of channels 62 in their second surface 60, the channels 62 being identified by reference numerals A to G in the accompanying drawings. Figure 10 As shown, channels 62 can have different cross-sectional shapes and sizes. In this respect, channels 62C and 62D have larger cross-sectional areas than other channels 62; channel 62A has a rounded top, while the other channels 62 are rectangular; channels 62A and 62B are partially aligned with each other; channels 62C and 62D are identical and fully aligned; channel 62F has a smaller cross-sectional area than other channels 62; and channels 62E, 62F, and 62G are not aligned. It is understood that any one or more of these features can be incorporated into the through fitting 38.

[0075] While various embodiments have been described in conjunction with this disclosure, it should be understood that certain changes and modifications can be made to the described exemplary embodiments within the scope of this disclosure. Therefore, the embodiments discussed above are to be considered illustrative rather than restrictive.

Claims

1. A heat exchanger, comprising: (a) A first plate having an inner surface, an outer surface and at least one first hole; (b) A second plate having an inner surface, an outer surface and at least one second hole, wherein each of the at least one first hole is opposite and spaced apart from one of the at least one second hole; (c) A fluid flow path defined between the inner surfaces of the first plate and the second plate; (d) At least one through fitting, wherein each through fitting includes a first segment and a second segment, each segment having a first open end located outside the fluid flow passage, a second open end located inside the fluid flow passage, and a hollow interior; Each of the aforementioned segments includes a tube portion and a flange portion; The flange portion is located inside the fluid flow passage; In this embodiment, the tubular portion of each segment extends through one of the first hole or the second hole to reach the first open end of the segment; Each of the segments has a flange portion that extends radially outward from and is joined to the tube portion. The flange portion has opposing first and second surfaces, wherein the first surface is continuous and sealingly joined to the inner surface of one of the first and second plates to provide a continuous seal between the segment and the first or second plate in the region surrounding the first or second hole. Wherein, the second surface of the flange portion of the first segment and the second surface of the flange portion of the second segment are facing each other; The second surface of one or both of the first segment and the second segment includes one or more channels, each channel having a first open end and an opposing second open end, wherein the first open end is in flow communication with the hollow interior of the through fitting, and the second open end is in flow communication with the fluid flow passage.

2. The heat exchanger according to claim 1, characterized in that, The fluid flow path extends between the inlet port and the outlet port; Each of the inlet port and the outlet port is in the form of a through opening, the through opening including a pair of at least one first hole and at least one second hole.

3. The heat exchanger according to claim 1, characterized in that, The first and second sections of each of the through fittings are arranged concentrically with each other.

4. The heat exchanger according to claim 1, characterized in that, The flange portion of each segment is annular and has a thickness approximately half the height of the fluid flow passage in the region surrounding the first and second holes.

5. The heat exchanger according to claim 1, characterized in that, The flange portion has an outer peripheral edge that is spaced apart from the edge of the fluid flow passage.

6. The heat exchanger according to claim 1, characterized in that, Each of the one or more channels extends partially through the thickness of the flange portion and has an open surface coplanar with the second surface.

7. The heat exchanger according to claim 1, characterized in that, The one or more channels include a plurality of channels spaced apart from each other along the second surface.

8. The heat exchanger according to claim 1, characterized in that, The second surface of each of the first segment and the second segment is provided with one or more channels.

9. The heat exchanger according to claim 8, characterized in that, Each of the channels in the second surface of the first segment is aligned with one of the channels in the second surface of the second segment to provide one or more combined flow channels.

10. The heat exchanger according to claim 9, characterized in that, The second surfaces of the first segment and the second segment are mirror images of each other, such that each channel in the second surface of the first segment is aligned with the corresponding channel in the second surface of the second segment.

11. The heat exchanger according to claim 1, characterized in that, The hole is located near the outer edge of the fluid flow passage, such that the fluid flow passage includes a narrow edge channel between each of the through fittings, wherein the narrow edge channel is open at its end; In this embodiment, the second open end of at least one of the channels faces the outer edge of the fluid flow passage and is in flow communication with the narrow edge channel.

12. The heat exchanger according to claim 1, characterized in that, The flange portions of the first and second segments have a combined height such that the flange portions extend substantially over the entire height of the fluid flow passage to provide internal support for the fluid flow passage in the region surrounding the first and second holes, while providing flow communication between the hollow interior of each fitting and the fluid flow passage.

13. The heat exchanger according to claim 12, characterized in that, The combined height of the flange portions of the first and second sections is slightly less than the height of the fluid flow passage; A narrow gap is provided between the second surfaces of the flange portions of the first segment and the second segment.

14. The heat exchanger according to claim 12, characterized in that, The primary amount of fluid flow between the hollow interior of each through fitting and the fluid flow passage passes through the passage, and the secondary amount of fluid flow passes through the gap between the second surfaces of the flange portion.

15. The heat exchanger according to claim 12, characterized in that, The spacing between the second surfaces of the flange portion is less than about 5% of the height of the fluid flow passage.

16. The heat exchanger according to claim 1, characterized in that, The first plate and the second plate are made of aluminum alloy, wherein the inner surface of the plate is provided with a brazing alloy coating, wherein the first surface of the flange portion is sealed to the inner surface of the first plate and the second plate, and the coating forms a brazing joint between the first surface of the flange and the inner surface of the first plate and the second plate.

17. The heat exchanger according to claim 1, characterized in that, Each of the holes is surrounded by an upright collar that engages with the outer surface of one of the tube portions.

18. The heat exchanger according to claim 1, characterized in that, Each of the segments has a flange portion with an annular disc shape and an outer peripheral edge that is circular and concentric with the tube portion.

19. The heat exchanger according to claim 1, characterized in that, Each of the channels is straight and is radially guided between the first open end and the second open end.

20. A thermal management system comprising a plurality of heat exchangers according to claim 1, wherein the heat exchangers are fluidly connected in a parallel flow arrangement, and wherein, The heat exchangers are spaced apart from each other to receive components to be cooled and / or heated between the outer surfaces of adjacent pairs of heat exchangers.

Images