Cooling device for at least two electronic power modules of a drive train and cooling arrangement

Abstract

The invention relates to a cooling arrangement and a cooling device (10) for at least two electronic power modules (21, 22, 23) of a drive train, in particular for a traction inverter, comprising an interior space (30) bounded by an interior boundary (40), wherein the interior boundary (40) has an inlet opening (41) for supplying a coolant into the interior space (30) and an outlet opening (42) for discharging the coolant from the interior space (30), and the interior space (30) can be permeated by a coolant flow (K) in the flow direction (S) from the inlet opening (41) to the outlet opening (42), wherein the interior space (30) has at least two, preferably three, fluidically separated cooling chambers (51, 52) arranged one behind the other in the flow direction (S) between the inlet opening (41) and the outlet opening (42).53) comprising, wherein waste heat from a power module (21, 22, 23) attributable to each cooling chamber (51, 52, 53) can be supplied by means of a heat exchange area (61, 62, 63) encompassed by the interior boundary (40), wherein the interior (30) is designed such that the coolant flow (K) in the interior (30) and in the flow direction (S) after the inlet opening (41) can be divided and that coolant partial flows (K1, K2, K3) that can be generated from the inflowing coolant can be guided such that each coolant partial flow (K1, K2, K3) intended to flow through a cooling chamber (51, 52, 53) flows through only one of the cooling chambers (51, 52, 53). which provides an easily manufactured cooling system with efficient cooling for a multiple power modules.

Description

Technical area

[0001] The invention relates to a cooling device for at least two electronic power modules of a drive train; furthermore, the invention relates to a cooling arrangement comprising at least two power modules with a cooling device.

[0002] The cooling devices mentioned above can be used for a variety of applications. In this application, they are described, without limitation, in the context of a drive train for battery-electric vehicles, in particular automobiles.

[0003] A power module, also known as a power module, is an electronic assembly used in power electronics. The assembly can comprise several interconnected power semiconductor components, such as transistors, particularly MOSFETs (metal oxide semiconductor field-effect transistors), diodes, or IGBTs (insulated gate bipolar transistors), to enable current and voltage regulation in a circuit.

[0004] The power module is used to switch, provide, and / or control high power. A power module or multiple power modules are often used in applications requiring efficient energy conversion, such as power converters, inverters, motor controllers, switching power supplies, and other power electronic systems.

[0005] A typical application for power modules is traction inverters for driving electric motors in the context of mobility solutions, for example, for battery-electric vehicles such as cars or boats, or DC-powered trains. By converting energy provided by a DC power supply, for example, from a battery, the electrical energy can be made available to operate an electric motor.

[0006] Since power modules switch comparatively high voltages and / or currents, they heat up considerably during operation, partly due to loss processes in the semiconductor components.

[0007] On the one hand, this is being counteracted by making the power semiconductor components used in power modules increasingly efficient. In particular, materials such as silicon carbide or gallium nitride are increasingly being used for power semiconductor components, which have lower switching losses during operation than silicon-based components.

[0008] On the other hand, active cooling of a power module is usually provided so that it can be operated smoothly and with consistent efficiency despite heating, and so that it has the longest possible service life.

[0009] If several power modules are required for an application, for example three power modules for a three-phase traction inverter, these are usually spatially grouped together as an assembly.

[0010] Such an assembly, for example, consisting of three power modules, is then typically cooled with a cooling system. Often, the three power modules of a traction inverter assembly are cooled with the same coolant flow, which flows serially to the power modules.

[0011] This has the disadvantage that the coolant flow gradually heats up during the cooling process and has different temperatures for the different power modules. If this is not taken into account, it will have a detrimental effect on the efficiency and service life of the power modules.

[0012] German Patent Application DE102019202425 A1 discloses a cooling device that uses such a coolant flow to cool multiple waste heat-generating components. The coolant flow flows from an inlet to an outlet, thereby cooling at least two components. The heating of the coolant flow is taken into account by providing at least two cooling structures for regionally adjusting different heat flows between the at least two components and the coolant.

[0013] Furthermore, DE 10 2020 207 966 A1 discloses a cooling arrangement for electronic components of a motor vehicle, wherein the cooling device has a coolant inlet opening arranged centrally in a base plate. Through this inlet opening, a turbulence mat is flowed centrally, and the coolant flows outward from the center of the base plate, cooling the electronic component, while the heated coolant is discharged via outlet openings.

[0014] This solution is disadvantageous because it requires a large number of mechanical components. Furthermore, such an arrangement can only cool one component, so the effort required for multiple components to be cooled is multiplied. Description of the invention

[0015] The invention is based on the object of providing a cooling device that is easy to manufacture and enables efficient cooling of a plurality of power modules. Furthermore, the invention is based on the object of specifying an easily manufactured cooling arrangement comprising at least two power modules and a cooling device for efficient cooling of the at least two power components.

[0016] The object is achieved by the subject matter of the independent claims. Advantageous developments of the invention are specified in the dependent claims, the description, and the accompanying figures. In particular, the independent claims of one claim category can also be developed analogously to the dependent claims of another claim category. Further embodiments and developments emerge from the subclaims and from the description with reference to the figures.

[0017] The present invention comprises a cooling device for at least two electronic power modules of a drive train, in particular for a traction inverter, comprising an interior space delimited by an interior space boundary, wherein the interior space boundary has an inlet opening for supplying a coolant into the interior space and an outlet opening for discharging the coolant from the interior space, and the interior space can be flowed through by a coolant flow in the flow direction from the inlet opening to the outlet opening, wherein the interior space between the inlet opening and the outlet opening comprises at least two, preferably three, fluidically separated cooling chambers arranged one behind the other in the flow direction, wherein each cooling chamber can be supplied with waste heat from a power module assigned to the respective cooling chamber by means of a heat exchange area enclosed by the interior space boundary, wherein the interior space is designed in such a way thatthat the coolant flow can be divided in the interior and in the flow direction after the inlet opening and that partial coolant flows that can be generated from the inflowing coolant can be guided in such a way that each partial coolant flow intended to flow through a cooling chamber flows through only one of the cooling chambers.

[0018] Using such a cooling device, it is possible to efficiently cool at least two power modules. By designating a coolant flow to flow through only one of the cooling chambers at a time, all cooling chambers can be flowed through with a partial coolant flow of essentially the same temperature. Cooling performance differences due to different coolant temperatures for the power modules to be cooled can thus be avoided. Furthermore, the simple, particularly flat, design results in a compact arrangement of the cooling device, which can also be implemented with few components. The use of only a few components significantly simplifies production. In particular, the cooling device can be manufactured using 3D printing processes, casting processes, bulk forming processes, in particular hot forming, semi-hot forming or cold forming, or other processes.

[0019] As explained above, power modules typically refer to assemblies of power semiconductors, such as so-called half-bridges or full-bridges. Due to their operating point, power modules and the power semiconductor components they contain generate significant power losses (in the form of heat) and require cooling during operation.

[0020] Such power modules are used in particular in the drivetrains of battery-electric vehicles, such as electrically powered cars or trucks. The cooling device according to the invention is not limited to this, but can be advantageously used in this area.

[0021] In particular, the power modules can form a traction inverter that supplies a vehicle's drive system with alternating current. The traction inverter converts direct current, for example, from an electric vehicle battery, into alternating current. Power outputs in the range of 80 to 150 kW are typical; however, these can also be higher or lower. Furthermore, the DC voltage in current electric vehicles is in the range of 400 V or 800 V. Despite the high efficiency of modern traction inverters, the semiconductor components heat up considerably due to thermal losses. This waste heat must be dissipated using a cooling system to prevent damage to the traction inverter.

[0022] In this context, three power modules are often used, since the vehicle drive is usually supplied with a three-phase alternating voltage. The cooling device according to the invention can be used for three power modules.

[0023] However, two or more than three power modules can also be provided, which can be cooled by means of the cooling device according to the invention. Preferably, the number of cooling chambers of the cooling device corresponds to the number of power modules to be cooled.

[0024] A cooling chamber is the area through which the heat of a power module assigned to the cooling chamber can be transferred to the coolant. The cooling device comprises at least two cooling chambers, whereby each cooling chamber can be provided for cooling only one power module. The cooling device comprises at least two cooling chambers, but can also have more than two cooling chambers, in particular three, four, or more cooling chambers.

[0025] The at least two, preferably three, cooling chambers are arranged one behind the other in the flow direction. Furthermore, the respective cooling chambers are fluidically separated from one another. The fluidic separation of the cooling chambers is designed such that a coolant partial flow that has flowed through one of the cooling chambers does not mix with a coolant partial flow assigned to another cooling chamber before this coolant partial flow has flowed through the cooling chamber assigned to it. However, mixing of different coolant partial flows assigned to different cooling chambers can be provided outside a cooling chamber, in particular downstream of the cooling chambers.

[0026] The flow direction refers to the macroscopic flow direction of the coolant during operation, i.e. the direction from the inlet opening to the outlet opening.

[0027] The heat to be transferred to the coolant via a cooling chamber can be supplied to the cooling chamber via a heat exchange area assigned to the cooling chamber. The heat exchange area advantageously has high thermal conductivity and can be made, in particular, of metal. The heat exchange area can be a portion of the interior boundary and, during operation, is in thermally conductive contact with the power module to be cooled. Preferably, each power module is assigned its own heat exchange area.

[0028] The heat exchange area can be a structurally defined area. Likewise, a heat exchange area can also be functionally considered the area where, during operation, a large portion of the heat is transferred from a power module to the cooling device. In particular, this can be the area of ​​the cooling device where a power module is intended to be arranged.

[0029] Preferably, a power module can be arranged on a surface of the heat exchange area enclosed by the interior boundary, facing away from the interior. The waste heat from a power module assigned to the heat exchange area can enter the cooling chamber through the heat exchange area and be transferred there to the coolant. The heat exchange area preferably comprises a flat surface on which a power module can be arranged.

[0030] It is advantageous if the thickness of the heat exchange area, through which the heat must pass in order to reach the interior or the respective cooling chamber, is designed to be as small as possible.

[0031] In an advantageous embodiment of the invention, the entire interior boundary can be made of metal, in particular copper or aluminum. Copper can be understood as copper or a copper alloy, and aluminum can be understood as aluminum or an aluminum alloy. This can also be understood as a powder material that is bonded in a form-fitting and material-locking manner using a corresponding process.

[0032] The interior boundary serves to delimit the interior space from the outside. This means, on the one hand, that the interior boundary prevents unwanted coolant from escaping from the cooling system during operation. On the other hand, the interior boundary includes heat exchange areas through which the waste heat from power modules connected to these heat exchange areas can be conducted into the cooling chamber.

[0033] The interior space is the volume defined by the interior boundary. The interior space does not necessarily have to be completely permeable to coolant; in particular, the interior space may contain structures that serve to guide the coolant. Furthermore, the interior space may include structures that also perform other functions. In particular, so-called dry chambers may also be provided, i.e., hollow volumes enclosed by the interior space that are not permeable to coolant during operation, but which influence the flow behavior of the coolant in the permeable interior space.

[0034] The interior space comprises at least two cooling chambers and is further configured so that the coolant flow can be divided in the interior space and in the flow direction after entering the interior space.

[0035] The division can take place in a single step or in several steps. In the latter variant, for example, the incoming coolant flow can first be divided into a first coolant partial flow and a further coolant partial flow, also referred to as the coolant residual flow. The first coolant partial flow is intended to flow through the first cooling chamber. The coolant residual flow can comprise the coolant partial flows for at least one further cooling chamber in the flow direction, preferably several cooling chambers. The respective coolant flows assigned to the respective subsequent cooling chamber are then branched off from the coolant residual flow by means of further guide elements, possibly gradually. Each coolant partial flow assigned to a cooling chamber flows only through the cooling chamber assigned to it and no further cooling chamber.This design of the interior ensures that each cooling chamber can be supplied with a partial coolant flow with essentially the same temperature.

[0036] By specifically designing the interior space for dividing the coolant partial flows, the cooling performance of each cooling chamber can be influenced by the volume flow of the respective coolant partial flow. Typically, the interior space is designed such that the incoming coolant is divided in such a way that a substantially equal volume of coolant partial flow can flow through at least two cooling chambers.

[0037] However, the interior space can also be designed such that at least two cooling chambers arranged one behind the other in the flow direction can be flowed through by partial coolant flows of different sizes. This allows the cooling capacity for each cooling chamber to be individually adjusted based on the intended design of the interior space, by means of which the volume flow of the partial coolant flow assigned to the respective cooling chamber can be determined.

[0038] By adapting the interior design, the cooling chambers can be supplied with different cooling flow rates. If the cooling capacity to be achieved by each cooling chamber is known, the interior can be designed in such a way that the coolant flows for the different cooling chambers are dimensioned so that the different cooling capacities are achieved by the respective cooling chambers.

[0039] In order to supply and discharge coolant into and from the interior of the cooling device, the interior boundary has an inlet opening and an outlet opening for the coolant. The inlet opening is preferably arranged upstream of the first cooling chamber in the flow direction. The outlet opening is preferably arranged downstream of the last of the at least two cooling chambers in the flow direction. Furthermore, the inlet opening and the outlet opening can each be arranged symmetrically to a longitudinal center axis of the cooling device running in the flow direction.

[0040] Incompressible liquids with high heat capacity are preferred as coolants. Water is a suitable coolant for most applications. However, other coolants, such as gaseous coolants, can also be used.

[0041] In one embodiment of the cooling device, at least one of the at least two cooling chambers has a plurality, in particular a multiplicity, of pin-shaped cooling elements, which are thermally conductively connected to the heat exchange area assigned to this cooling chamber. The number and dimensions of the cooling elements are configured such that, for a predetermined partial coolant flow through the respective cooling chamber, a target cooling performance is achieved by the respective cooling chamber and / or a predetermined pressure loss is not exceeded. This can be provided, in particular, for each of the at least two cooling chambers.

[0042] By adjusting the number and size of the cooling elements for each cooling chamber, the cooling performance of a cooling chamber can be further customized to the power module to be cooled. On the one hand, the design of the interior can adjust the respective partial coolant flow through each cooling chamber, thus influencing the cooling performance of the cooling chamber. On the other hand, the cooling performance of the chamber can be adjusted by changing the number and nature of the pin-shaped cooling elements contained in that cooling chamber. In particular, the partial coolant flow assigned to the cooling chamber and the number and size of the pin-shaped cooling elements of the same cooling chamber can be coordinated in such a way that a desired target cooling performance can be achieved.

[0043] In an advantageous embodiment, the at least two cooling chambers are designed with the same number of cooling elements and equally dimensioned, in particular shaped, pin-shaped cooling elements.

[0044] Increasing the number of pin-shaped cooling elements generally increases the cooling capacity of the cooling chamber, while reducing the number of pin-shaped cooling elements generally decreases the cooling capacity. However, the flow dynamic influence associated with changing the number and dimensions of the cooling elements must be taken into account. Changing the number and dimensions of the cooling elements can influence the flow resistance of the corresponding cooling chamber, which can affect the partial coolant flow assigned to the cooling chamber, particularly the back pressure during steady-state operation.

[0045] The pin-shaped cooling elements have a longitudinal direction, meaning they are at least 1.1 times longer than they are wide. In particular, the pin-shaped cooling elements can be longer than they are wide by a factor of between 1.3, in particular 1.4 and 20 times longer than they are wide. In particular, the pin-shaped cooling elements can be at least 3 times longer than they are wide. In particular, the pin-shaped cooling elements can be a maximum of 7 times longer than they are wide. The pin-shaped cooling elements are preferably arranged with their longitudinal axis perpendicular to the flow direction.

[0046] The cross-section of the pin-shaped cooling elements can also be used to adjust the cooling performance of the cooling chamber containing the pin-shaped cooling elements. For example, the cross-section of the pin-shaped cooling elements can be circular, elliptical, teardrop-shaped, triangular, square, rectangular, or polygonal. Another shape, in particular an asymmetrical shape, can also be provided. The cross-section is formed by a cutting plane through the pin-shaped cooling element perpendicular to its longitudinal direction.

[0047] Preferably, the pin-shaped cooling elements extend longitudinally across the entire height of a cooling chamber, i.e., perpendicular to the flow direction. This maximizes the surface area of ​​the pin-shaped cooling element that interacts with the partial coolant flow. Furthermore, a pin-shaped cooling element configured in this way provides a supporting function for mechanically stabilizing the cooling device.

[0048] In a further embodiment of the cooling device, the interior is designed such that the first cooling chamber in the flow direction can be acted upon by a first coolant partial flow, and the first coolant partial flow behaves in relation to the coolant flow entering the interior in the same way as the first cooling chamber behaves in relation to all existing cooling chambers. This is an advantageous embodiment of the interior in which a uniform distribution of the coolant is provided across the cooling chambers. This is particularly advantageous when the power modules assigned to the cooling chambers have the same or similar power loss during operation and the cooling chambers are structurally identical.

[0049] The first coolant substream is the coolant substream assigned to the first cooling chamber. If only a second cooling chamber is available, the coolant flow is divided into two equal coolant substreams by the design of the interior.

[0050] If the cooling system comprises three cooling chambers, the first coolant partial flow amounts to one-third of the coolant flow, while two-thirds are intended for flow through the second and third cooling chambers. A further coolant partial flow amounting to one-third of the coolant flow entering the cooling system flows through the second and third cooling chambers. The same applies if there are more than three cooling chambers.

[0051] In an advantageous embodiment of the cooling device, the interior space is designed such that the first cooling chamber receives the coolant flow directly from the inlet opening. The coolant flow is divided into the first coolant partial flow and the coolant residual flow by dimensioning the inlet area of ​​the first cooling chamber, in particular by its cross-section perpendicular to the flow direction of the coolant, and by a cooling channel bypassing the first cooling chamber, through which the coolant residual flow can be guided. Furthermore, the interior space can be designed such that the coolant flow flows from the last cooling chamber directly to the outlet opening. If the first and / or last cooling chamber or cooling unit receives / is supplied directly to or from the first and / or last cooling chamber or cooling unit (from the inlet opening or to the outlet opening, or into the inlet or outlet), the back pressure (at the inlet opening) is reduced enormously.Without a direct flow to the first cooling chamber, the entire volume flow for all cooling units, for example, three, would have to be fed into a common supply channel. By directly flowing to the first cooling unit, the volume flow in the supply channel, for example, with a total of three cooling units, is reduced by one-third. This reduces the pressure loss in particular.

[0052] In a further embodiment of the cooling device, the at least two cooling chambers are arranged symmetrically to a longitudinal center axis of the interior boundary, wherein a boundary element of the first cooling chamber, arranged at least partially parallel to the flow direction, together with a first guide element running parallel to the flow direction, in particular a part of the interior boundary, form at least one inlet region of a cooling channel, wherein the cooling channel is designed to guide the partial coolant flow entering the inlet region of the cooling channel around the first cooling chamber. The first guide element is advantageously arranged such that a plane arranged in the inlet region of the cooling channel perpendicular to the flow direction encompasses both the boundary element of the first cooling chamber and the first guide element.

[0053] This solution is advantageous because a small number of flow guidance structures can be provided from the interior to guide the residual coolant flow entering the inlet area. The boundary element of the first cooling chamber fluidically separates at least the inlet area of ​​the cooling channel from the first cooling chamber. The boundary element of the first cooling chamber thus performs a dual function, guiding the first partial coolant flow in the first cooling chamber on the one hand, as well as the residual coolant flow in the inlet area of ​​the cooling channel.

[0054] The inlet area of ​​the cooling channel is further formed, at least in sections, by a first guide element, in particular formed by a part of the interior boundary, which interacts with the boundary element in such a way that the residual coolant flow is guided into the inlet area of ​​the cooling channel. Preferably, the first guide element and the boundary element form the inlet area of ​​the cooling channel.

[0055] The first guide element can also be provided as a separate guide element in the interior. A separate first guide element increases the flexibility of the coolant guide configuration.

[0056] Preferably, the cross section of the inlet region of the first cooling chamber and the cross section of the inlet region of the cooling channel are dimensioned such that, during stationary operation of the cooling device, the first coolant partial flow and the coolant residual flow are adjusted in the desired manner.

[0057] By designing the cooling channel in such a way that the residual coolant flow is guided around the first cooling chamber, which is arranged symmetrically to the longitudinal center axis of the interior boundary, it is possible for the second cooling chamber to also be arranged symmetrically to the longitudinal center axis, while still allowing a separate partial coolant flow to flow through each cooling chamber. A central arrangement of the cooling chambers in the interior offers advantages with regard to the ability to arrange the power modules on the cooling device.

[0058] In a further embodiment of the cooling device, the cooling channel has at least one second guide element which is designed to guide the coolant partial flow entering the cooling channel at least partially to at least one second cooling chamber.

[0059] The second guide element thus serves to divide or guide the coolant partial flow entering the cooling channel depending on the number of cooling chambers downstream of the first cooling chamber in the flow direction. If only a second cooling chamber is present, the entire coolant partial flow entering the cooling channel is guided into the second cooling chamber. If, however, a third cooling chamber is also present, a second defined coolant partial flow is fed to the second cooling chamber and a third coolant partial flow to the third cooling chamber by means of the second guide element. If more than three cooling chambers are provided, this is taken into account accordingly for the coolant partial flows, for example by providing a third guide element by means of which the third and fourth coolant partial flows can be adjusted.

[0060] The partial coolant flows entering the existing cooling chambers are advantageously of substantially equal size. However, the partial coolant flows can also be configured to vary in size in a predefined manner by modifying the interior, in particular the first guide element and / or the second guide element and / or additional guide elements.

[0061] In a further embodiment of the cooling device, the interior boundary is formed in two parts, wherein the two-part interior boundary comprises a solid-formed base part with the at least two cooling chambers, as well as a cover part, in particular a stamped or laser-cut one. When closed, the base part and the cover part seal the interior in such a way that no coolant escapes between the base part and the cover part during operation. Such a design of the cooling device results in a particularly simple-to-manufacture, low-part design.

[0062] The decisive factor for considering a part of the cooling system as a base part is the solidity of the component, which is designed to absorb the high loads during operation. The base part is therefore independent of the spatial arrangement of the cooling system. This means that the base part can be located below the cover part, above the cover part, or possibly even to the side of the cover part.

[0063] The base part is manufactured by forging, particularly by warm or cold forming. The forged base part can have all or a selection of the above-described interior configurations, for example, at least two cooling chambers, a plurality of pin-shaped cooling elements, first and second guide elements, the inlet and outlet openings for the coolant, etc.

[0064] Preferably, the solid-formed base part comprises the inlet and outlet openings for the coolant, as well as the at least two cooling chambers with their respective, in particular pin-shaped, cooling elements and a plurality of limiting elements and / or guide elements for guiding respective partial coolant flows.

[0065] This manufacturing method also allows the base part to be made of metal, particularly copper or aluminum. This simultaneously ensures good thermal conductivity of the interior boundary, which is advantageous for heat exchange areas enclosed within the interior boundary.

[0066] Furthermore, this design allows for the provision of a compact and lightweight cooling device, particularly for power modules of traction inverters. Due to its simple construction and compactness, such a design requires only a very low installation height. With regard to use in traction inverters, the cooling device can thus be installed in a space-saving manner or integrated into an inverter unit.

[0067] Furthermore, the solid forming of the base part allows for easy provision of additional functionalities for the cooling device, such as stiffening ribs, mounting points, housing functions, internal support structures, etc., which can be important, for example, for the assembly of the cooling device with the power modules, the arrangement of the cooling device during operation and for the operation of the cooling device itself.

[0068] Furthermore, in this embodiment, the interior boundary comprises a cover part. This can also be made of metal, in particular sheet metal, and is advantageously produced by stamping or laser cutting. The thickness of the cover part can be selected to be small, since a large portion of the mechanical stresses occurring during operation can be absorbed by the solid-formed base part. The base part and the cover part can thus be formed from the same metallic material, in particular copper or aluminum.

[0069] The solid-formed base part and the cover part are connected to each other in such a way that no coolant can escape between the base part and the cover part. This is also referred to as the sealed state of the cooling device. The coolant-tight sealing of the base part and the cover part can be achieved, for example, by laser welding or soldering, especially brazing.

[0070] In an advantageous embodiment, the solid-formed base part has the inlet opening and the outlet opening, and the cover part has at least one of the heat exchange areas. This means that at least one power module is arranged on the cover part side. Preferably, all power modules to be cooled are arranged on the cover part side.

[0071] It is advantageous to arrange the power modules on the cover section because the thickness of the cover section can be kept comparatively low, unlike the solid-formed base section. Therefore, the low thickness also allows for good heat transfer from a power module to the interior via a heat exchange area enclosed by the cover section.

[0072] In a further advantageous embodiment, a surface of the heat exchange area encompassed by the cover part facing the assignable power module is designed as a plane section for arranging a power module on the surface.

[0073] This means that the cover part is designed, at least in sections, as a flat cover part, particularly made of sheet metal, and is spatially configured such that the surface of the heat exchange area intended for contact with the power module is flat. This allows for a simple arrangement of the power modules on the cover part side and a flat heat transfer from a power module into the interior via the respective heat exchange area.

[0074] In a further embodiment, the lid part, in the closed state, is thermally conductively connected, in particular by a material bond, to the pin-shaped cooling elements of the at least two cooling chambers, which are enclosed by the solid-formed base part. This ensures effective distribution of the heat supplied via the heat exchange area into the respective cooling chamber.

[0075] A heat-conducting connection of the pin-shaped cooling elements, in particular a plurality of pin-shaped cooling elements, with the cover part can be provided particularly advantageously by means of a material connection.

[0076] For example, the lid part is coated with solder on the side facing the interior. When closed, the pin-shaped cooling elements protrude toward the lid part. A furnace process melts the solder, which then bonds to the parts of the cooling elements that protrude toward the lid part. This creates a good heat-conducting connection between the pin-shaped cooling elements and the lid part.

[0077] Such a metallic material connection of the cooling elements of a cooling chamber with the cover part allows the heat of a power module arranged on the cover part to be effectively supplied to the partial coolant flow flowing through the cooling chamber.

[0078] According to a further embodiment, the solid-formed base part has the inlet opening and the outlet opening, wherein the solid-formed base part further comprises at least one of the heat exchange regions, which is arranged between the inlet opening and the outlet opening. In particular, a surface of the heat exchange region facing the assignable power module is designed as a plane section for arranging a power module on the surface.

[0079] According to this embodiment, an arrangement of at least one power module is additionally or alternatively provided on the base part side on a heat exchange area assigned to the power module.

[0080] This design generally requires somewhat more complex preparation of the heat exchange area of ​​a solid-formed base part assigned to a power module. Due to the solid design of the base part, the thickness between a surface of the heat exchange area facing a power module and the cooling chamber is comparatively high. This would limit heat dissipation into the cooling chamber during operation. Therefore, it is advantageous, at least for the intended heat exchange areas, to provide a thickness that is not too high or to reduce the thickness of the base part, at least for the at least one heat exchange area.

[0081] Subsequently reducing the thickness of the heat exchange area requires an additional machining step of the base part. The thickness in the heat exchange areas can be reduced, for example, using machining processes, i.e., removing material from the outside of the interior boundary, for example by machining.

[0082] Advantageously, however, during the production of the solid-formed base part, it can already be provided that the thickness of the base part is reduced at least in the intended heat exchange areas, so that any subsequent processing of the base part to provide heat exchange areas with a small thickness can be avoided or at least reduced.

[0083] Preferably, a surface encompassed by the heat exchange area and facing the power module is designed as a plane section in order to enable a planar heat input of a power module into the heat exchange area of ​​the base part.

[0084] It is also advantageous that this design allows power modules to be arranged on the cover part side and the base part side and thus to provide a cooling device with which an increased number of power modules can be cooled.

[0085] When providing power modules arranged on the cover part side and the base part side, the cooling capacity of the respective cooling chamber is preferably increased by appropriately designing the interior, since in such a case one cooling chamber is typically intended to dissipate the heat input from two opposing power modules.

[0086] The cooling capacity can be increased by increasing the partial coolant flow through the cooling chamber, in particular by increasing the cross-sectional area of ​​the cooling chamber perpendicular to the flow direction. Furthermore, the cooling capacity can be increased by increasing the number of pin-shaped cooling elements or by adjusting their dimensions.

[0087] In a further embodiment of the cooling device, the interior space has a plurality of support elements for mechanically stabilizing the cooling device, in particular the interior space boundary, wherein the support elements are designed as part of the base part and, in the closed state, contact the cover part mechanically, preferably in a materially bonded manner.

[0088] In particular, such support elements can be provided in the area of ​​the inlet and / or outlet openings. These serve to provide mechanical stabilization during operation, during which considerable stresses can occur in parts of the cooling system due to thermal and fluid-mechanical processes.

[0089] Furthermore, such support elements simplify the arrangement of the power modules on the cooling device, as the support elements can apply sufficient counterforce when installing power modules on the heat exchange areas. The power modules can be attached, for example, by soldering or sintering to the surface of the heat exchange area facing the power module.

[0090] Such support elements can also function as guide elements or cooling elements, which guide a coolant flow or partial coolant flow or transfer heat to the coolant flow or partial coolant flow. Stiffening ribs can also be provided on the base and / or ceiling sections as support elements to minimize or prevent deformation of the cooling device during operation—due, for example, to fluidic and / or thermal stress.

[0091] Furthermore, the invention particularly relates to a cooling arrangement comprising at least a first and a second power module and a cooling device according to one of the preceding claims, wherein the first power module is in thermally conductive contact with a heat exchange region associated with the first cooling chamber, and the second power module is in thermally conductive contact with a heat exchange region associated with a second cooling chamber. Thus, the invention extends not only to the cooling device, but also to the arrangement of at least two, in particular three, power modules connected to the respective heat exchange region of the cooling device.

[0092] The above statements regarding the cooling device apply accordingly to the cooling arrangement insofar as they concern the cooling device. To the extent that, within the scope of the above statements, the at least two power modules or at least one of the at least two power modules can only be arranged on the cooling device in a specific manner, they are part of the cooling arrangement.

[0093] In an advantageous embodiment of the cooling arrangement, the interior boundary is formed in two parts, wherein the two-part interior boundary comprises a solid-formed base part having at least two cooling chambers, as well as a, in particular stamped, cover part, wherein the base part and the cover part, in the closed state, close the interior in such a way that no coolant escapes between the base part and the cover part during operation.

[0094] At least one of the at least two power modules can be arranged on the cover part side. In particular, the at least two power modules can be arranged on the cover part side. Alternatively, at least one of the at least two power modules can be arranged on the base part side. In particular, the at least two power modules can be arranged on the base part side. Further alternatively, two power modules can be assigned to at least one cooling chamber of the at least two, preferably three, fluidically separated cooling chambers arranged one behind the other in the flow direction, wherein a first power module of the at least two power modules assigned to the cooling chamber is arranged on the base side and a second power module of the at least two power modules assigned to the cooling chamber is arranged on the cover side.In particular, two power modules can be assigned to each of the at least two, preferably three, cooling chambers arranged one behind the other in the flow direction and fluidically separated from one another, one of which is arranged on the bottom part side and one on the cover part side.

[0095] The arrangement of a power module, in particular a plurality of power modules, on the cover part side is advantageous for the reasons described above. In particular, the cover part is easy to manufacture, especially in a flat form from a thin metal strip, which allows for easy arrangement of the power modules and enables a flat heat input into the heat exchange surface.

[0096] In a further embodiment of the cooling arrangement, the interior boundary is formed in two parts, wherein the two-part interior boundary comprises a solid-formed base part having at least two cooling chambers, and a, in particular stamped, cover part, wherein the base part and the cover part, in the closed state, close the interior in such a way that no coolant escapes between the base part and the cover part during operation, wherein at least one of the at least two power modules is arranged on the base part side.

[0097] In a further embodiment, the cooling arrangement has at least one power module, in particular a plurality of power modules, which is or are arranged on the cover part side, and at least one power module, in particular a plurality of power modules, which is or are arranged on the base part side. Character description

[0098] Advantageous embodiments of the invention are explained below with reference to the accompanying figures. They show: Fig. 1 a perspective view of an exemplary cooling arrangement and its components in a first configuration, Fig. 2 a plan view of an open base part of an exemplary cooling device, Fig. 3 a sectional view through an interior of an exemplary cooling device perpendicular to the longitudinal center axis, Fig. 4 is a perspective view from below of an exemplary cooling arrangement in a second configuration, and Fig. 5 a perspective view of the cooling arrangement from Fig. 4 without lid part.

[0099] The figures are merely schematic representations and serve only to illustrate exemplary embodiments of the invention. Identical or equivalent elements are provided with the same reference numerals throughout. The respective reference numerals are generally used only for the figure in which they are first used and are assumed to be familiar in subsequent figures.

[0100] Fig. Figure 1 shows a perspective view of a cooling assembly 100 with components shown separately. This assembly comprises a cooling device 10 and a first power module 21, a second power module 22, and a third power module 23. The cooling device 10 is constructed in two parts and includes a base part 91 produced by forging and a cover part 92, which are shown spatially separated. Fig. 1 shows a first configuration according to which an arrangement of the power modules 21, 22 and 23 is provided on the cover part 92.

[0101] The base part 91 and the cover part 92 can be sealed together in such a way that no coolant leaks between the base part 91 and the cover part 92 during operation. This can be achieved by appropriate connecting elements, such as screws or rivets. In particular, a coolant-tight seal can also be achieved by brazing or laser welding the sealing interfaces of the base part 91 and the cover part 92.

[0102] The base part 92 comprises an interior space 30 through which coolant can flow during operation. The interior space 30 is bounded on the outside by the interior boundary 40, typically an outer wall of the base part 91 or the cover part 92.

[0103] The interior boundary 40 has an inlet opening 41 through which the coolant can flow into the interior 30 during operation. Furthermore, the interior boundary 40 has an outlet opening 42 through which the coolant can flow out of the interior 30 during operation. The inlet opening 41 and the outlet opening 42 are in the Fig. 1, they are formed in the base part 91. Alternatively, they can also be provided or formed in the cover part 92.

[0104] During steady-state operation, the coolant thus flows from the inlet opening 41 to the outlet opening 42. This macroscopic flow direction of the coolant is referred to as flow direction S. The coolant entering the interior space 30 through the inlet opening 41 forms the coolant flow.

[0105] The interior space 30 is designed such that a coolant flow entering the interior space 30 through the inlet opening can be divided into coolant partial flows after entry by appropriate design of the interior space 30.

[0106] The interior 30 can comprise a plurality of structures that contribute to the formation of the coolant partial flows. These are described in more detail in the description sections. Fig. 2 and Fig. 3 explained.

[0107] In particular, the interior space 30 comprises a first cooling chamber 51, a second cooling chamber 52 and a third cooling chamber 53, which are arranged one behind the other in the flow direction S.

[0108] During operation, a significant portion of the waste heat of the power modules 21, 22, or 23 is fed to the respective cooling chamber 51, 52, or 53 and there released to the partial coolant flow flowing through the respective cooling chamber 51, 52, or 53.

[0109] The cover part 92 is formed as a flat sheet of low thickness, for example with a thickness of at least 0.5 mm, in particular with a thickness of 0.8 mm to 10 mm, in particular with a thickness of up to 5 mm, preferably with a thickness of between 1 mm and 3 mm. Furthermore, the cover part 92 has a plurality of heat exchange areas, which serve to dissipate heat from the respective power modules 21, 22, 23 into the interior 30 of the cooling device 10.

[0110] A first heat exchange area 61 is provided for heat exchange with the first power module 21, a second heat exchange area 62 is provided for heat exchange with the second power module 22, and a third heat exchange area 63 is provided for heat exchange with the third power module 23.

[0111] A heat exchange area 61, 62, 63 is typically the area through which the majority of the waste heat of a power module 21, 22 or 23 can be transferred to the cooling device 10. Typically, the heat exchange area is between the respective cooling chamber 51, 52 or 53 and the area defined by the interior boundary 40, in particular according to Fig. 1 from the cover part 92, which is provided for the arrangement of the power module 21, 22 or 23 on the cooling device 10.

[0112] The heat exchange areas 61, 62 and 63 are the respective Fig. 4, not shown, are assigned to cooling chambers 51, 52, and 53, respectively. This means that, in the viewing direction perpendicular to the flat surface of the cover part 92, the surfaces of the heat exchange regions 61, 62, 63 essentially overlap with the surfaces projected in this direction of the cooling chambers 51, 52, and 53 respectively assigned to the heat exchange region 61, 62, and 63. Preferably, the cooling chambers 51, 52, and 53 have a projected surface that is equal to or larger than the contact surface of a power module 21, 22, and 23, respectively.

[0113] The contact surface of the power module 21, 22, 23 is the surface of the power module 21, 22, 23 which, when the power module is arranged on the cooling device 10, is in contact with the cooling device 10, or the surface through which the waste heat can essentially be dissipated to the cooling device 10 or the respective heat exchange area 61, 62, 63. The contact surface of the power module 21, 22, or 23 is preferably flat.

[0114] Fig. 2 shows a top view of the Fig. 1 in the open state. The illustrated base part 91 has a longitudinal center axis L. The first, second, and third cooling chambers 51, 52, and 53, respectively, are arranged one behind the other symmetrically to the longitudinal center axis L in the flow direction S.

[0115] Each of the cooling chambers 51, 52 and 53 has a plurality of pin-shaped cooling elements 54. These extend from the inlet or outlet opening-side interior boundary 40, in other words from the bottom of the bottom part 91, to the non- Fig. 2 shown cover part.

[0116] In the closed state, the pin-shaped cooling elements 54 of each cooling chamber 51, 52, 53 are integrally connected to the cover part so that the heat entering during operation via the respective heat exchange area 61, 62 or 63 of the cover part can be effectively dissipated via the pin-shaped cooling elements 54 to the coolant flowing around the pin-shaped cooling elements 54.

[0117] The pin-shaped cooling elements 54 can be designed in various ways. In particular, the cooling performance achievable by the respective cooling chambers 51, 52, or 53 can be adjusted by varying their number and shape.

[0118] The coolant flow entering the base part 91 can be divided into various coolant sub-flows by appropriately designing the interior space 30 of the cooling device 10. This is achieved in particular by providing appropriate guide elements and dimensioning inlet openings in the interior space 30 for the coolant flow or for the coolant sub-flows.

[0119] The interior space 30 is designed such that a first coolant partial flow K1 can be fed to the first cooling chamber 51. An inlet region 51' of the first cooling chamber 51 is preferably arranged symmetrically, in particular transversely, to the longitudinal center axis L, with a center of the inlet opening 41 being arranged on the longitudinal center axis L. In particular, the interior space 30 is designed such that, after entering the interior space 30, the coolant flows directly into the first cooling chamber, i.e., without the presence of a further guide element between the inlet opening 41 and the inlet region 51' of the first cooling chamber 51.

[0120] The interior space 30 is further configured such that the first coolant flow K1 can be guided around the second and third cooling chambers 52 and 53, respectively, after exiting the first cooling chamber 51.

[0121] Furthermore, the interior space 30 is designed such that a coolant partial flow in the form of a coolant residual flow Kr, resulting from the coolant flow minus the first coolant partial flow K1, can be guided around the first cooling chamber 51.

[0122] The first cooling chamber 51 comprises a delimiting element 73 assigned to it. The delimiting element 73 of the first cooling chamber 51 delimits the first cooling chamber 51 perpendicular to the flow direction S and prevents the first coolant partial flow K1 from mixing with the coolant residual flow Kr that can be guided around the first cooling chamber 51 when flowing through the first cooling chamber 51.

[0123] The coolant residual flow Kr can also be guided by means of the limiting element 73 of the first cooling chamber 51, which cooperates with a first guide element 71. The first guide element 71 is according to Fig. 1 the surface of the interior boundary 40 facing the interior, in particular a part of a side wall of the interior boundary 40.

[0124] In particular, to form an inlet area 75 of the cooling channel, a separate structure in the form of additional guide elements can also be provided in the interior space 30.

[0125] In the present case, the guide element 71 and the limiting element 73 of the first cooling chamber 51 form an inlet region 75 of a cooling channel through which the coolant residual flow Kr flows into the cooling channel and can be guided around the first cooling chamber 51.

[0126] Downstream of the inlet region 75, the cooling channel comprises a second guide element 72, by means of which the coolant residual flow Kr can be divided into a second coolant partial flow K2, which is assigned to the second cooling chamber 52, and a third coolant partial flow K3, which is assigned to the third cooling chamber 53. The coolant partial flows K1, K2, and K3 can be of the same size or different, depending on the heat dissipation requirements of the respective assigned power modules 21, 22, and 23, respectively, or the cooling capacity of the cooling chambers 51, 52, and 53 assigned to the power modules 21, 22, and 23.

[0127] The second cooling chamber 52 comprises a first limiting element 74 associated therewith and a second limiting element 74' associated therewith. The first limiting element 74 serves to ensure that, during operation, the second coolant partial flow K2, when flowing through the second cooling chamber 52, does not mix with parts of the third coolant partial flow K3 that have not yet passed through the third cooling chamber 53. The second limiting element 74' serves to ensure that the second coolant partial flow K2, while flowing through the second cooling chamber 52, does not mix with the parts of the first coolant partial flow K1 that have already left the first cooling chamber 51.

[0128] The third cooling chamber 53 also comprises a limiting element 76 associated therewith. This has the function of preventing mixing of the third coolant partial flow K3 with the first and second coolant partial flows K1 and K2, respectively, which are guided around the third cooling chamber 53 while flowing through the third cooling chamber 53.

[0129] In particular, this limiting element 76 of the third cooling chamber 53 prevents mixing of the coolant partial flow K3 when flowing through the third coolant chamber 53 with the parts of the first and second coolant partial flows K1 and K2, respectively, which have already passed their respective associated cooling chambers 51 and 52.

[0130] The interior space 30 is designed such that, during operation, the third coolant flow K3, after flowing through the third cooling chamber 53, flows directly to the outlet opening 42 without the presence of a further guide element between the outlet region 53' of the third cooling chamber 53 and the outlet opening 42.

[0131] In particular, the outlet region 53' of the third cooling chamber 53 is arranged symmetrically to the longitudinal center axis L, wherein the center of the outlet opening 42 is arranged on the longitudinal center axis L. The sum of the first coolant partial flow K1 and the second coolant partial flow K2 can be fed to the outlet opening 42 asymmetrically to the longitudinal center axis L.

[0132] All limiting elements 73, 74, 74' or 75 and guide elements 71 or 72, or a subset thereof, can simultaneously be designed as support elements 80. These thus serve not only to guide the coolant but also to mechanically stabilize the cooling device 10.

[0133] A plurality of support elements 80 can be provided, in particular, in the region of the inlet opening 41 and the outlet opening 42. In particular, a plurality of support elements can each be arranged concentrically or radially to a center point of the inlet opening 41 and / or the outlet opening 42.

[0134] These support elements 80 serve to keep the mechanical stress in the thin sheet metal of the cover part low under operating pressure. A large "self-supporting" surface of the cover part would lead to high stresses in the cover part during operation, especially if it is designed as a thin sheet metal. The support elements 80 and their connection, particularly by means of a material bond, to the cover part can significantly reduce these stresses during operation.

[0135] Fig. 3 shows a representation of a floor part from Fig. 1 and Fig. 2 from an elevated perspective, which is shown cut approximately at the level just behind an inlet area of ​​the second cooling chamber 52. By Fig. 3 thus gives an impression of a cross-section of the interior 30.

[0136] Out of Fig. 3 shows that the inlet region 75 of the cooling channel is also influenced by the support element 80, which is arranged radially around the inlet opening 41 and is closest to the inlet region 75. Thus, this support element 80 not only has a supporting function for mechanically stabilizing the cooling device 10, but also a guiding function for the coolant flow in the interior space 30, in particular for the residual coolant flow entering the inlet region 75 of the cooling channel.

[0137] Furthermore, a second boundary element 73' associated with the first cooling chamber 51 is shown. This boundary element 73' delimits the first cooling chamber 51 from a coolant-inaccessible area of ​​the interior 30.

[0138] It can thus be provided that not the entire interior space 30 serves to guide the coolant, but the interior space 30 has “dry areas” that are not accessible to the coolant, the presence of which results from the desired coolant distribution and the desired flow behavior of the coolant in the interior space 30 during operation of the cooling device.

[0139] Furthermore, Fig. 3 that the pin-shaped cooling elements 54 of the cooling chambers 51, 52, and 53 are a one-piece formation of the base part 91, and not separate components of the cooling device 10 (see sectional plane). Furthermore, this illustration shows that the height of the cooling chambers 51 and 52 is significantly less than the height of the inlet region 75 of the cooling channel. In other words, the U-shaped cross-section of the surface of the interior boundary 40 facing the interior space 30 is raised in steps in the region of the cooling chambers 51, 52, and 53. These differences in the passage cross-sections for the partial coolant flows serve to adjust the back pressure and, consequently, the adjustment of the partial coolant flows. This also makes it clear that, instead of changing the height in the inlet region 75 of the cooling channel, the width could alternatively be varied to adjust the back pressure.

[0140] The first coolant partial flow, which enters the first cooling chamber 51 during operation, has - when using an incompressible liquid as the coolant - an increased flow velocity due to the lower height of the cooling chamber (compared to a non-reduced height of the cooling chamber), while the coolant residual flow in the inlet region 75 of the cooling channel has an increased volume flow and an increased flow velocity compared to the first coolant partial flow, with a simultaneously lower back pressure. By adjusting the passage cross-sections in the region of the cooling chambers and in the region of the inlet region 75 of the cooling channel, the flow velocity, volume flow, and back pressure can be adjusted, whereby the overall back pressure at the inlet opening is reduced by a direct flow into the first cooling chamber (and direct flow out of the last cooling chamber).

[0141] A high flow velocity in the respective cooling chamber has the advantage that more heat can be transferred from the pin-shaped cooling elements 54 to the coolant and dissipated.

[0142] Furthermore, Fig. 3 that the coolant residual flow, which flows into the inlet region 75 of the cooling channel, can be further divided by means of the second guide element 72. By means of the second guide element 72, the coolant residual flow can be divided into the second coolant partial flow and the third coolant partial flow, wherein the second coolant partial flow only flows through the second cooling chamber 52 and the third coolant partial flow only flows through the Fig. 3 third cooling chamber, not shown, can be flowed through.

[0143] Fig. Figure 4 shows a perspective view of the cooling assembly 100 with a separate view of the components in a second configuration. The cooling assembly 100 comprises a cooling device 10 with a solid-formed base part 91 and a cover part 92.

[0144] Furthermore, the cooling arrangement 100 comprises a first power module 21, a second power module 22 and a third power module 23, which are arranged during operation on the surfaces of the heat exchange regions 61, 62 and 63 facing away from the interior.

[0145] According to the second configuration, the heat exchange areas 61, 62, and 63 are enclosed by the solid-formed base part 91. The power modules 21, 22, and 23 are intended for arrangement on a flat surface of the base part 91 facing away from the interior space, which extends between the inlet opening 41 and the outlet opening 42. Furthermore, the coolant flow K entering through the inlet opening 41 during operation is designated, which coolant flow K exits again from the outlet opening 42 after flowing through the interior space.

[0146] The three heat exchange areas 61, 62 and 63 are assigned to the respective Fig. 4, three cooling chambers (not shown), i.e., viewed perpendicular to the flat surface, the surfaces of the heat exchange regions 61, 62, 63 essentially overlap with the projected surface of the respective cooling chamber in this direction. Preferably, the cooling chamber has a projected surface that is equal to or larger than the contact surface of a power module 21, 22, or 23. Fig. 4 also shows the cover part 92 with which the base part 91 can be closed.

[0147] Fig. 5 shows a perspective view of the cooling arrangement 100 without the cover part 91 from an elevated view with a separate illustration of the base part 91 and the three power modules 21, 22 and 23 that can be arranged between the inlet opening 41 and the outlet opening 42. The interior space 30 for a cooling arrangement 100 according to this second configuration can be designed in the same way as in connection with Fig. 1 to Fig. 3 explained.

[0148] Furthermore, a combination of the configuration of the cooling arrangement 100 according to the Fig. 1 and Fig. 2 with the configuration of the cooling arrangement 100 according to Fig. 4 and Fig. 5 can be provided, for example, by arranging three power modules on the base part 91 and three power modules on the cover part 92, with two opposing power modules each being assigned to one of the cooling chambers.

[0149] Furthermore (in an embodiment not shown), the cover part 92 can be manufactured as a solid-formed cover part, similar to the base part 91, and the interior boundary 40, inlet opening 41, outlet opening 42, pin-shaped cooling elements 54, first guide element 71, second guide element 72, boundary element 73 for the first cooling chamber 51, first boundary element 74 for the second cooling chamber 52, second boundary element 74' for the second cooling chamber 52, first boundary element 76 for the third cooling chamber 53, and / or support element(s) 80 can be partially and / or completely formed integrally with the cover part 92. This can be advantageous if the base part 91 and the cover part 92 are formed in a less complex manner, thus reducing overall manufacturing costs despite the use of a second solid-formed part compared to a more complex solid-formed part and a simple stamped part. However, this requires a case-by-case assessment.Even in such an embodiment, the base part 91 and the cover part 92 can be connected to one another in a materially bonded manner.

[0150] Since the devices described in detail above are exemplary embodiments, they can be modified widely by those skilled in the art without departing from the scope of the invention. In particular, the mechanical arrangements and the relative dimensions of the individual elements are merely exemplary. LIST OF REFERENCE SYMBOLS 10 Cooling device 21 Power module, first 22 Power module, second 23 Power module, third 30 Interior 40 Interior boundary 41 Entrance opening 42 Exit opening 51 Cooling chamber, first 51' Inlet area of ​​the first cooling chamber 52 Cooling chamber, second 53 Cooling chamber, third 53' Outlet area of ​​the third cooling chamber 54 Cooling element, pin-shaped 61 Heat exchange area, first 62 Heat exchange area, second 63 Heat exchange area, third 71 Guide element, first 72 Guide element, second 73 Limiting element, first cooling chamber 74 Limiting element, second cooling chamber, first 74' limiting element, second cooling chamber, second 75 Inlet area of ​​the cooling channel 76 Limiting element, third cooling chamber, first 80 support element 91 Base part, solid formed, especially made of aluminum 92 Cover part, stamped, in particular made of aluminum 100 cooling arrangement K coolant flow K1 Coolant partial flow, first K2 Coolant partial flow, second K3 Coolant partial flow, third Kr coolant residual flow L Longitudinal center axis S Flow direction QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] DE 102019202425 A1

[0012] DE 10 2020 207 966 A1

[0013]

Claims

[1] Cooling device (10) for at least two electronic power modules (21, 22, 23) of a drive train, in particular for a traction inverter, comprising an interior space (30) delimited by an interior space boundary (40), wherein the interior space boundary (40) has an inlet opening (41) for supplying a coolant into the interior space (30) and an outlet opening (42) for discharging the coolant from the interior space (30), and a coolant flow (K) can flow through the interior space (30) from the inlet opening (41) to the outlet opening (42) in the flow direction (S), wherein the interior space (30) between the inlet opening (41) and the outlet opening (42) has at least two, preferably three, cooling chambers (51, 52) arranged one behind the other in the flow direction (S) and fluidically separated from one another.53), wherein each cooling chamber (51, 52, 53) can be supplied with waste heat from a power module (21, 22, 23) that can be assigned to the respective cooling chamber (51, 52, 53) by means of a heat exchange region (61, 62, 63) enclosed by the interior boundary (40), wherein the interior space (30) is designed in such a way that the coolant flow (K) can be divided in the interior space (30) and in the flow direction (S) downstream of the inlet opening (41), and that coolant partial flows (K1, K2, K3) that can be generated from the inflowing coolant can be guided in such a way that each coolant partial flow (K1, K2, K3) provided for flowing through a cooling chamber (51, 52, 53) flows through only one of the cooling chambers (51, 52, 53). [2] Cooling device according to claim 1, wherein at least one of the at least two cooling chambers (51, 52, 53) has a plurality, in particular a multiplicity, of pin-shaped cooling elements (54) which are thermally conductively connected to the heat exchange region (61, 62, 63) assigned to this cooling chamber (51, 52, 53), wherein a number and a dimensioning of the cooling elements (54) is designed such that, for a predetermined partial coolant flow (K1, K2, K3) through the respective cooling chamber (51, 52, 53), a desired cooling performance is achieved by means of the respective cooling chamber (51, 52, 53) and / or a predetermined pressure loss is not exceeded. [3] Cooling device according to one of the preceding claims, wherein the interior space (30) is designed such that the first cooling chamber (51) in the flow direction (S) can be acted upon by a first coolant partial flow (K1), and the first coolant partial flow (K1) behaves in relation to the coolant flow (K) entering the interior space in the same way as the first cooling chamber (52) to the number of all existing cooling chambers (51, 52, 53). [4] Cooling device according to one of the preceding claims, wherein the at least two cooling chambers (51, 52, 53) are arranged symmetrically to a longitudinal center axis (L) of the interior boundary (40), wherein a boundary element (73) of the first cooling chamber (51) arranged at least in sections parallel to the flow direction (S) in the flow direction (S) together with a first guide element (71) running parallel to the flow direction (S), in particular a part of the interior boundary (40), form at least one inlet region (75) of a cooling channel, wherein the cooling channel is designed to guide the coolant partial flow (Kr) entering the inlet region (75) of the cooling channel around the first cooling chamber (51). [5] Cooling device according to claim 4, wherein the cooling channel has at least one second guide element (72) which is designed to guide the coolant partial flow (Kr) entering the cooling channel at least partially to at least one second cooling chamber (52). [6] Cooling device (10) according to one of the preceding claims, wherein the interior boundary (40) is formed in two parts, wherein the two-part interior boundary (40) comprises a solid-formed base part (91) comprising the at least two cooling chambers (51, 52, 53), and a cover part (92), in particular a punched or laser-cut one, wherein the base part (91) and the cover part (92) in the closed state close the interior (30) in such a way that no coolant escapes between the base part (91) and the cover part (92). [7] Cooling device according to claim 6, wherein the solid-formed base part (91) has the inlet opening (41) and the outlet opening (42) and the cover part (92) has at least one of the heat exchange areas (61, 62, 63), in particular, wherein a surface of the heat exchange area (61, 62, 63) facing the assignable power module (21, 22, 23) is designed as a plane section for arranging a power module (21, 22, 23) on the surface. [8] Cooling device according to claim 7, wherein the cover part (92), in the closed state, is connected in a heat-conducting, in particular materially bonded, manner to the pin-shaped cooling elements (54) of the at least two cooling chambers (51, 52, 53) encompassed by the solidly formed base part (91). [9] Cooling device according to claim 6, wherein the solid-formed base part (91) has the inlet opening (41) and the outlet opening (42), wherein the solid-formed base part (91) further comprises at least one of the heat exchange regions (61, 62, 63) which is arranged between the inlet opening (41) and the outlet opening (42), in particular wherein a surface of the heat exchange region (61, 62, 63) facing the assignable power module (21, 22, 23) is designed as a plane section for arranging a power module (21, 22, 23) on the surface. [10] Cooling device according to one of the preceding claims 6 to 9, wherein the interior (30) has a plurality of support elements (80) for mechanically stabilizing the cooling device (10), wherein the support elements (80) are designed as part of the base part (91) and, in the closed state, contact the cover part (91) mechanically, preferably in a materially bonded manner. [11] Cooling arrangement (100) comprising at least a first and a second power module (21, 22, 23) and a cooling device (10) according to one of the preceding claims, wherein the first power module (21) is in thermally conductive contact with a heat exchange region (61) associated with the first cooling chamber (51), wherein the second power module (52) is in thermally conductive contact with a heat exchange region (62) associated with a second cooling chamber (52). [12] Cooling arrangement according to claim 11, wherein the interior boundary (40) is formed in two parts, wherein the two-part interior boundary (40) comprises a solid-formed base part (91) with the at least two cooling chambers (51, 52, 53), and a, in particular stamped, cover part (91), wherein the base part (91) and the cover part (92) in the closed state close the interior (30) in such a way that no coolant escapes between the base part (91) and the cover part (92) during operation. [13] Cooling arrangement according to claim 11 or 12, wherein at least one of the at least two power modules (21, 22, 23) is arranged on the cover part side. [14] Cooling arrangement according to one of claims 11 to 13, wherein at least one of the at least two power modules (21, 22, 23) is arranged on the bottom side. [15] Cooling arrangement according to one of claims 11 to 14, wherein the interior boundary (30) is formed in two parts, wherein the two-part interior boundary (40) comprises a solid-formed base part (91) having the at least two cooling chambers (51, 52, 53), and a, in particular stamped, cover part, wherein the base part (91) and the cover part (92) in the closed state close the interior (30) in such a way that no coolant escapes between the base part (91) and the cover part (92) during operation, wherein at least one of the at least two power modules is arranged on the base part side.

Images