Heat exchanger consisting of plates connected to each other

Abstract

The invention relates to a heat exchanger composed of plate elements connected to one another. The heat exchanger has a plurality of plate elements connected to one another, wherein between them cavities are formed which are separated from the surroundings, which are alternately flowed through by a first and a second medium via inlet and outlet lines, wherein the plate elements have a respective pair of openings as inlet and outlet lines, wherein the plate elements are configured such that between the respective corrugation profiles of the plate elements connection sites occur in which the plate elements are fastened to one another, wherein the corrugation profiles of the plate elements and their connection sites are configured such that the flow of the first and second medium between the plate elements from the respective inlet line to the respective outlet line extends non-linearly, wherein the plate elements each have a first corrugation profile which extends substantially transversely to the main flow direction, wherein the openings are each surrounded by a second corrugation profile.

Description

Technical Field

[0001] This invention relates to a heat exchanger, preferably for use in motor vehicles, comprising interconnected plates, according to the category of the independent patent claims. Furthermore, a method for manufacturing a heat exchanger according to the category of the parallel patent claims and an application of a heat exchanger according to the category of the parallel patent claims are also claimed. Background Technology

[0002] Printed document DE 10 2004 036 951 A1 discloses a heat exchanger composed of interconnected plates. The disclosed heat exchanger for motor vehicles is formed by interconnected plates, wherein outwardly closed cavities are formed between the plates, and these cavities are alternately traversed by first and second media via at least one inlet and one outlet channel, respectively. The plates are corrugated (heterogeneous) such that connecting portions (contact portions) appear between the corresponding corrugated profiles (heterogeneous profiles) of the plates, in which the plates are fastened together. The disclosed plates are corrugated and their connecting portions are configured such that the flow of the first and second media between the plates from the corresponding inlet channel to the corresponding outlet channel is non-linear. The disclosed plates have repeating corrugated profiles that extend substantially transversely to the main flow direction and are particularly corrugated in a zigzag pattern around the extension direction. The disclosed heat exchanger plates each have a pair of openings (holes) perpendicular to the plate plane as inlet and outlet paths, wherein these openings are raised relative to the plate plane (base plane), and one of the two openings alternately has a fluid-technical connection only to every other cavity (internal space of the plate). At least a portion of the openings is surrounded by a non-corrugated region, preferably in an annular shape. These regions are not supported on adjacent plates. The disclosed heat exchanger is traversed by two media, the pressures of which load the surface of the plates, and particularly the unsupported non-corrugated regions. To reduce pressure loss within the heat exchanger, the openings are typically enlarged. This disadvantageously increases the area of ​​the non-corrugated region surrounding the openings, and thus the unsupported area of ​​the plates, thereby adversely reducing the strength of the heat exchanger. Furthermore, this also reduces the corrugated profile of the sheet metal, thereby increasing the area of ​​the sheet metal without corrugated profile, which in turn reduces the strength-enhancing effect of the corrugated profile and reduces the strength of the heat exchanger. Summary of the Invention

[0003] The objective of this invention is to improve the heat exchanger in terms of strength and to reduce pressure loss within the heat exchanger.

[0004] The subject of this invention is a heat exchanger having two fluidically separated flow paths for two media that transfer heat to each other. The heat exchanger has plates that are alternately stacked on top of each other in a block-like arrangement. These plates are connected to each other. The heat exchanger according to the invention can be used in a refrigerant circuit, a coolant circuit, or both as a refrigerator. Heat exchangers having interconnected, stacked, or side-by-side plates are known. The heat exchanger according to the invention can have two fluidically separated flow paths for two media that transfer heat to each other; particularly preferably, the heat exchanger has only two fluidly separated flow paths. The first medium can be a single-phase refrigerant or preferably a two-phase refrigerant, which can have a gaseous phase and a liquid phase. Two-phase refrigerants such as R1234yf, R134a, carbon dioxide (R744), or propane (R290) can be used as the first medium, for example. The second medium can be a coolant based on a water-glycol mixture. Preferably, the heat exchanger has only two media. Each of these two media has a pressure that is applied to the surface of the plate. These two pressures are typically different in magnitude. Furthermore, it has been discussed that refrigerants currently used in refrigerant circuits, such as R1234yf or R134a, are prohibited. This is because currently used refrigerants have high greenhouse effect potential values, which deplete the ozone layer and contain permanent chemicals. Permanent chemicals are aliphatic organic compounds in which at least one carbon atom on the carbon skeleton has been completely replaced by a fluorine atom. These permanent chemicals or their degradation products are very persistent in the natural environment and can pose health hazards to humans and animals. Two-phase refrigerants carbon dioxide (R744) or propane (R290) can be used as alternatives. These two refrigerants can have pressures up to three times higher than currently used refrigerants, which further increases the load on the plate and may require a further unfavorable increase in plate wall thickness.

[0005] Cavities are constructed between two adjacent plates, fluidly sealed from the surrounding environment. These cavities are alternately traversed by two media. The first and second media flow alternately through these cavities via at least one inlet and one outlet path, respectively. Each plate has a pair of openings perpendicular to its plane as the inlet and outlet paths. The two media transfer heat to each other via the surfaces of the plates. Each cavity is assigned to one of two flow paths. Each plate has openings through which the two media are distributed onto the cavities and collected again. These openings are arranged such that it is possible to arrange the plates with corresponding 180° rotations relative to each other. The openings of adjacent plates are concentrically arranged. Channels are formed between two adjacent plates, each assigned to one of the two flow paths. The plates are stacked or arranged side-by-side to form a block. The plates can also be stacked into a block. Within the block, plates of varying geometries can be arranged, enabling the medium to be redirected or blocked along the plate stack. These plates can each have a rectangular shape. Preferably, these plates each have a rectangular shape including either a longer or shorter side. Alternatively, it is conceivable that these plates each have two sides of equal length. The thickness of these plates corresponds to the thickness of the material. These plates each have a plate plane, which can coincide with the base plane. Plates without additional functions are geometrically identical. The heat exchanger can have a stacking direction extending along the block.

[0006] In a block, plates arranged stacked or side-by-side are directly adjacent to each other. Connection points exist between two adjacent plates, where the plates are connected to each other. Two media exert pressure on each plate. These two pressures are typically different. Because the plates arranged in the block are subjected to pressure loads from both media on their surfaces, the plates are loaded with at least the difference between these two pressures. This is especially true in areas adjacent to openings and at connection points between plates adjacent to openings. Therefore, these areas of the plates have lower strength than the plate plane. Furthermore, the areas of the plates adjacent to openings are non-corrugated, thus eliminating the strength-enhancing effect of corrugated profiles in these areas, further reducing the strength of the plates and the heat exchanger. Additionally, the openings in the plates are chosen to be as large as possible to minimize pressure losses within the heat exchanger through the larger through-surface area of ​​the openings and, consequently, the channels. This unfavorably increases the area of ​​the non-corrugated profile surrounding the openings. This further reduces the strength of these plates, and consequently, the heat exchanger.

[0007] These two media can flow through the plate or cavity, either parallel to one side of the plate or diagonally opposite to one side of the plate. This direction can be the main flow direction of the media. The flow directions of the two media can be in the same direction or opposite to each other. A first cavity, fluidly connected to each other, is assigned to a first flow path for the first media to flow through the heat exchanger according to the invention. A second cavity, fluidly connected to each other, is assigned to a second flow path for the second media to flow through the heat exchanger according to the invention. These two flow paths are fluidly separated from each other.

[0008] "Concentric" is understood as geometric shapes (e.g., circles) having the same center point and thus being arranged substantially symmetrically around a common center point. A motor vehicle is a land vehicle that moves by mechanical force without being constrained by tracks. "Substantially" is understood as a deviation of ±10% in mass flow rate. "Substantially" is understood as an angular deviation of ±10° and a length deviation of ±1mm. "Technically separated by fluids" is understood as no medium or only a negligible amount of medium passing through the connection. "Hydraulic diameter" is a calculation parameter used when the cross-section of a pipe or channel deviates from a circle. The hydraulic diameter can be used, for example, to calculate pressure loss in a flow path or the flow rate of a medium in a flow path. Pressure loss is the pressure difference that occurs and may be related to the cross-section of the channel or pipe and the pressure, because a cross-section that is too small acts like a throttling device. Pressure loss in a refrigerant circuit can have an undesirable effect on the boiling point of the medium or refrigerant used. Pressure loss increases exponentially with the mass flow rate of the medium. Pressure loss corresponds to energy loss. The mass flow rate of a medium describes the rate of a specific mass movement of the medium over a period of time. A "flow path" is defined as the fluid-technical connection between two regions of the medium, for example, in a refrigerant circuit, and describes the segment through which the medium flows through a heat exchanger or a refrigerant circuit and / or a coolant circuit. When the required power of the heat exchanger is low, the mass flow rate of the first medium through the heat exchanger along the first flow path is also low. "Strength" is understood as the mechanical load-bearing capacity of one of the plates until the plate, and consequently the heat exchanger, fails. Fracture or excessive residual deformation of one or more plates can, for example, cause such failure. "Loading" refers to all external force parameters (forces and moments) acting on a component such as a plate or cover, as well as imposed deformation (displacement, temperature-induced, and length changes caused by constraints). "Pressure" is a force distributed over a surface and can consist of the pressure of the medium (operating pressure) and a component caused by the local flow conditions of the medium in the heat exchanger according to the invention. This causes the plates or the connections between plates to be subjected to pressure or tensile loads. Under compressive load, a component is compressed by the applied force or load. Under tensile load, components are pulled apart by the applied force or load. "Stiffness" describes a component's resistance to elastic deformation caused by external loads (forces or torques). Stiffness may be related to the component's material and / or shape.

[0009] The power of a heat exchanger corresponds to the energy transferred between the two media based on heat. In particular, the temperature difference is related to the input temperature, and especially to the flow guidance of the two media in the heat exchanger, such as cross-flow. The flow of the two media in the cavity can be in the same direction or in opposite directions.

[0010] The subject of this invention is a heat exchanger preferably used in motor vehicles. The heat exchanger according to the invention has at least two fluidically separated flow paths for two media, thereby allowing heat transfer between the two media. These at least two flow paths extend inside the heat exchanger, with each medium flowing through the heat exchanger along one of these two flow paths. The heat exchanger according to the invention is an indirect heat exchanger. This is because the two media are spatially separated from each other, and heat is transferred via heat-permeable walls, each formed by the surface of a plate.

[0011] According to the invention, the claimed heat exchanger, preferably for motor vehicles, comprises: a plurality of interconnected plates, wherein cavities fluidically separated from the surrounding environment are formed between these plates, through which first and second media alternately flow via at least one inlet and one outlet line, respectively, wherein each plate has a pair of openings perpendicular to the plate plane as the inlet and outlet lines, wherein the plates are configured such that connecting portions appear between corresponding corrugated profiles of the plates, wherein the plates are fastened together in the regions of these connecting portions, wherein the corrugated profiles of the plates and their connecting portions are configured such that the flow of the first and second media between these plates from the corresponding inlet to the corresponding outlet line is non-linear, wherein each plate has a repeating first corrugated profile extending substantially transversely to the main flow direction and, particularly, corrugated in a zigzag pattern around the extension direction, wherein the openings are respectively surrounded by second corrugated profiles. The main flow direction essentially corresponds to the flow of the first and second media from their respective inlet and outlet lines between the plates. Connection points appear at the second corrugated profiles of two adjacent plates. At these connection points, the areas adjacent to the openings are supported on the adjacent plates, thereby increasing the strength of the plates. Furthermore, the second corrugated profile surrounding the openings reduces the unsupported areas of the plates, further enhancing their strength. The flow of media through the openings is unimpeded. Additionally, the shape of the second corrugated profile increases the areal density of the connection points between the two plates, and these connection points are closer to the center point of the openings. This also reduces the area of ​​the plate plane without corrugated profiles adjacent to the openings, further increasing the strength of the plates. Furthermore, with an increased through-surface area of ​​the plates for both media, an undesirable increase in the area of ​​the plate plane without corrugated profiles can be advantageously avoided, thereby reducing pressure loss in the heat exchanger while also preventing an undesirable reduction in plate strength. One of the openings can be directly adjacent to the second corrugated profile.

[0012] The term "zigzag" is understood as a geometric shape that is implemented as lines that bend alternately with concave and convex angles.

[0013] By employing two corrugated profiles on the plates, the cavity between two adjacent plates can be divided into multiple channels. The surface area of ​​the plates available for heat exchange can be increased due to these two corrugated profiles. The larger surface area of ​​the plates allows for increased power of the heat exchanger. Furthermore, the rigidity of the plates can be increased by these two corrugated profiles, and the strength of the plates is enhanced by the increased number of connections between adjacent plates. The individual profiles of the first corrugated profile can be arranged staggered or non-linearly to generate turbulence or eddies in the flow of the two media, thereby further improving heat transfer between the two media. The first corrugated profile can be configured as an embossed profile with multiple elongated ridges and / or recesses, formed in a portion of the plate plane between openings. The profiles constituting the first corrugated profile can be embossed or otherwise formed regions, thereby obtaining a profile with ridges and / or recesses. These profiles can be, for example, wavy in cross-section. For example, these profiles can be formed by rolled edges or grooved ridges. The first corrugated profile can have a specific pattern as known in the field of plates used in heat exchangers. Furthermore, both corrugated profiles increase the strength of the plate because they have a reinforcing effect on the plate.

[0014] In a first advantageous embodiment of the heat exchanger according to the invention, the profiles of the second corrugated profiles can be configured substantially orthogonal to the enclosed openings. These openings can be defined by closed, continuous curves, to which the profiles of the second corrugated profiles can be arranged orthogonally. The profiles of the second corrugated profiles can each have an elongated shape and be configured substantially straight. For example, the profiles of the second corrugated profiles can be constructed as elongated, straight recesses or ridges relative to the plane of the plate, such that adjacent plates can be supported on the second corrugated profiles, and multiple connection points appear on the second corrugated profiles of two adjacent plates. This method advantageously further increases the strength of the plates.

[0015] Particularly preferably, the first and second corrugated profiles can be connected to each other, thereby creating continuous, heterogeneous regions of the plate. This advantageously increases the surface area of ​​the plate available for heat transfer between the two media. Furthermore, this enhances the strength of the first and second corrugations, thereby improving the strength of the plate and the heat exchanger according to the invention.

[0016] In another design of the invention, the second corrugated profile can respectively surround the corresponding opening in a star shape. The openings can be respectively bounded by a closed, continuous curve, and the corresponding profiles of the second corrugated profile can be arranged in a star shape relative to this curve. "Star-shaped" is understood to mean that straight lines can be drawn from the center point of the opening to all points or positions of the second corrugated profile. This avoids the corrugated profiles adjacent to the openings from exhibiting an arched shape, thereby increasing the surface density of the support portion between two adjacent plates, thus further improving the strength of the plates.

[0017] According to the invention, a portion of the openings is surrounded by arches, which bulge relative to the plate plane in such a way that one of the two openings is alternately fluidically connected to only every other cavity. This ensures that the cavities are alternately traversed by two media. Accordingly, two adjacent cavities can be fluidly separated from each other. Furthermore, the cavities can be fluidly separated from their surroundings. The arches can be connected to adjacent plates, thus forming a connection between two adjacent plates at that location. The arches can be constructed as rolled-edge bulges or recesses and have a closed shape. The arches can extend along the stacking direction.

[0018] According to the present invention, the arches can be respectively arranged between the opening and the second corrugated profile, wherein the arches and the second corrugated profile can be respectively connected to each other. This increases the surface area of ​​the plate available for heat transfer between the two media. Furthermore, it improves the lifting strength of both corrugated profiles because it avoids large flat areas in the plate. For example, each profile of the second corrugated profile can extend into the arch.

[0019] In another design of the invention, a portion of the openings is surrounded by a non-corrugated profile region, which is arranged between the surrounded opening and a second corrugated profile. Therefore, the non-corrugated profile region can be flat and may not have a profile. The arches of adjacent plates can be connected to the non-corrugated profile regions, and connection points can appear between the arches and the non-corrugated profile regions. This establishes a fluid-tight connection between the two cavities. This enables the simple and inexpensive manufacture of the claimed heat exchanger.

[0020] In another design embodiment of the invention, the openings may each have a diameter of 10mm. 2 Up to 500mm 2 For the through surface of the medium, the openings are preferably each 200mm in size. 2 Up to 300mm 2The through-face is the surface facing the medium. The through-face can be constructed substantially perpendicular to the plate plane. The large through-face of the opening ensures that the heat exchanger being protected has no pressure loss. Because the second corrugated profile surrounds the opening, the area adjacent to the opening can be supported on adjacent plates. "Through-face" is also understood as the hydraulic diameter of the opening. The unit of measurement for the through-face of the protected area is square millimeters in the metric decimal system.

[0021] Preferably, these openings can each be substantially circular. These openings are each bounded by a circular curve. This enables the simple and inexpensive manufacture of the heat exchanger requiring protection.

[0022] Particularly preferably, the first corrugated profile can be configured to differ geometrically from the second corrugated profile, wherein these plates can be integrally formed. The first corrugated profile can, for example, be zigzag-shaped around the direction of extension, and the second corrugated profile can, for example, be star-shaped, thereby making the two corrugated profiles geometrically different and thus giving the plates higher strength. The integral plate enables simple and inexpensive manufacturing of the heat exchanger requiring protection.

[0023] The connection points at the second corrugated profiles of two adjacent plates can be constructed substantially linearly, while the connection points at the first corrugated profiles of two adjacent plates can be constructed substantially point-like. Because the second corrugated profiles of two adjacent plates are orthogonal to their respective openings and arranged in a star-like pattern, are elongated, and substantially coincide even when adjacent plates are twisted, a substantially linear connection point can be formed between the second corrugated profiles of two adjacent plates. Because the first corrugated profiles of two adjacent plates are zigzag-shaped and do not coincide due to the twisting of the plates, the connection points between the first corrugated profiles can be constructed substantially point-like. This allows for a good and stable connection between adjacent plates.

[0024] In another embodiment of the invention, the areal density of the connection portions constructed at the second corrugated profiles of two adjacent plates is greater than the areal density of the connection portions constructed at the first corrugated profiles of two adjacent plates. This reduces the size of unsupported areas, thereby increasing the strength of the plates. Furthermore, the stiffness of the heat exchanger according to the invention can be increased by a large number of connection portions, which further enhances the strength of the heat exchanger. "Area density of connection portions" is understood to refer to the number of connection portions and / or the total surface area of ​​the connection portions.

[0025] In a second embodiment of the heat exchanger according to the invention, the plates may each have two first openings, and each plate may each have two second openings. The plates may each have four spaced-apart second corrugated profiles, and each plate may each have a first corrugated profile. These four second corrugated profiles may be continuously formed with the first corrugated profiles. The plates may each have a longer side and a shorter side, and two openings may be arranged along the shorter side. One of the first openings may be surrounded by an arch. Another first opening may be surrounded by a region without a corrugated profile. One of the second openings may be surrounded by an arch. Another second opening may be surrounded by another region without a corrugated profile. The four second corrugated profiles, the first corrugated profiles, the two arches, and the circumferentially upward-pulled edges may each be formed along the stacking direction.

[0026] The method for manufacturing the heat exchanger according to the invention comprises the following steps: embossing and / or stamping out plates, thereby simultaneously producing at least two corrugated profiles; additionally, openings may be created in the same or another step, for example, by cutting; followed by stacking these plates vertically, preferably by twisting two adjacent plates 180° relative to each other; and then fastening the adjacent plates at the connection points between the two adjacent plates, preferably by material locking, and particularly preferably by brazing. Here, the connection achieved by brazing can be particularly achieved by sealing the plates together at their edges, and especially by simultaneously connecting adjacent plates at the connection points of the two corrugated profiles. Additionally, the connection of adjacent plates at the connection points from the arch to the adjacent plate plane can be performed. Thus, in a particularly advantageous embodiment, a rigid heat exchanger with high strength is produced.

[0027] In another embodiment of the invention, the plates can be joined together by material locking at the joints. It is conceivable that these plates are joined by brazing. For this purpose, the plates can be plated with brazing filler metal. Alternatively, it is conceivable that these plates are joined together by adhesive. For this purpose, the plates can be coated accordingly.

[0028] Particularly preferred are these plates, which are identical, wherein two adjacent plates are stacked or arranged side by side with their respective plates twisted 180°. The plates may be geometrically identical.

[0029] In another embodiment of the invention, the plates may each have a first metallic material. Particularly preferred is that the first metallic material is an aluminum alloy. This material has the advantages of low density, high thermal conductivity, and the ability to easily produce a corrugated profile, for example, through embossing.

[0030] In another embodiment of the invention, an additional cover plate may be arranged at one end of the block. It is conceivable that this additional cover plate has a wall thickness greater than or equal to the wall thickness of these plates. This additional end plate may be made of a first metallic material.

[0031] In another embodiment of the invention, an additional end plate may be arranged at one end of the block. This end plate may have at least one inlet and one outlet line for each of the two media. It is conceivable that the additional end plate has a wall thickness greater than or equal to the wall thickness of these plates. The additional end plate may be made of a first metallic material.

[0032] In another embodiment of the invention, the heat exchanger may have at least one partition plate or deflector plate. At least one partition plate or deflector plate may be arranged in a stack of plates. This allows the medium to be deflected or blocked at least once along the height of the stack. The partition plate may be manufactured, for example, by stamping out openings in the plates. It is conceivable that at least one partition plate has a wall thickness greater than or equal to the wall thickness of the plates.

[0033] In another embodiment of the invention, the plates may each have a circumferentially upward-curving edge. At this edge, two adjacent plates can be connected to each other, thus fluidly separating the cavity between the two adjacent plates from the surrounding environment. When the plates are stacked or arranged side by side, they can be piled up on top of each other by means of the edges, thus facilitating their fixation before heat exchanger assembly.

[0034] In another design of the present invention, the through surfaces of the openings can be of the same size.

[0035] In another embodiment of the invention, the hydraulic diameter of at least one first opening may be substantially the same as the hydraulic diameter of at least one second opening.

[0036] According to the present invention, the refrigerant circuit or coolant circuit for motor vehicles preferably has at least one heat exchanger according to the present invention.

[0037] In a first application according to the invention, the heat exchanger according to the invention can be used in a refrigerant circuit of a motor vehicle. The refrigerant circuit according to the invention is traversed by a two-phase refrigerant as the first medium. This two-phase refrigerant has a liquid phase and a gaseous phase, and can be, for example, carbon dioxide (R744) or propane (R290). The second medium can be, for example, a mixture of ethylene glycol and water. The refrigerant circuit according to the invention can have at least one (first) heat exchanger according to the invention, a compressor, an expansion valve, and another (second) heat exchanger. The heat exchanger according to the invention can be arranged downstream of the expansion valve. In this case, the first heat exchanger according to the invention can operate as an evaporator. Here, the refrigerant (first medium) evaporates at the coolant (second medium), and heat is transferred from the coolant to the refrigerant. In the compressor, at least a majority of the vaporized refrigerant (first medium) is compressed. The second heat exchanger can operate as a condenser in such a way that heat is transferred from the hot vaporized refrigerant (first medium) to another medium, in which the refrigerant (first medium) condenses at the other medium. Another medium can be, for example, air, and the second heat exchanger is a direct heat exchanger. Liquid, cold refrigerant (the first medium) is depressurized in the expansion valve and flows back to the first heat exchanger according to the invention. The refrigerant (the first medium) flows through the first cavity of the heat exchanger according to the invention, and the coolant (the second medium) flows through the second cavity, thus transferring heat to each other. Because the plates have two corrugated profiles that are geometrically different from each other, the second corrugated profiles respectively star-shaped surround the openings, and the areas of the plates adjacent to the openings are respectively supported on adjacent plates. This results in the claimed heat exchanger having sufficiently high strength. Furthermore, the openings have a sufficiently large through surface, thereby resulting in a sufficiently small pressure loss in the (first) heat exchanger according to the invention.

[0038] In a second application according to the invention, the heat exchanger according to the invention can be used in the coolant circuit of a motor vehicle. The coolant circuit according to the invention can include a heat source, coolant, the heat exchanger according to the invention, a pump, and an expansion valve. It is conceivable that the heat exchanger according to the invention can be used as an oil cooler. To prevent the oil from aging in the motor vehicle, it is necessary to discharge heat as constantly as possible. In the heat exchanger according to the invention, the heat of the oil (second medium) can be transferred to the coolant (first medium). For example, a mixture of ethylene glycol and water can be used as the coolant. The coolant can flow through the coolant circuit by means of a pump. The pump generates pressure that carries the coolant from the heat source to the heat exchanger according to the invention and back. The coolant (first medium) flows through a first flow path, and the oil (second medium) flows through a second flow path, and thus they transfer heat to each other. Because the plates have two corrugated profiles that are geometrically different from each other, namely, the second corrugated profiles respectively surround the openings in a star shape, and the areas of the plates adjacent to the openings are respectively supported on adjacent plates. This makes the claimed heat exchanger have sufficiently high strength. In addition, the opening is made to have a sufficiently large through surface, thereby ensuring that the heat exchanger to be protected has a sufficiently small pressure loss.

[0039] In a third application according to the invention, the heat exchanger according to the invention can be used accordingly in the coolant circulation loop and refrigerant circulation loop of a motor vehicle. The motor vehicle may have a drive system that is at least partially electric. Coolant can flow through the coolant circulation loop according to the invention, which is a mixture of water and ethylene glycol. The refrigerant circulation loop according to the invention can be traversed by a two-phase refrigerant. Carbon dioxide (R744) or propane (R744) can be used as the refrigerant. In a motor vehicle with a drive system that is at least partially electric, the battery and the electric drive motor should always be maintained at a constant temperature level in order to achieve the longest possible service life for both components and to obtain the full power of both components. In cases where the ambient temperature is high, it is possible that the power of the cooler in the coolant circulation loop is insufficient for this task. In this case, a first flow path of the heat exchanger according to the invention can be connected to the refrigerant loop, and a second flow path can be connected to the coolant loop. The refrigerant (first medium) flows through the first flow path, and the coolant (second medium) flows through the second flow path and transfers heat between them. Because the refrigerant (first medium) is colder than the coolant, the coolant (second medium) is cooled to a temperature low enough that the battery and drive motor can be maintained at a constant temperature. Therefore, the heat exchanger according to the invention is used as a refrigerator. Because the plates have two corrugated profiles that are geometrically different from each other, namely, the second corrugated profiles respectively surround the opening in a star shape, and the regions of the plates adjacent to the openings are respectively supported on adjacent plates, the claimed heat exchanger has sufficiently high strength. Furthermore, the opening has a sufficiently large through surface, thereby making the claimed heat exchanger have sufficiently low pressure loss. Attached Figure Description

[0040] Other details and advantages of the invention will become apparent from the following description of embodiments taken in conjunction with the accompanying drawings, wherein: Figure 1 A top view of a plate according to a first embodiment of the present invention is shown; Figure 2 It shows that, respectively, according to Figure 1 Exploded view of two adjacent plates; Figure 3 shows the following in two partial views: Figure 1 First and second details of the sprue; Figure 4 A top view of an assembled heat exchanger according to a first embodiment of the invention is shown. Detailed Implementation

[0041] Figure 1A top view of a plate P in a heat exchanger 100 according to a first embodiment of the invention is shown. Plate P has a substantially rectangular shape, having a longer side and a shorter side. Plate P has a plate plane PE, which is extended from two mutually orthogonal sides of plate P. The stacking direction SR is orthogonal to the plate plane PE. Plate P has two first openings O1 as inlet channels and two second openings O2 as outlet channels, respectively perpendicular to the plate plane PE. The main flow direction HF of the medium (not shown) extends substantially from one of the first openings O1 to the opposite second opening O2. The four openings O1, O2 are circular. Plate P is configured such that connection portions appear between corresponding corrugated profiles W1, W2 of two adjacent plates P, in which the plates P are fastened together (partially shown). Plate P has repeating first corrugated profiles W1, which extend substantially transversely to the main flow direction HF and are corrugated in a zigzag pattern around the extension direction by numerous lines respectively implemented with alternating concave and convex angles. The profiles of the first corrugated profiles W1 are respectively constructed as groove-like recesses and ridges. Four openings O1, O2 are respectively surrounded by second corrugated profiles W2. Each profile of the second corrugated profiles W2 is constructed substantially orthogonal to the enclosed openings O1, O2. The four second corrugated profiles W2 respectively surround the four openings O1, O2 in a star shape. The four openings O1, O2 each have a diameter of 10 mm. 2 Up to 500mm 2 The preferred through-face width is 200mm. 2 Up to 300mm 2 In this way, the heat exchanger (not shown) has a smaller pressure loss. Four second corrugated profiles W2 are each composed of elongated profiles in the form of raised sections, arranged orthogonally to the enclosed openings O1 and O2. The first corrugated profile W1 and the four second corrugated profiles W2 are connected to each other. One of the two first openings O1 is surrounded by an arch D, which is raised relative to the plate plane PE. One of the two second openings O2 is surrounded by an arch D, which is raised relative to the plate plane PE. These two arches D are respectively arranged between the corresponding openings O1 and O2 and the corresponding second corrugated profile W2. Another first opening O1 is surrounded by a region B without corrugated profiles. Another second opening O2 is surrounded by a region B without corrugated profiles. These two regions B without corrugated profiles are respectively arranged between the corresponding openings O1 and O2 and the corresponding second corrugated profile W2. Plate P has an edge RA that is pulled upwards around the perimeter. Plate P is integrally constructed and has a first metallic material.

[0042] Figure 1 The first detail D1 mentioned includes a section of plate P that includes a second opening O2 surrounded by an arch D and a second corrugated profile W2.

[0043] Figure 1 The second detail D2 mentioned includes a section of plate P that includes a second opening O2 surrounded by a region B without corrugated profile and a second corrugated profile W2.

[0044] Figure 2 It shows that, respectively, according to Figure 1 An exploded view of two adjacent plates P. The two plates P are thus shown according to a first embodiment of the invention. The upper plate P is arranged with its orientation twisted 180° relative to the adjacent lower plate P. A connection point (not shown) between the two plates P occurs at two corrugated profiles W1 and W2. Furthermore, a connection point (not shown) between the two plates P also occurs at the arch D and the region B without corrugated profiles, respectively. Additionally, a connection point (not shown) between the plates P occurs at the edge RA.

[0045] Figure 3 shows the results according to the two partial views. Figure 1 The first detail 1 and the second detail 2 of part P.

[0046] exist Figure 3.1 The first detail 1 is shown. The second opening O2 is surrounded by a second corrugated profile W2. An arch D is arranged between the second corrugated profile W2 and the second opening O2. The second corrugated profile W2 and the arch D are connected to each other. The star-shaped second corrugated profile W2 surrounding the second opening O2 reduces the unsupported area of ​​the plate P. Nevertheless, a medium (not shown) can still flow to or away from the second opening O2. Additionally, the linear shape of the second corrugated profile W2 increases the areal density of the (not shown) connection points between the two plates, and these connection points are closer to the center point of the second opening O2. The first corrugated profile W1 is connected to the second corrugated profile W2.

[0047] Figure 3.2 The second detail 2 is shown. The second opening O2 is surrounded by a second corrugated profile W2. A region B without a corrugated profile is arranged between the second corrugated profile W2 and the second opening O2. The star-shaped second corrugated profile W2 surrounding the second opening O2 reduces the unsupported area of ​​the plate P. Nevertheless, a medium (not shown) can still flow to or away from the second opening O2. Additionally, the linear shape of the second corrugated profile W2 increases the areal density of the (not shown) connection points between the two plates, and these connection points are closer to the center point of the second opening O2. The first corrugated profile W1 is connected to the second corrugated profile W2. Advantageously, the strength of the plate is increased even when the through surface of the opening is increased by the second corrugated profile W2.

[0048] Figure 4 A top view of an assembled heat exchanger 100 according to a first embodiment of the invention is shown. The heat exchanger according to the invention is preferably used in a refrigerant circuit or coolant circuit (neither shown) of a motor vehicle. The heat exchanger 100 according to the invention has plates P stacked vertically on top of each other to form a block B1, wherein two adjacent plates P are respectively twisted 180° relative to each other. Plates P have first and second openings for forming channels for collecting or distributing two media M1, M2 (partially shown). A sealing plate AP is arranged at the bottom, which closes the block B1. An end plate EP is arranged at the top, which closes the block B1 at the top. Plates P, sealing plate AP, and end plate EP are each made of a metallic material, preferably an aluminum alloy. Adjacent plates P, sealing plate AP, and end plate EP are respectively connected to each other. Preferably, adjacent plates P, sealing plate AP, and end plate EP are connected to each other in a material-locking manner, particularly preferably by means of brazing. Plates P are stacked between sealing plate AP and end plate EP along the stacking direction SR. Plates P, AP, and EP are directly adjacent to each other. The heat exchanger 100 has two flow paths (not shown) extending inside the heat exchanger 100 and through which two media M1 and M2 flow respectively. End plate EP has a first inlet line ZL1 and a first outlet line AL1, through which the first medium M1 is supplied to the heat exchanger 100. The first inlet line ZL1 is connected to a first channel, through which the first medium M1 is distributed to a first cavity, and the first outlet line is connected to the first channel, through which the first medium M1 is collected again from the first cavity (partially shown). A second inlet line ZL2 is connected to a second channel, through which the second medium M2 is distributed to a second cavity, and the second outlet line is connected to the second channel, through which the second medium M2 is collected again from the second cavity (partially shown). The first medium M1 is a refrigerant, preferably propane (R290) or carbon dioxide (R744), while the second medium M2 is a coolant, preferably a mixture of ethylene glycol and water. Because the plate P has two different geometrically distinct corrugated profiles, namely, the second corrugated profiles respectively surround the openings in a star-shaped manner, the regions of the plate P adjacent to these openings are supported on adjacent plate P (not shown). This results in the heat exchanger 100 according to the invention having sufficiently high strength. Furthermore, the openings have a sufficiently large through surface, thereby resulting in the claimed heat exchanger 100 having sufficiently low pressure loss (not shown).

[0049] List of reference numerals

[0050] 100 Heat exchanger according to the present invention

[0051] 200 A refrigerant circuit having a heat exchanger according to the invention

[0052] 201 A coolant circuit having a heat exchanger according to the invention

[0053] P board

[0054] The corrugated profile of plates W1 and W2 according to the present invention

[0055] AP cover plate

[0056] EP end plate

[0057] PE sheet flat surface

[0058] B. Areas without wavy outlines

[0059] Bl block

[0060] SR stacking direction

[0061] The main flow direction of HF in the cavity between two adjacent plates.

[0062] Openings in O1 and O2 panels

[0063] H is the cavity between two adjacent plates.

[0064] D arch, which partially surrounds the first and third openings.

[0065] The upward-pulling edge of the RA panel.

[0066] The media flowing through the heat exchanger in M1 and M2

[0067] ZL1 and ZL2 are used for the inlet lines of the medium.

[0068] AL1 and AL2 are used for the drainage lines of the medium.

Claims

1. A heat exchanger (100) preferably used in motor vehicles, said heat exchanger having: - Multiple interconnected panels (P) - in, A cavity (H) is formed between the plates (P) to be fluidically separated from the surrounding environment. The first and second media (M1, M2) flow alternately through the cavity through at least one inlet line and one outlet line, respectively. - Wherein, the plate (P) has a pair of openings (O1, O2) perpendicular to the plate plane (PE) as inlet and outlet lines, - Wherein, the plates (P) are configured such that connection points appear between the respective corrugated profiles (W1, W2) of the plates, and in the region of the connection points, the plates are fastened to each other. - Wherein, the corrugated profiles (W1, W2) of the plates (P) and their connecting portions are configured such that the flow of the first and second media (M1, M2) formed between the plates (P) from their respective inlet lines to their respective outlet lines is non-linear. - Wherein, the plates (P) each have a repeating first corrugated profile (W1), which extends substantially transversely to the main flow direction (HF) and, particularly, corrugates in a zigzag pattern around the extension direction. - Wherein, the openings (O1, O2) are respectively surrounded by a second corrugated profile (W2).

2. The heat exchanger (100) according to claim 1, characterized in that, Each profile of the second corrugated profile (W2) is substantially orthogonal to the openings (O1, O2) it encloses.

3. The heat exchanger (100) according to claim 1 or 2, characterized in that, The first corrugated profile (W1) and the second corrugated profile (W2) are connected to each other.

4. The heat exchanger (100) according to claim 1, 2 or 3, characterized in that, The second corrugated profile (W2) surrounds each of its openings (O1, O2) in a star shape.

5. The heat exchanger (100) according to any one of the preceding claims, characterized in that, One of the openings (O1, O2) is surrounded by an arch (D) that bulges relative to the plate plane (PE), such that one of the two openings (O1, O2) is alternately fluidically connected to an alternate cavity (H).

6. The heat exchanger (100) according to claim 5, characterized in that, The arch (D) is respectively arranged between the opening (O1, O2) and the second corrugated profile (W2), wherein the arch (D) and the second corrugated profile (W2) are respectively connected to each other.

7. The heat exchanger (100) according to claim 5 or 6, characterized in that, A portion of the openings (O1, O2) are each surrounded by a region (B) without corrugated profiles, wherein the region (B) is respectively arranged between the surrounded openings (O1, O2) and the second corrugated profile (W2).

8. The heat exchanger (100) according to any one of the preceding claims, characterized in that, The openings (O1, O2) are each 10mm in diameter. 2 Up to 500mm 2 200mm is preferred 2 Up to 300mm 2 The through surface.

9. The heat exchanger (100) according to any one of the preceding claims, characterized in that, The openings (O1, O2) are each substantially circular in shape.

10. The heat exchanger (100) according to any one of the preceding claims, characterized in that, The first corrugated profile (W1) is constructed to be geometrically different from the second corrugated profile (W2), wherein the plates (P) are integrally formed.

11. The heat exchanger (100) according to any one of the preceding claims, characterized in that, The connection points at the second corrugated profile (W2) of two adjacent plates (P) are basically linear, while the connection points at the first corrugated profile (W1) of two adjacent plates (P) are basically point-like.

12. The heat exchanger (100) according to any one of the preceding claims, characterized in that, The areal density of the connection portion at the second corrugated profile (W2) of two adjacent plates (P) is greater than the areal density of the connection portion at the first corrugated profile (W1) of two adjacent plates (P).

13. The heat exchanger (100) according to any one of the preceding claims, characterized in that, The plate (P) has two first openings (O1), two second openings (O2), four second corrugated profiles (W2) spaced apart from each other, and a first corrugated profile (W1).

14. A method for manufacturing a heat exchanger (100) according to any one of claims 1 to 13, the method comprising the following steps: - Embossing and / or stamping out sheet metal (P). - The plates (P) are stacked vertically, preferably stacked such that two adjacent plates (P) are twisted 180° relative to each other. - At the connection point between two adjacent plates (P), the plates (P) that are close to each other are fastened, preferably by material locking, and particularly preferably by brazing.

15. A refrigerant circuit (200) or a coolant circuit (201) having at least one heat exchanger (100) according to any one of claims 1 to 13.

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