Counterflow heat exchanger for thermal battery management applications

Abstract

A battery cell heat exchanger (10) comprising:a first outer plate (12) having a central, generally planar region (18) surrounded by a peripheral flange (20);a second outer plate (14) having a central, generally planar region (18) surrounded by a peripheral flange (20);andan intermediate plate (16) disposed between the first and second outer plates (12, 14) and having a circumferential flange (40), the circumferential flanges (20) of the outer plates (12, 14) being in sealing contact with the circumferential flange (40) of the intermediate plate (16), a plurality of first fluid flow passages (58) formed between the intermediate plate (16) and the first outer plate (12), each of the first fluid flow passages (58) having a first end for admitting a fluid into the first fluid flow passages (58) and a second end for discharging the fluid from the first fluid flow passages (58), the first and second ends defining a direction of flow through the first fluid flow passages (58);a plurality of second fluid flow passages (60) formed between the intermediate plate (16) and the second outer plate (14), each of the second fluid flow passages (60) having a first end for admitting fluid into the second fluid flow passages (60) and a second end for discharging fluid from the second fluid flow passages (60), the first and second ends defining a direction of flow through the second fluid flow passages (60); wherein the battery cell heat exchanger (10) further comprises:a first protrusion (64) extending out of the plane of the peripheral flange (40) of the intermediate plate (16) in a first direction and provided for sealing contact with an inner surface of the second outer plate (14);a first manifold opening (34) formed in the first protrusion (64) and in fluid communication with the first ends of the plurality of first fluid flow passages (58);a second protrusion (65) extending out of the plane of the peripheral flange (40) of the intermediate plate (16) in a second direction opposite to the first protrusion (64) and provided for sealing contact with an inner surface of the first outer plate (12); a second manifold opening (36) formed in the second protrusion (65) and in fluid communication with the second ends of the plurality of second fluid flow passages (60); an inlet in fluid communication with the first manifold opening (34) and for admitting fluid into the battery cell heat exchanger (10);an outlet in fluid communication with the second manifold opening (36) and for discharging fluid from the battery cell heat exchanger (10), wherein the first and second fluid flow passages (58, 60) are arranged to alternate over a main body region such that the first fluid flow passages (58) are in heat transfer relationship with the second fluid flow passages (60); wherein the second ends of the first fluid flow passages (58) are in fluid communication with the first end of the second fluid flow passages (60), and the flow direction of the first fluid flow passages (58) is therefore opposite to the flow direction of the second fluid flow passages (60);

Description

CROSS-REFERENCE TO RELATED REGISTRATION

[0001] This application claims the priority and benefits of provisional US patent application No. 62 / 150625, filed on April 21, 2015, entitled "Counterflow Heat Exchanger for Thermal Battery Management Applications." The content of the aforementioned patent application is hereby expressly incorporated into the detailed description of the present application. TECHNICAL AREA

[0002] This disclosure relates to a heat exchanger for thermal battery management applications. More specifically, the disclosure relates to a battery cell heat exchanger that can be arranged under a stack of several adjacent battery cells or battery cell containers, or that can be arranged between the adjacent battery cells or battery cell containers in the stack to dissipate heat in rechargeable battery units. BACKGROUND

[0003] Rechargeable batteries, such as those consisting of many lithium-ion cells, can be used in a wide range of applications, including electric vehicles (EVs) and hybrid electric vehicles (HEVs). These applications often require advanced battery systems with high energy storage capacity that can generate significant amounts of heat, which must be dissipated. The thermal management of these types of systems generally requires that the maximum temperature of individual cells remains below a predetermined specific temperature.

[0004] Cold plate heat exchangers are heat exchangers on which a stack of adjacent battery cells or battery cell containers, each holding one or more battery cells, is arranged for cooling and / or regulating the temperature of a battery unit. The individual battery cells or battery cell containers are arranged in mutually facing contact to form the stack, with the stack of battery cells or battery cell containers on a cold plate heat exchanger such that an end face or end surface of each battery cell or battery cell container is in surface-to-surface contact with a surface of the heat exchanger.

[0005] Heat exchangers for cooling and / or regulating the temperature of a battery unit can also be arranged between the individual battery cells or battery cell containers that form the stack or battery unit, with the individual heat exchangers being interconnected by common inlet and outlet manifolds. Heat exchangers arranged or clamped between adjacent battery cells or battery cell containers in the stack may sometimes be referred to as inter-cell elements (e.g., "ICE" plate heat exchangers) or cooling fins.

[0006] Temperature uniformity across the surface of an individual battery cell, as well as across all cells in the battery pack, is of paramount importance because the battery is a chemical reaction whose performance is significantly influenced by the temperature at which it occurs. A thermal gradient within the battery causes some cells to charge and discharge faster than others, leading to problems with the battery pack's durability. Accordingly, temperature uniformity across the heat exchanger surface is a crucial consideration in the thermal management of battery units, as it helps ensure that the temperature difference between individual battery cells within the overall battery pack is kept to a minimum.It is generally known that the temperature of the coolant passing through a heat exchanger increases as it travels along the length of the fluid channel(s) from inlet to outlet. Assuming that the surface temperature of the heat exchanger is generally proportional to the temperature of the coolant or fluid passing through it, the coolant temperature is lower at the inlet end of the heat exchanger and higher near the outlet end, resulting in an inherent temperature difference across the surface of the heat exchanger. Consequently, battery cells located near the inlet end of the heat exchanger are exposed to a lower coolant temperature than battery cells located near the outlet end, resulting in a potential temperature difference between the battery cells, which is generally undesirable.Therefore, heat exchangers that offer improved temperature uniformity across the heat exchange surface can provide improved or more uniform cooling for individual battery cells or battery cell containers across the entire surface of the heat exchanger plates. SUMMARY OF THE PRESENT DISCLOSURE

[0007] According to an embodiment of the present disclosure, a battery cell heat exchanger is provided, comprising: a main body region with opposite ends and a first and a second outer surface, each defining a primary heat exchange surface between the opposite ends, wherein the main body region comprises a first outer plate, a second outer plate and an intermediate plate arranged between the first and the second outer plate;several first fluid flow passages formed within the main body region between the intermediate plate and one of the first and second outer plates, each of the first fluid flow passages having a first end for letting fluid into the first fluid flow passages and a second end for letting fluid out of the first fluid flow passages, and the first and second ends defining a flow direction through the first fluid flow passages;Several secondary fluid flow passages formed within the main body area between the intermediate plate and the other outer plate, each of the secondary fluid flow passages having a first end for admitting fluid into the secondary fluid flow passages and a second end for discharging fluid from the secondary fluid flow passages, the first and second ends defining a flow direction through the secondary fluid flow passages; an inlet manifold in fluid communication with the first ends of the several secondary fluid flow passages; an outlet manifold in fluid communication with the second ends of the several secondary fluid flow passages;wherein the first and second fluid flow passages are arranged such that they alternate through the main body region such that the first fluid flow passages are in a heat transfer relationship with the second fluid flow passages; and wherein the second ends of the first fluid flow passages are in fluid contact with the first end of the second fluid flow passages and the flow direction of the first fluid flow passages is therefore opposite to the flow direction of the second fluid flow passages. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Reference is now made, by way of example, to the accompanying drawings, which show exemplary embodiments of the present application, and in which:

[0009] Fig. 1 a perspective view of a battery cell heat exchanger according to an embodiment of the present disclosure;

[0010] Fig. 2. A skewed perspective view of the heat exchanger according to Fig. 1 is;

[0011] Fig. 3 a perspective view of an intermediate plate of the heat exchanger of Fig. 1 is;

[0012] Fig. 4 a detailed view of one end of the intermediate plate of Fig. 3 is;

[0013] Fig. 5 a perspective detail view of the heat exchanger of Fig. 1 along a longitudinal section line through the inlet manifold, wherein the upper plate of the heat exchanger is transparent;

[0014] Fig. 6 A perspective detail view of part of the heat exchanger of Fig. 1 along a longitudinal section line through the inlet manifold, with part of the upper plate removed, and containing schematic flow direction lines;

[0015] Fig. 6A a perspective detail view of part of the heat exchanger of Fig. 1 along a longitudinal section line through the inlet manifold, the upper plate being transparent and containing schematic flow direction lines;

[0016] Fig. 7 a perspective detail view of the opposite end of the in Fig. The intermediate plate shown in section 3 is;

[0017] Fig. 7A a perspective detail view of the in Fig. 7 shown end of the heat exchanger, wherein the upper plate of the heat exchanger is transparent;

[0018] Fig. 8 a perspective detail view of the heat exchanger of Fig. 1 along a longitudinal section line through the outlet distributor, wherein the upper plate of the heat exchanger is transparent;

[0019] Fig. 9 a perspective detail view of the heat exchanger of Fig. 1 along a longitudinal section line through the outlet manifold, wherein the upper plate of the heat exchanger is transparent, and which contains schematic flow lines illustrating the outflow from the heat exchanger;

[0020] Fig. 9A another perspective detail view of the heat exchanger from Fig. 1 along a longitudinal section line through the outlet manifold, wherein the upper plate of the heat exchanger is transparent, and contains schematic flow lines illustrating the outflow from the heat exchanger;

[0021] Fig. 10 a perspective detail view of the area 9 from Fig. Figure 9 illustrates the outflow through the heat exchanger;

[0022] Fig. 11 is a perspective view of an alternating intermediate plate of another embodiment of the heat exchanger;

[0023] Fig. 12 a perspective detail view of an area of ​​the heat exchanger of Fig. 1 along a section line that extends across the width of the heat exchanger;

[0024] Fig. 13 is an expanded perspective view of a heat exchanger according to another embodiment of the present disclosure;

[0025] Fig. 14 a cross-sectional view of the composite heat exchanger of Fig. 13 along the longitudinal axis of the heat exchanger or the intersection line 14-14 in Fig. 13 is;

[0026] Fig. 15 a cross-sectional view of the distributor area of ​​the heat exchanger along the in Fig. The section line 15-15 shown in section 13 is;

[0027] Fig. 16 a detailed view of the in Fig. 14 circled areas;

[0028] Fig. 17 a split perspective view of another embodiment of the heat exchanger of Fig. 13 is;

[0029] Fig. 18 a cross-sectional view of the distributor area of ​​the heat exchanger of Fig. 17 along the intersection line 18-18;

[0030] Fig. 19 a schematic sectional view of an area of ​​the heat exchanger of Fig. 13 or Fig. 17 in the transverse direction;

[0031] Fig. 20 a schematic sectional view of an area of ​​the heat exchanger of Fig. 13 or Fig. 17, which uses a modified intermediate plate, is in the transverse direction;

[0032] Fig. 21 a perspective partial view of another embodiment of an intermediate plate for forming the heat exchanger of Fig. 13 or Fig. 17 is; and

[0033] Fig. 22 A schematic top view of a modified outer plate for use with the heat exchanger of Fig. 13 or Fig. 17 is.

[0034] The same reference numbers can be used in different figures to denote similar components. DESCRIPTION OF EXAMPLES OF EXECUTION

[0035] Fig. Figure 1 shows an exemplary embodiment of a battery cooling heat exchanger. 10 according to an embodiment of the present disclosure. As shown, the battery cooling heat exchanger has 10 a pair of outer plates 12 , 14 with an intermediate plate arranged between them 16 up. The outer plates 12 , 14 Each defines a middle, generally flat area 18 , which is from a circumferential flange 20 is surrounded. The circumferential flange 20extends from the middle, generally flat area 18 away to the outside and around the perimeter of the outer plates 12 , 14 around. The middle, generally flat area 18 each of the records 12 , 14 protrudes from the plane of the circumferential flange 20 so that, when the outer plates 12 , 14 with the intermediate plate 16 are composed of internal spaces or gaps between the middle, generally flat areas 18 each of the outer plates 12 , 14 and the corresponding side or surface of the intermediate plate 16 are formed. More precisely, in the embodiment illustrated in the drawings, the outer plates 12 , 14 generally identical to each other, with one of the outer plates being 12 , 14 with reference to the other of the outer plates 12 ,14 The opposite is true if they are connected to the intermediate plate. 16 are composed so that the outer plates 12 , 14 They are essentially mirror images of each other. Therefore, if the outer plates 12 , 14 and the intermediate plate 14 are composed of each other, the first (or lower) outer plate 12 under (or on one side of) the intermediate plate 16 arranged, and the second (or upper) outer plate 14 is above (or on the opposite side of) the intermediate plate 16 arranged. When the outer plates 12 , 14 and the intermediate plate 16 When arranged together, the circumferential flange seals. 20 the respective outer plate 12 , 14 against a corresponding area of ​​the corresponding side of the intermediate plate 16ab, thereby obtaining a fluid-tight seal if the plates are brazed or otherwise joined together and a distance of the middle, generally flat area. 18 each outer plate 12 , 14 to the intermediate plate 16 consists of creating gaps between them. Accordingly, a first gap is 26 between the first or lower outer plate 12 and the corresponding surface of the first page 15 the intermediate plate 16 formed. Similarly, a second gap is formed. 28 between the second or upper outer plate 14 and the corresponding surface or second side 17 the intermediate plate 16 educated.

[0036] While the embodiment illustrated in the drawings shows that the outer plates 12 , 14 with a circumferential flange 20are formed, which is located in a region that is separate from the middle, generally flat area. 18 the plates 12 , 14 It should be noted that the outer plates extend to different levels. 12 , 14 also as stamped flat plates with a separate frame part that is placed between the respective outer plates 12 , 14 is arranged, can be formed, with the corresponding surface or respective side 15 , 17 the intermediate plate 16 is arranged in such a way that it provides a fluid-tight seal and a distance between the outer plates 12 , 14 from the intermediate plate 16 The way is obtained, which the column 26 , 28 between these forms. Alternatively, the intermediate plate can be used. 16with a circumferential rib or equivalent sealing feature on each side of it to form a seal against the corresponding outer plate 12 , 14 to obtain. Therefore, it should be noted that there are various methods for sealing the outer plates. 12 , 14 opposite the intermediate plate 16 the provision of gaps or enclosed fluid channels between these shall be considered within the scope of the present disclosure.

[0037] According to Fig. 2 are inlet and outlet openings. 30 , 32 at one end of the outer plates 12 , 14 formed. The inlet and outlet openings. 30 , 32 are arranged adjacent to each other and laterally along the end or width of the plates 12 , 14 aligned. Corresponding inlet and outlet distribution openings. 34 , 36are also in the intermediate plate 16 formed. Therefore, if the outer plates 12 , 14 and the intermediate plate 16 The inlet and outlet openings are composed of each other. 30 , 32 , which are in the outer plates 12 , 14 are formed axially with the corresponding inlet and outlet distributor openings 34 , 36 , which are in the intermediate plate 16 are formed, aligned. The inlet and outlet distribution openings. 34 , 36 are specifically shaped and / or shaped in such a way that the inlet distributor opening 34 a fluid access to the first gap 26 , which is between the first outer plate 12 and the intermediate plate 16 is formed, provides, while the outlet distributor opening 36 a fluid access to the second gap 28 , which is between the second outer plate 14and the intermediate plate 16 It is formed, provides. The inlet and outlet openings. 30 , 32 , 34 , 36 Together they form inlet and outlet manifolds for supplying and discharging a heat exchange fluid to and from the heat exchanger. 10 , as described in detail below.

[0038] In the Fig. 1– Fig. The inlet and outlet openings are shown in the illustrated embodiment 2. 30 , 32 in both outer plates 12 , 14 formed. This is particularly suitable when the heat exchanger 10 intended for use as an intercellular element (or ICE plate) in which multiple heat exchangers 10 are arranged and are to be connected to each other by common connecting inlet and outlet distributor fluid lines (not shown). If, on the other hand, the heat exchanger 10Designed for use as a cold plate heat exchanger, the inlet and outlet openings are 30 , 32 to an inlet similar to a hole for a hose hook fitting in the area 30 the record 12 or 14 and an outlet access point in the area 32 the record 12 or 14 reduced, whereby the other inlet or outlet areas of the other outer plate 12 , 14 are potentially free of fluid openings.

[0039] The intermediate plate 16 is in connection with the Fig. 2, Fig. 3 and Fig. 5 describe in detail. The intermediate plate 16 is a generally flat part with a central, generally flat surface 38 , which also includes a circumferential flange 40 is surrounded. The intermediate plate 16 It generally has the same base area as the outer plates.12 , 14 with their respective circumferential flanges 20 , 40 , which form a seal in surface-to-surface contact when the outer plates 12 , 14 with the intermediate plate 16 are composed of...

[0040] The middle, generally flat surface 38 extends between the first and second ends 42 , 44 the intermediate plate 16 The first end 42 the intermediate plate 16 features an inlet and an outlet distribution opening 34 , 36 as well as a transition area 43 , which generally lie between the inlet and outlet distribution openings 34 , 36 and the middle, generally flat surface 38 the intermediate plate 16 is arranged on, wherein the transition surface 43 along the width of the intermediate plate 16extends and is generally in the same plane as the circumferential flange 40 , which determines the circumference of the intermediate plate 16 forms, lies. The second end 44 the intermediate plate 16 has an elongated distribution opening or channel 46 up, which is in the intermediate plate 16 is formed and generally extends across the width of the intermediate plate 16 extends so that the distribution channel 46 between the middle, generally flat surface 38 the record 16 and the corresponding end edge of the surrounding area of ​​the circumferential flange 40 is arranged.

[0041] The middle, generally flat area 38 the record 16 It generally has the form of a corrugated surface with several interconnected coils or elongated ribs. 50 exhibits features that extend beyond the surface of the plate 16are formed and extend over the length of the middle, generally flat surface 38 between the transition area 43 and the distributor opening or the channel 46 extend. The twists or elongated ridges 50 Each have an upper surface area 52 (or "comb") and a pair of side areas 54 on, whereby the elongated bridges 50 through lower surface areas 56 are connected to each other. The coils or elongated webs 50 are within the middle level range 38 the plate is formed in such a way that the elongated ribs 50 from the plane of the intermediate plate 16 protrude, with the upper surface areas 52 lie in a plane that is generally parallel to, but at a distance from or above, the plane of the transition surface 43 and the circumferential flange 40is arranged, and the lower surface areas 56 lie in a plane that is generally parallel to, but at a distance from or below, the plane of the transition surface 43 and is arranged on the circumferential flange. The distance by which the elongated webs are spaced 50 and the lower surface areas 56 from the plane of the middle plane area 38 the intermediate plate 16 The distance by which the generally flat area is raised or recessed generally corresponds to the distance by which it is raised or recessed. 18 each of the outer plates 12 , 14 from the plane of the corresponding circumferential flange 20 The term "above" and "below" refers to the illustrative orientation of the intermediate plate. 16as shown in the drawings, and it is not intended that these terms should be interpreted as restrictive, since the person skilled in the art recognizes that the heat exchanger 10 It can be arranged upright or in different orientations.

[0042] A first set of flow passages 58 (as indicated by dashed flow direction arrows in the Fig. 5 and Fig. 6 is shown) is in the spaces or cavities that are below each of the elongated webs 50 are formed, formed, while a second set of flow passages 60 in the spaces or gaps between the elongated struts 50 through lower areas 56 are formed, is formed, so that the first and second flow passes 58 , 60 across the width of the middle, generally flat area 38 the intermediate plate 16 alternate each other.

[0043] The inlet and outlet distribution opening 34 , 36 will now be discussed in detail with reference to the Fig. 4– Fig. 6 described. The inlet and outlet distributor openings. 34 , 36 are in their respective forms 64 , 65 formed, which are generally identical to each other, but one of the forms 64 , 65 with reference to the other 64 , 65 is arranged in the opposite direction or vice versa. More precisely, if the in Fig. 3 or Fig. 4 View shown from top to bottom of the embodiment of the intermediate plate 16 The form is considered. 64 from the plane of the circumferential flange 40 upwards, while the expression 65 is formed as a depression and therefore rises from the plane of the circumferential flange 40protrudes downwards. The inlet and outlet distributor openings. 34 , 36 They therefore each have a sealing or contact surface. 66 , 67 , which are on opposite sides of the intermediate plate 16 to open the corresponding opening 34 , 36 are formed to face the corresponding surface of the corresponding outer plate 12 , 14 to seal when the panels 12 , 14 , 16 are assembled together to form the heat exchanger 10 to form a second sealing or contact surface. 68 , 69 is also one of the characteristics 64 , 65 formed, with the second sealing surface being at a distance from the corresponding opening 34 , 36 and the first contact surface 66 , 67 through trough areas 70 , 71 features. The trough areas 70 , 71only partially surround the corresponding inlet or outlet distribution opening. 34 , 36 and the first contact surface 66 , 67 and define another sealing or contact surface 72 , 73 for contacting and sealing against a corresponding area of ​​the corresponding outer plate 12 , 14 , when the plates 12 , 14 , 16 are composed of each other. Additionally, the first and second contact or sealing surfaces result in... 66 , 67 , 68 , 69 to be provided, which are provided by respective trough areas 70 , 71 have a mutual distance, with corresponding sealing or contact surfaces 72 , 73 , which are on the opposite side of the intermediate plate 16 from the corresponding first and second sealing surfaces 66 , 67 , 68 , 69are arranged, the characteristics 64 , 65 an overall stiffness through the plane to create a surface-to-surface seal between the intermediate plate 16 and the outer plates 12 , 14 to support the connection of the corresponding cooling openings. Therefore, while the inlet and outlet manifold openings are 34 , 36 and their respective forms 64 , 65 , the sealing surfaces 66 , 67 , 68 , 69 and trough areas 70 , 71 with sealing surfaces 72 , 73 , etc. have a similar structure, indicating that the features of one are arranged opposite each other with reference to the corresponding features of the other, as for example in the detailed views of the Fig. 4, Fig. 5, Fig. 6A is shown.

[0044] Several protrusions 74 , 75for example, in the form of indentations along one edge of the corresponding distributor opening. 34 , 36 formed. The advantages 74 , 75 exhibit a mutual distance, with the projections 74 , which is connected with the opening of the entrance distribution area 34 are associated as depressions that are formed in such a way that they extend downwards into the first cleft 26 extend between the intermediate plate 16 and the corresponding surface of the first outer plate 12 is formed. The protrusions 75 , which is connected to the outlet distributor opening 36 are associated, stand upwards in the second column 28 before, which is between the intermediate plate 16 and the corresponding surface of the second outer plate 14 is formed. Each of the protrusions 74 This therefore defines a contact or sealing surface. 76to seal against a corresponding area of ​​the first outer plate 12 , each of the individual sealing surfaces 76 therefore generally in the same plane as the contact or sealing surface 72 , which pass through the trough area 70 is defined, lies. Each of the protrusions also defines 75 a contact or sealing surface 77 , which are generally in the same plane as the contact or sealing surface 73 lies, which is through the corresponding trough area 71 is defined. Since the protrusions 74 , 75 , which are connected to each distributor opening 34 , 36 are associated, have a mutual distance, are column 78 , 79 between the adjacent projections 74 , 75 formed. Column 78 , 79 They serve as small flow passages that tend to pass through the fluid inlet distributor opening. 34into the heat exchanger 10 incoming and through the fluid outlet distributor opening 36 from the heat exchanger 10 escaping fluid onto respective distribution surfaces 80 , 82 , which are inside the heat exchanger 10 on each side of the intermediate plate 16 are formed in the columns, or areas that are between the transition surface 43 the intermediate plate 16 and the corresponding surface of the first and second outer plate 12 , 14 are created to distribute.

[0045] Since the middle, generally flat area 18 the first outer plate 12 a distance from the intermediate plate 16 features to close the first gap 26 Fluid flows between these, passing through the inlet distributor opening. 34 into the heat exchanger 10 enters through the openings 30 , 34, which are in the second outer plates 14 and the intermediate plate 16 , which are located at the contact surface 66 which are sealed together, and flow through the gap 78 , which are between the row of projections 74 , which against the first outer plate 12 seal, are formed, and into a first distribution area 80 , which are between the transition area 43 the intermediate plate 16 and the corresponding inner surface of the first outer plate 12 is formed, where the fluid then enters the first set of flow passes. 58 , which are between the intermediate plate 16 and the first outer plate 12 is formed by the elongated struts 50 is distributed. When the fluid passes through the first set of flow paths. 58Moving in a first longitudinal direction, the fluid draws heat from the battery cells or battery cell containers that are in contact with the primary heat exchange surface(s) or outer surface(s) of the heat exchanger. 10 are arranged. After the fluid has moved along the length of the first set of flow paths, 58 Once moved, it is driven by the intermediate plate 16 formed, open distribution channel 46 to a second distribution area 84 , which is formed by the space between the first and second outer plate 12 , 14 The formed open inner space is defined and delivered. See, for example, Fig. 7. The second distribution area 84 Fluidically connects the first set of flow passages 58 and the second set of flow passages 60 , which makes it possible to obtain data from the first flow passes 58escaping fluid into the adjacent second flow passages 60 enters. The second distribution area 84 This is made possible by the heat exchanger 10 flowing fluid, in order to 180 to be turned (e.g., redirected) and through the second flow passes 60 along the middle, generally flat surface 38 the intermediate plate 16 in a second flow direction, which is generally opposite to the first flow direction through the first flow passes 58 is to flow. This U-flow, which occurs in the second distribution area 84 is created, will be detailed in Fig. 7 by flow direction arrows 85 illustrated. As shown, the fluid flows through the first flow passes. 58 and then forms a U-shaped curve in the second distribution area 84 , before it passes through the second flow passages 60flows. Accordingly, the alternating arrangement of the first and second flow passes creates 58 , 60 across the width of the heat exchanger 10 a two-way flow path for the flow through the heat exchanger 10 fluid passing through. If the heat exchanger 10 For example, when used for cooling, the fluid enters the heat exchanger at a low temperature. 10 and gradually increases its temperature as it travels along the length of the first flow passes. 58 This occurs because the fluid draws heat from the battery cells or battery cell containers associated with the heat exchanger. Accordingly, the temperature of the fluid from the first flow passes is... 58 The outgoing fluid is higher than the temperature of the fluid entering the first flow passes. 58 incoming fluid, and therefore this is due to the second set of flow passages. 60The fluid passing through has a higher temperature than the fluid passing through the first set of flow passes. 58 Fluid passing through, which has already completed one passage through the heat exchanger. By the second fluid passages 60 by their alternating arrangement across the central, generally flat surface 38 the intermediate plate 16 with the first flow passes 58 If the flow is interleaved, the warmer fluid will be used in the second flow passes. 60 in thermal contact with the cooler fluid that passes through the first set of flow passages 58 through, brought about, whereby heat transfer occurs between the two sets of flow passages. 58 , 60 over the surface of the heat exchanger 10 This takes place. The introduction of the warmer fluid in the second set of flow passes. 60in thermal contact or heat transfer relationship with the fluid in the first set of flow passes 58 contributes to reducing the temperature difference across the primary heat transfer surface of the heat exchanger 10 to counteract this, which in turn contributes to adequate thermal management of the battery cells or battery cell containers that are in thermal contact with the heat exchanger 10 are arranged to ensure this. The close proximity of the first and second sets of flow passages also allows for this. 58 , 60 and the arrangement of the intermediate plate 16 , which are between both the first and second outer plates 12 , 14 and is arranged in thermal contact with these, forming a thermal conduction in the plane along the surface of the outer plates 12 , 14 , which also leads to a more uniform surface temperature across the heat exchanger 10contributes.

[0046] After that, through the heat exchanger 10 flowing fluid passes through the second set of flow passages 60 Once finished, the fluid leaves the second flow cycles. 60 and enters the third distribution area 82 one that lies between the transition area 43 the intermediate plate 16 and the second outer plate 14 is formed. The third distribution area 82 is therefore in fluid connection with the second flow passes 60 and also in fluid connection with the outlet distributor opening 36 between the several protrusions 75 formed column 79 .

[0047] While the preceding embodiment was described such that the first fluid flow passages occur in the first gap between the first side 15 the intermediate plate 16 and the first outer plate12 are formed and the second fluid flow passages in the second gap 28 , which is between the second side 17 the intermediate plate 16 and the second outer plate 14 is formed, are formed, wherein each of the first fluid flow passes and the second fluid flow passes is in fluid communication with its respective inlet or outlet distributor opening. 34 , 36 It should be noted that the first and second fluid flow passes and the inlet and outlet distributor opening 34 , 36 they can have the opposite configuration and that the fluid flow path described above passes through the heat exchanger 10 The opposite may be true depending on the specific application and / or the desired location of the special inlet / outlet fluid connections, as is understandable to a person skilled in the art.

[0048] Because of the alternating arrangement of the first and second flow passes 58 , 60 via a single level of the heat exchanger 10 a heat transfer between the adjacent first and second flow passes 58 , 60 This makes it possible to utilize any temperature difference between the fluid entering the heat exchanger. 10 enters and through the first flow passages 58 flows through it, and the fluid that passes through the second flow passages 60 from the heat exchanger 10 exits, through heat transfer between the adjacent flow passages 58 , 60 and through the conduit in the plane in the upper and lower outer plate 12 , 14 somewhat reduced. Accordingly, a more uniform temperature profile can be achieved across the outer surface or primary heat transfer area of ​​the heat exchanger. 10This can be achieved, which is generally preferred or considered desirable for thermal battery management applications.

[0049] In some embodiments, the first and second flow passes can 58 , 60 be provided with heat transfer enhancement features, such as a series of mutually spaced depressions or tongues extending along the side walls or side areas 54 and / or upper or lower areas 52 , 56 are formed, which together create the individual waves 50 in the middle, generally flat area 38 the intermediate plate 16 form. If desired, the indentations or tongues can be placed on the sides. 54 and / or upper and lower areas 52 , 56 be formed in such a way that they fit into the corresponding fluid flow passages 58 , 60protrude without mutual interference with the upper or lower areas 52 , 56 , which are connected to other records 12 , 14 are brazed or otherwise joined. In some embodiments, instead of using heat transfer reinforcement features, these can be incorporated as part of the surface of the intermediate plate. 16 are formed, separate ribs or turbulencers also within each of the fluid flow passages. 58 , 60 be arranged.

[0050] It will now be on Fig. 11 Reference is made to an alternative embodiment of the intermediate plate 16' shows, using the same reference numbers to identify similar characteristics as those above in conjunction with the Fig. 1– Fig. 10 described to identify. As in Fig. As shown in 11, these are, instead of the inlet and outlet distributor openings. 34 , 36at one of the opposite ends of the intermediate plate 16 to order the inlet and outlet distribution opening 34 , 36 instead, on one side of the middle, generally flat surface 38 the intermediate plate 16' arranged. Accordingly, in the present embodiment, the intermediate plate 16' a somewhat T-shaped base, with the inlet and outlet distributor openings 34 , 36 and their corresponding variations 64 , 65 from the edges of the middle, generally flat surface 38 the record 16' protrude outwards. Although this is not shown in the drawings, it should be noted that in the present embodiment the outer plates 12 , 14 have a similar T-shaped base to match the base of the intermediate plate 16' to comply when the plates 12 ,14 , 16' are assembled together to form the heat exchanger 10 to form.

[0051] The middle, generally flat surface 38 the intermediate plate 16' remains essentially unchanged in that it features a series of grooves or elongated ribs or ridges. 50 is equipped with the first and second sets of fluid flow passes 58 , 60 form areas that extend across the middle, generally flat surface 38 the record 16 alternate. However, instead of the transition area 43 between the inlet and outlet openings 34 , 36 and the wavy surface 38 as in the previously described embodiment, the transition surface 43 along the end 42 the intermediate plate 16'arranged and extends across the width of the central, generally flat surface 38 the intermediate plate 16' beyond, whereby they are linked to the respective characteristics 64 , 65 , which form the inlet and outlet distributors, is connected. The transition surface 43 therefore extends into the circumferential flange 40 , which determines the circumference of the intermediate plate 16' defines, and forms part of it.

[0052] As in the previously described embodiment, the inlet distributor opening 34 in its form 64 formed, which are formed from the plane of the circumferential flange 40 protrudes upwards, and the entrance distribution opening 34 is therefore from the first contact surface 66 surrounding, opposite the corresponding surface of the corresponding outer plate 14 seals. The trough area 70 partially surrounds the contact surface 66, whereby the trough area 70 a suitable contact or sealing surface 72 defined on the opposite side of this, in order to face the corresponding surface of the outer plate 14 to seal. In the present embodiment, the second sealing surface is located 68 not in the same plane as the first contact surface 66 (as in Fig. 5), but instead forms part of the circumferential flange 40 , which lies in a plane parallel to, but below, the first sealing surface 66 lies. A series of indentations or projections arranged at intervals from one another. 74 is along one edge of the inlet distributor opening 34 formed, which descend into the first gap 26 protruding, which is between the first outer plate 12 and the corresponding surface 15 the intermediate plate 16is formed, with each of the depressions or protrusions forming a contact surface 76 for sealing against the outer plate 12 defined. Gaps or flow spaces 78 are between the projections arranged at a distance from each other 74 formed, which creates a fluid connection between the inlet distributor opening 34 and the first distribution area 80 , which are between the transition area 43 and the corresponding surface of the outer plate 12 is formed, provide, whereby the first distribution area 80 the incoming fluid or coolant flow to the first set of fluid flow passes 58 , which are located under each of the elongated ribs 50 and the outer plate 12 are educated, leads.

[0053] The opposite end 44 the intermediate plate 16'is essentially identical to that of the previously described embodiment and has an elongated opening or channel 46 on, whereby the intermediate plate 16' and the outer plates 12 , 14 an open interior space or distribution area 84 form the outer ends of the fluid flow passages in terms of fluid flow. 58 and the inlets of the fluid flow passages 60 connects them, creating the U-flow, which forms the counterflow arrangement between the fluid flow passages. 58 , 60 results.

[0054] After the second set of fluid flow passes 50 Once the backflowing fluid or coolant of the second pass through the heat exchanger has ended, it is followed by the second fluid flow passes. 60 into the third distribution area 82 issued, which between the transition area43 the intermediate plate 16' and the corresponding surface of the second outer plate 14 is formed. From the third distribution area 82 The fluid or coolant is then directed to the outlet distributor opening. 36 , which are on the opposite side of the heat exchanger 10 is formed, directed. The outlet distributor opening. 36 is in its manifestation 65 formed, which are essentially identical to the one, but arranged in the opposite direction with regard to the form 64 is. Accordingly, the form 65 the first sealing surface 67 , which opens 36 on the first page 15 the intermediate plate 16' surrounds and the corresponding surface of the first outer plate 12 contacted and sealed against it. The trough area 71 surrounds the first sealing surface 67 partially and defines a sealing or contact surface73 on the opposite side of this, in order to face the corresponding surface of the second outer plate 14 to seal it. As with the inlet distributor opening. 34 The second sealing surface is located there 69 not in the same plane as the first sealing surface 67 , but instead extends into the circumferential flange 40 , which determines the circumference of the intermediate plate 16' forms, and forms a part of this, which lies in a plane generally parallel to but between the plane formed by the first sealing surface 67 is defined, and the sealing surface 73 , which pass through the trough area 71 is educated.

[0055] To the heat exchanger 10 using the intermediate plate 16' To form corresponding outer plates 12 , 14 provided with a corresponding base area, whereby the slabs 12 , 14 , 16'They are arranged one above the other in the same manner as described above to form the heat exchanger. 10 to form, whereby the outer plates 12 , 14 the first and second fluid flow passes 58 , 60 form and enclose when they are used together with the intermediate plate 16' to be stacked.

[0056] In use, for a heat exchanger 10 , which uses either the intermediate plate 16 or the alternative intermediate plate 16' The middle, generally flat area is formed 18 the outer plates 12 , 14Each serves as a primary heat transfer surface on which the individual battery cells or battery cell containers holding the individual battery cells are positioned / arranged. In the case of a cold plate heat exchanger, where several individual battery cells or individual battery cell containers holding the individual battery cells are stacked on the cold plate heat exchanger, only a central, generally flat area serves as a primary heat transfer surface. 18 the corresponding outer plate 12 , 14 as the primary heat transfer surface, and the thicknesses of the individual plates 12 , 14 , 16 They can be adapted to ensure that specific requirements for a cold plate application are met. In the case of an intercellular arrangement (ICE plate heat exchanger), where several individual heat exchangers are used. 10Provided and arranged between adjacent battery cells or adjacent battery cell containers, both middle, generally flat areas act 18 as primary heat transfer surfaces, since both surfaces are in contact and heat transfer relationship with the adjacent battery cell or battery cell container. The particular thickness of the individual plates 12 , 14 , 16 ( 16' ) and the specific size (e.g. width, length) of the first and second flow passes 58 , 60 can be adapted to suit the specific application.

[0057] By the outer plates 12 , 14 with medium, generally flat areas 18Since these are formed, which are typically free of surface interruptions and generally have a flat surface, they are also particularly suitable for thermal battery management applications, as the heat exchanger 10 provides an adequate surface area capable of achieving proper surface-to-surface contact with the battery cells or battery cell containers. This is also achieved by using external plates. 12 , 14 are used which are generally identical to each other, with one of the outer plates 12 , 14 with reference to the other of the outer plates 12 , 14 Conversely, if they are used together with the intermediate plate 16 , 16' are arranged, the production of the heat exchanger 10 somewhat simplified, as only a single mold is required for both outer plates 12 , 14to produce them, for example, when they are formed by stamping, while a second form is required to create the intermediate plate 16 to produce. In cases where the outer plates 12 , 14 as flat plates using a cutting process with a separate frame part that provides the fluid-tight seal with the intermediate plate 16 ( 16' ) forms, to be manufactured, only a single mold is required to create the intermediate plate 16 ( 16' ) to produce. By using only a single mold to create two separate parts (e.g., the outer plates). 12 , 14 ) to produce, or by using only a single shape (e.g. to create the intermediate plate) 16 , 16' to produce, whereby the outer plates 12 , 14(manufactured through a cutting process) manufacturing and / or tooling costs associated with the overall production of the heat exchanger may apply. 10 are associated with being downplayed.

[0058] It will now be referred to as Fig. 13– Fig. 16 Reference is made to another embodiment of a battery cooling counterflow heat exchanger 100 as shown in the present disclosure. As in the previously described embodiment, the heat exchanger has 100 a pair of outer plates 112 , 114 each of which has a central, generally flat area 118 have, each of which acts as a primary heat transfer surface of the heat exchanger 100 can be used to contact the corresponding battery cell(s) or battery cell container, which are either on the heat exchanger 100 stacked or adjacent to and in contact with its surfaces 118They can be arranged. A circumferential edge 120 generally extends perpendicular to the central, generally flat area 118 the plates 112 , 114 and extends around the perimeter of the central, generally flat area 118 from each of the records 112 , 114 to form a side wall. Accordingly, based on the in Fig. 13. The first or lowest outer plate is shown in the view / orientation shown. 112 a raised side wall or perimeter edge 120 , where the circumferential edge is separated from the inner surface of the plate 112 away upwards, while the second or uppermost outer plate 114 has a downward-sloping side wall where the circumferential edge 120 from the inner surface of the plate 114 extends downwards. Therefore, if the outer plates 112 , 114Arranged in their paired relationship, the end edges of the circumferential edges come together. 120 the plates 112 , 114 to each other to form an open inner space 117 between the mutually spaced, generally flat central areas 118 the respective plates 112 , 114 .

[0059] An intermediate plate 116 is between the first and second outer plate 112 , 114 arranged and occupies the main part of the open inner space between the paired outer plates 112 , 114 is formed, one. The intermediate plate 116 It has the form of a corrugated ribbed plate, which has several interconnected coils or elongated webs. 150 exhibits. As in the previously described embodiment, the coils or elongated webs have 150 each an upper surface area 152(or "comb") and a pair of side areas 154 on, with the elongated struts passing through lower surface areas 156 are connected to each other. Accordingly, when the intermediate plate 116 between the two outer plates 112 , 114 is arranged or clamped, the upper surface areas 152 in sealing contact with the corresponding inner surface of the upper or second outer plate 114 , while the lower surface areas 156 in sealing contact with the inner surface of the lower or first outer plate 112 This results in a first set of flow passages. 158 in the spaces between each of the elongated walkways 150 are arranged, i.e., in the gaps that are between the lower surface areas 156 and the corresponding inner surface of the upper or second outer plate 114are formed, formed, while a second set of flow passages 160 under each of the twists or elongated ridges 150 , i.e., in the gaps between the intermediate plate 116 and the corresponding inner surface of the first or lower outer plate 112 is formed. While the first set of flow passages 158 was described as being able to pass through the gap between the intermediate plate 116 and the corresponding inner surface of the second or upper outer plate 114 is formed, and the second set of flow passages 160 was described as being able to pass through the gap between the intermediate plate 116 and the first or lower outer plate 112 It should be noted that the opposite arrangement is also possible, depending on the specific design and / or application of the heat exchanger. 100 .

[0060] The intermediate plate 116 is dimensioned such that its length is not exactly the length of the space between the outer plates 112 , 114 formed open inner space 117 corresponds to a distribution area 184 at one end of the heat exchanger 100 is obtained, whereby fluid passing through the first fluid channels 158 passes through, from the canals 158 exits at its downstream or second end, which fluid then flows to the second set of flow channels 160 is transported, and the fluid is enabled to approximately 180 The direction is reversed or "switched back" when it leaves the first flow channels. 158 to the second or return flow channels 160 transitions.

[0061] For the heat exchanger 100 The incoming fluid is formed by the first and second outer plates. 112 , 114 each with a series of fluid openings130 , 132 formed, which are located at the corresponding ends of the plates 112 , 114 are formed. The rows of fluid openings 130 , 132 are such in the first and second outer plate 112 , 114 formed that the one in the second or upper outer plate 114 formed series of fluid openings 132 generally with the ones between the elongated struts 150 the intermediate plate 116 formed first flow passages 158 is aligned, while the one in the first or lower outer plate 112 formed fluid openings 130 generally with the second flow passes 160 , which are under the elongated walkways 150 and the inner surface of the outer plate 112 are educated, are aligned.

[0062] A first distributor 134in the form of an elongated part, which in the illustrated embodiment is generally rectangular with an open inner space 135 is, is above the series of fluid openings 130 , which are in the upper or second outer plate 114 are formed, arranged. A fluid opening 136 in the form of an inlet opening, it provides fluid access to the open inner space. 135 of the first distributor 134 ready, with the fluid subsequently going to the first fluid passes 158 via fluid openings 130 will be delivered.

[0063] A second distributor 138 also in the form of an elongated part that has an open inner space 135 defined, is on the outer surface of the first or lower outer plate 112 above the series of fluid openings formed therein 132 arranged. A fluid opening 140 (see e.g. Fig. 15) in the form of a fluid outlet opening serves to discharge fluid from the heat exchanger 100 , after passing through the second set of flow passes 160 to the open inner space 135 of the distributor 138 about openings 132 has passed through. Appropriate inlet and outlet fittings. 141 , 142 are within the fluid openings 136 , 140 of the first and second distributors 134 , 138 arranged to allow for adequate fluid lines to the heat exchanger 100 to be connected.

[0064] Since the one with the heat exchanger 100 The associated inlet and outlet manifold structure is quite simple; the manufacturing of the entire heat exchanger is straightforward. 100 This simplifies things, which can lead to cost savings. The simplified distribution structure also reduces costs. 134 , 138both for the inlet and outlet sides of the heat exchanger 100 The total area associated with the distributor allows for larger, generally flat surfaces (i.e., primary heat transfer surfaces) for contact with the corresponding battery cells or battery cell housings stacked on or in contact with them. Therefore, the structure of the heat exchanger 100 suitable for providing large contact areas with improved temperature uniformity across the surfaces that serve as the primary heat transfer surfaces of the heat exchanger 100 serve.

[0065] While that in the Fig. 13– Fig. The embodiment shown in 16 is suitable for applications where the inlet and outlet fitting 141 , 142 on opposite sides of the heat exchanger 100 are arranged, the heat exchanger can 100It can be modified to accommodate an inlet and an outlet fitting on the same side of the heat exchanger, as discussed in detail below.

[0066] It will now be referred to as Fig. 17– Fig. 18 referenced, in which a modified heat exchanger 100 shown, whose structure is similar to that of the above in conjunction with the Fig. 12– Fig. The heat exchanger described in 16 is such that it also has outer plates 112 , 114 with the corrugated intermediate plate arranged in between 116 features the outer plates 112 , 114 and the intermediate plate 116 have the same structure as in the previously described embodiment, wherein the intermediate plate 116 together with the first and second outer plates 112 , 114 a first set of flow passages 158 and a second set of flow passages160 forms when the plates are arranged or clamped together in their pairing relationship.

[0067] The first distributor 134 It also has the form of an elongated, generally rectangular part that sits above the row of parts in the upper or second outer plate. 114 formed fluid openings 132 is arranged. However, in the present embodiment, the first distributor extends 134 across the width of the slabs 112 , 114 , 116 , which the heat exchanger 100 form, out, so that the distributor 134 an extension area 161 has, which extends over the edge of the heat exchanger 100 protrudes at a distance D. The open inner space 135 , which is in the first distribution list 134 is formed to supply fluid to each of the fluid openings 130 to distribute, extends along the length of the first distributor. 134, but does not extend into the excellent area of ​​the first distributor 134 , so that the open inner space 135 at the corresponding end edges of the heat exchanger 100 ends.

[0068] The second distributor 138 It also depends on a corresponding distance D over the edge of the heat exchanger. 100(1) , including the second distributor 138 with an extension area 162 is formed, which extends upwards in such a way that it reaches the corresponding inner surface of the preceding extension area. 161 of the first distributor 134 hits or abuts it. An additional sealing element or spacer. 134 can be between the opposing contact surfaces of the protruding areas or extension areas 161 , 162 of the first distributor 134 and the second distributor 138must be arranged to ensure adequate contact between the two mated surfaces, together with a fluid-tight seal between the two distributor parts. 134 , 138 is achieved.

[0069] As in the previously described embodiment, the fluid opening 136 in the first distribution list 134 designed to provide fluid access to the open inner space 135 , which is in the first distribution list 134 is formed and is used to transport or distribute incoming fluid to each of the first fluid passes. 158 about in the outer plate 114 formed fluid openings 132 serves this purpose. Since the open inner space 135 of the first distributor 134 The fluid opening does not extend into the protruding area of ​​the distributor part. 136 at a location somewhere along the length of the open inner space 135arranged, which in the present embodiment is the width of the heat exchanger 100 corresponds.

[0070] Instead of in the outer surface of the second distributor 138 To be formed is the fluid opening 140 also in the first distribution list 134 formed. As shown, the fluid opening is 140 in the protruding or extension area 161 of the first distributor 134 so formed that they generally have openings 165 , 166 , which are in the spacer or sealing part 164 and the upper surface of the extension area 162 of the second distributor 138 are formed, is aligned. Those in the extension area 162 of the second distributor 138 formed fluid opening 166 establishes a fluid connection between the extension area 162 and the one in the second distribution list 138formed open inner space 135 ready.

[0071] During operation, fluid passes through the fluid opening. 136 into the heat exchanger 100 one and is spread across the open inner space 135 of the first distributor 134 and in the outer plate 114 formed fluid openings 132 to each of the first flow passes 158 distributed. The fluid flows along the length of the heat exchanger. 100 through the first set of flow passages 158 , until it reaches the distribution area 184 at the end of the intermediate plate 116 within the area defined by the paired outer plates 112 , 114 formed open inner space 117 reached where the fluid is allowed to turn around or flow back and enter the second set of flow passes. 160 to enter. Since the fluid passes through the second set of flow paths. 160As it flows, it enters into a heat transfer relationship with the incoming fluid, which passes through the first flow cycles. 158 Flows, brought. As in the previously described embodiment, this contributes to a more uniform surface temperature across the surfaces. 118 of the heat exchanger 100 to obtain, since there is additional heat transfer between the adjacent fluid passages 158 , 160 takes place, as the temperature of the fluid flow is affected by the first fluid flow passes. 158 The flowing fluid tends to be cooler than the temperature of the fluid passing through the second flow cycles. 160 flowing fluid that has already passed through the heat exchanger 100(1) has been completed. The alternating arrangement of the first and second flow passes. 158 , 160 over the surfaces 118 of the heat exchanger 100This "intermediate channel" heat transfer contributes to a more uniform surface temperature, which has been found to be desirable for the thermal management of the battery unit. Also, because of the heat exchanger... 10 , 100 Flowing fluid above and below the intermediate plate 116 flows, whereby the outer plates 112 , 114 Generally flat surfaces on both sides of the heat exchanger 10 , 100 provide the heat exchanger 10 , 100 able to provide two main or primary heat transfer surfaces for contact with battery cells or battery cell housings on each side of the heat exchanger 10 , 100 , 100(1) to provide, for example as an intercellular element or an ICE plate.

[0072] After the fluid has completed its second pass through the heat exchanger 100(1)through the second flow passes 160 Once finished, the fluid enters the open inner space. 135 of the second distributor 138 via the fluid openings 130 one. From this, the fluid is taken by the heat exchanger. 100 through aligned fluid openings 166 , 165 , which are in the extension area 162 of the second distributor 138 are formed via the extension channel 167 through the fluid outlet or opening 140 , which are in the first distribution list 134 is formed, issued. Since both the inlet and the outlets 136 , 140 in the first distribution list 134 This arrangement is particularly suitable for applications that require the inlet and outlet to be on the same side of the heat exchanger. 100 are arranged. The present heat exchanger also represents 100(1) , since the distributors 134 , 138Each has only a single row of fluid openings. 130 , 132 exhibiting features that are generally located on the respective sides of the heat exchanger 100(1) aligned with each other, an additional area in the central, generally flat areas 118 the outer plates 112 , 114 ready to allow additional contact with the corresponding battery cells or battery cell housings / containers.

[0073] While the in the Fig. 12– Fig. The intermediate plate is shown in the 18 illustrated embodiments. 116 to illustrate that it has the shape of a corrugated ribbed plate, with the coils or elongated webs 150 generally have a square cross-section, as schematically shown in Fig. Figure 19, in addition to the preceding figures, should be noted to show that the elongated bridges 150 They can have alternative forms, in which the side areas154 each of the elongated bridges 150 are angled, as schematically shown in Fig. Figure 20 shows that it is possible to change the size / width of the fluid channels. 158 , 160 optimized or tailored for a specific application. The size of the upper surface areas can also be adjusted. 152 and the lower surface areas 156 They can also be varied (see lengths L1, L2) if desired, to control flow paths. 158 , 160 to provide those that have the desired properties for a specific application. In other embodiments, the elongated webs can 150 be wavy or have a sinusoidal format, as for example in Fig. Figure 21 shows that these can serve to create or enhance turbulence in the fluid passing through them in order to improve heat transfer properties. Accordingly, it should be noted that the present disclosure does not relate to square or rectangular coils or elongated webs. 150 It should be limited.

[0074] In some embodiments, to control the fluid distribution to / from the area between the first and second flow passes 158 , 160 and their respective first or second distributor part 134 , 138 to increase the size of the fluid openings 130 , 132 , which are in the corresponding outer plates 112 , 114 are formed, so that a series of graduated openings are created. 130 , 132 , as schematically in Fig. 22 is illustrated, is provided.

[0075] During examples of heat exchanger designs 10 , 100 , 100(1) As described above, it should be noted that certain adaptations and modifications of the described embodiments are possible. Therefore, the embodiments discussed above should be considered illustrative and not limiting.

Claims

[1] Battery cell heat exchanger, which has: a main body region with opposite ends and a first and a second outer surface, each defining a primary heat transfer surface between the opposite ends, which main body region has: a first outer plate; a second outer plate; and an intermediate plate that is arranged between the first and the second outer plate; several first fluid flow passages formed within the main body region between the intermediate plate and one of the first and second outer plates, each of the first fluid flow passages having a first end for letting fluid into the first fluid flow passages and a second end for discharging fluid from the first fluid flow passages, the first and second ends defining a flow direction through the first fluid flow passages; several second fluid flow passages formed within the main body area between the intermediate plate and the other of the first and second outer plates, each of the second fluid flow passages having a first end for letting the fluid into the second fluid flow passages and a second end for discharging the fluid from the second fluid flow passages, the first and second ends defining a flow direction through the second fluid flow passages; an inlet distributor in fluid connection with the first ends of the several first fluid flow passages; an outlet distributor in fluid connection with the second ends of the several second fluid flow passages; wherein the first and second fluid flow passes are arranged such that they alternate over the main body region in such a way that the first fluid flow passes are in a heat transfer relationship with the second fluid flow passes; and wherein the second ends of the first fluid flow passes are in fluid communication with the first end of the second fluid flow passes, and the flow direction of the first fluid flow passes is therefore opposite to the flow direction of the second fluid flow passes. [2] Heat exchanger according to claim 1, wherein: the first outer plate has a central, generally flat area surrounded by a circumferential flange; the second outer plate has a central, generally flat area surrounded by a circumferential flange; and the intermediate plate has a central, generally flat surface surrounded by a circumferential flange, wherein the intermediate plate is arranged between the first and the second outer plate and the circumferential flanges of the outer plates are in sealing contact with the circumferential flange of the intermediate plate; where the intermediate plate has: a first end comprising an inlet distributor opening and an outlet distributor opening arranged adjacent to each other and aligned laterally along the width of the intermediate plate, and a transition surface extending along the width of the intermediate plate; a second end which has a distribution channel extending along the width of the intermediate plate and forming an open inner space with the first and second outer plates; several elongated webs formed in the central, generally flat surface of the intermediate plate, each of the elongated webs having an upper surface and a pair of side regions, and the elongated webs being connected to each other by lower regions; the several elongated webs extend between the transition surface and the distribution channel. [3] Heat exchanger according to claim 2, wherein the upper surface and the pair of side regions of the elongated webs form longitudinal gaps with the first outer plate, which form the first fluid flow passages; and wherein the elongated webs have a mutual distance through the lower regions, wherein the lower regions and the side regions of adjacent elongated webs form longitudinal gaps with the second outer plate, which form the second flow passages. [4] Heat exchanger according to claim 2, wherein the first fluid flow passages and the second fluid flow passages are connected to each other via the distribution channel formed in the intermediate plate. [5] Heat exchanger according to claim 2, which further comprises: a first distribution surface formed at one end of the main body area of ​​the heat exchanger between the intermediate plate and the first outer plate, fluidly connecting the inlet distributor and the first fluid flow passages; a second distribution surface formed at the opposite end of the main body area of ​​the heat exchanger, fluidically connecting the first fluid flow passages and the second fluid flow passages; and a third distribution surface formed between the intermediate plate and the second outer plate, generally above or aligned with the first distribution surface, wherein the third distribution surface connects the second fluid flow passages and the outlet distributor. [6] Heat exchanger according to claim 2, which further comprises: a first feature extending out of the plane of the circumferential flange of the intermediate plate in a first direction, with the inlet distributor opening being formed in the first feature; a second feature extending out of the plane of the circumferential flange of the intermediate plate in a second direction opposite to the first feature, with the outlet distributor opening being formed in the second feature; a first sealing surface that surrounds each of the inlet and outlet distributor openings in order to contact a respective one of the first and second outer plates; a second sealing surface that partially surrounds each of the inlet and outlet distribution openings and has a distance from the first sealing surfaces in order to contact each of the first and second outer plates. [7] Heat exchanger according to claim 2, wherein the transition surface of the first end of the intermediate plate extends in the same plane as the circumferential flange of the intermediate plate, whereby the transition surface has a distance from the first and the second outer plate. [8] Heat exchanger according to claim 1, wherein the primary heat transfer surfaces are designed for thermal contact with several battery cell housings, each accommodating one or more battery cells. [9] Heat exchanger according to claim 1, wherein the heat exchanger is arranged between and in thermal contact with adjacent battery cells or battery cell housings. [10] Heat exchanger according to claim 1, wherein the inlet and outlet distributors are arranged laterally adjacent to each other at one end of the heat exchanger. [11] Heat exchanger according to claim 1, wherein the inlet and outlet distributors are arranged on opposite side edges of the main body area of ​​the heat exchanger. [12] Heat exchanger according to claim 11, in which a first distribution surface formed between the intermediate plate and one of the outer plates fluidly connects the inlet distributor and the first fluid flow passages to each other; and in which a further distribution surface formed between the intermediate plate and the other of the outer plates fluidly connects the outlet distributor and the second fluid flow passages to each other. [13] Heat exchanger according to claim 12, wherein the first distribution surface and the further distribution surface are arranged at one end of the heat exchanger and extend along its width. [14] Heat exchanger according to claim 1, wherein the first and second fluid flow passages further have heat transfer enhancement features formed thereon, the heat transfer enhancement features being selected from one of the following alternatives: recesses, ribs or tongues. [15] Heat exchanger according to claim 1, wherein the first outer plate has a central, generally flat area surrounded by a circumferential edge in the form of a side wall; the second outer plate has a central, generally flat area surrounded by a circumferential edge in the form of a side wall; and the intermediate plate is a corrugated plate having several elongated webs, each of which has an upper surface area and a pair of side areas, the elongated webs being spaced apart from each other and connected to each other by lower surface areas, and the elongated webs of the intermediate plate forming the several first and second flow passages together with the first and second outer plates; wherein the intermediate plate has a length that is smaller than the first and the second outer plate, which form a distribution area at the end thereof to provide a fluid connection between the second ends of the first flow passages and the first ends of the second flow passages. [16] Heat exchanger according to claim 15, which further comprises: several openings formed in the first outer plate at one end thereof, the several openings providing a fluid connection between the inlet distributor and one of the several first flow passages and several second fluid flow passages; several openings formed in the second outer plate at one end thereof, the several second openings providing a fluid connection between the outlet distributor and the other of the several first flow passages and several second fluid flow passages; wherein the inlet and outlet distributors are elongated parts with an open inner space formed therein, which elongated parts are arranged over the several openings in the first and second outer plates and seal around them. [17] Heat exchanger according to claim 16, wherein the inlet and outlet distributors are arranged on opposite sides of the heat exchanger. [18] Heat exchanger according to claim 16, wherein: the inlet and outlet distributors each have an extension area that extends beyond the width of the heat exchanger; a first fluid opening in a manifold formed by the inlet and outlet manifolds to provide fluid access to the open inner space formed therein; a second fluid opening is formed in the extension area of ​​the one of the inlet distributor and the outlet distributor to establish a fluid connection with the extension area of ​​the other of the inlet distributor and the outlet distributor, wherein the open inner space of the one of the inlet distributor and the outlet distributor ends before the extension area; The extension area of ​​the other by the inlet distributor and the outlet distributor has an extension channel formed therein to provide a fluid connection between the second fluid opening formed in the one by the inlet distributor and the outlet distributor, and the open inner space formed in the other by the inlet and the outlet distributor. [19] Heat exchanger according to claim 16, in which a first fluid opening is formed in the inlet manifold to provide fluid access to the open inner space formed therein; and a second fluid opening is formed in the outlet manifold to provide fluid access to the open inner space of the outlet manifold. [20] Heat exchanger according to claim 15, wherein the elongated webs forming the intermediate plate have one of the following alternative formats: generally square or rectangular longitudinal coils, sinusoidal or wavy longitudinal coils, or longitudinal coils with angled side regions. [21] Heat exchanger according to claim 16, wherein the multiple openings formed in the first and the second outer plate have gradually increasing diameters over the width of the plates.

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