Fluid pressure assisted seal for a directional control valve and directional control valve

Abstract

The invention relates to a seal (1) for forming a sealing contact with a housing and a rotary slide valve of a directional control valve arranged in the housing, for adjusting the flow of a fluid, such as a coolant, wherein the seal has a pressure chamber (13) and at least one communication channel (15) for flooding the pressure chamber with the fluid, wherein the pressure chamber surrounds a fluid passage opening of the seal, in particular along the outer contour of the fluid passage opening.

Description

[0001] Patent application October 17, 2023 W31801WO WOCO INDUSTRIETECHNIK GMBH, Hanauer Landstraße 16, 63628 Bad Soden-Salmünster Fluid pressure-assisted seal for a directional control valve and directional control valve The invention relates to a seal for forming a sealing contact with a housing and a rotary slide valve of a directional control valve arranged in the housing for adjusting the flow of a fluid, such as a coolant. Furthermore, the invention relates to a directional control valve with a seal. Furthermore, the invention relates to a motor vehicle fluid flow line system, such as a motor vehicle thermal management system, with a directional control valve. A directional control valve is to be understood in particular as a multi-way valve. Generic multi-way valves are used, for example, in motor vehicles for their thermal management and are used in particular to conduct coolants, such as water or oils, in order to cool, heat or generally temperature control components, particularly in the engine compartment. Such multi-way valves are inusually equipped with a rotary valve as a valve element in order to fluidically connect or separate fluid lines connected to the valve depending on the position of the rotary valve. For this purpose, the rotary valve is arranged in a housing so that it can rotate. To allow rotation in the housing, play is provided between the rotary valve and the housing, creating a gap between the rotary valve and the housing. To prevent leakage through this gap between separate fluid channels, seals are arranged between the rotary valve and the housing, which seal the fluid lines from the gap. For the most reliable seal, a high contact force is required, matched to the acting fluid pressure. A high contact force can be achieved, for example, by using springs. However, this increases the complexity and thus the costs andSusceptibility to failure and the installation space of the directional control valve. Alternatively, a high contact force can be achieved by using seals with a particularly high oversize compared to the movement play between the rotary valve and the housing. However, this leads to a high expenditure of force during assembly and operation of the rotary valve. From WO 2022 / 025513, it is known to address this problem by a sealing arrangement with a hard and sliding contact surface facing the rotary valve and a soft contact surface facing the housing. This can reduce the required assembly force due to lower frictional resistance between the rotary valve and the seal along the hard contact surface. In addition, the torque required to position the valve element during operation can be reduced, which reduces the required costs and the required installation space for the actuator. A disadvantage of this solution, however, isthat the different mechanical requirements for the two sealing surfaces require either complex two-part structures or technically demanding manufacturing processes, such as the "two-shot extrusion process" mentioned in WO 2022 / 025513. The object of the present invention is to overcome the disadvantages of the prior art, in particular to provide a seal for a directional control valve and a directional control valve with which the tightness between the rotary slide and the housing can be increased without increasing the complexity of the rotary slide and / or the force required for assembly and operation. This object is achieved by the subject matter of the independent claims. Preferred embodiments are specified in the dependent claims. One aspect of the invention relates to a seal for forming a sealing contact with a housing and a rotary slide arranged in the housing of a directional control valve for adjusting the flow of aFluid, such as a coolant. The seal has a pressure chamber and at least one communication channel for flooding the pressure chamber with the fluid. The seal is preferably designed to form such a sealing contact with the housing and the rotary valve such that a fluid line adjoining the housing can be sealed by means of the seal with respect to an intermediate space between the rotary valve and the housing. In particular, the seal is designed to reduce, preferably prevent, a fluid flow from the intermediate space into the fluid line and vice versa when the rotary valve is closed with respect to the fluid line. For this purpose, the seal preferably has a fluid passage opening which is completely surrounded by a sealing body of the seal. The sealing body can in particular comprise the pressure chamber described below, the inner leg, the outer leg, support ribs and / or the base of the seal.Preferably, the sealing body comprises elastic, in particular elastomeric, material and is in particular formed entirely therefrom. The fluid passage opening preferably has a diameter of at least 4 mm, preferably at least 8 mm, particularly preferably at least 12 mm, at least 16 mm, at least 20 mm, at least 24 mm, or at least 30 mm. However, the fluid passage opening does not necessarily have to be circular. It can, for example, also have an oval shape. In this case, the oval shape can have semicircular sections, preferably with predefined diameters, and a rectangular section connecting the semicircular sections. The length (distance between the semicircular sections) of the rectangular section can preferably be at least 3 mm, particularly preferably at least 5 mm, 10 mm, or 15 mm. The width of the rectangular section (length) can preferably have the same minimum dimensions as the previouslydescribed diameter, particularly preferably the same width as the diameter. A further embodiment of the passage opening can be a disk-section-shaped passage opening. In the end face designs described in detail below, the seal can have a plurality of passage openings, for example at least two, three, four, five or six passage openings. In this embodiment, the seal can be circular, for example, wherein the plurality of passage openings are separated from one another in the circumferential direction by sealing material of the seal. The pressure chamber can be formed by a groove made in the sealing material of the seal, in particular a V-shaped groove. Preferably, the pressure chamber, in particular groove, completely surrounds the fluid passage opening. Apart from the communication channel, the pressure chamber can be completely or partially enclosed by the sealing material of the seal.Preferably, the pressure chamber is incorporated into the seal in such a way that, in the assembled state, it is completely enclosed by the sealing material and the housing, in particular apart from the at least one communication channel. In particular, the pressure chamber can have an opening, in particular an annular opening, on its side facing the housing, which can be closed by the housing in the assembled state in order to completely enclose the pressure chamber, in particular apart from the at least one communication channel. By flooding the pressure chamber via the at least one communication channel, the fluid pressure can be used to provide, in particular to increase, the contact force between the seal and the rotary valve and the housing. The seal is in particular designed such that the pressure chamber is pressed against the rotary valve and / or the housing as a result of the flooding with the fluid. In particular, the seal is in such a waydesigned so that the pressure chamber is inflated, particularly in a balloon-like manner, by flooding with the fluid. By inflating the pressure chamber, it is compressed between the rotary valve and the housing, so that preferably resulting elastic restoring forces of the sealing material increase the contact pressure, thereby improving the tightness. The inventors have recognized that the inventive principle of the pressure chamber with communication channel allows the fluid pressure to be used to provide a self-reinforcing contact pressure. This, on the one hand, reduces the excess between the seal and the play of movement between the rotary valve and the housing, which requires less force for the assembly of the seal. During operation, the fluid pressure is then used to increase the contact pressure in such a way that leakage is reduced, in particular avoided. It has proven particularly advantageous that at higher fluid pressures, theThe contact pressure is also increased. As a result, the seal according to the invention can be used for different pressure conditions and always provides the required contact pressure. As a result, the fluid pressure itself ensures an adequate contact pressure adapted to the fluid pressure. This can, in particular, prevent unnecessarily high contact forces at low fluid pressures or insufficient contact forces at high fluid pressures. This also allows the drive power of the motors for the rotary valve to be individually adapted to the pressure conditions. The inventors have further discovered that the fluid pressure-assisted contact pressure eliminates the need for contact means such as springs and yet reliably prevents leakage. The seal can therefore preferably be used with directional control valves without separate contact means such as springs. The directional control valves described below are therefore particularly preferably directional control valves,which are free of any contact pressure means, such as springs, present in addition to the elastic material of the seal. As previously described, the pressure chamber is preferably formed by a groove, in particular a V-shaped groove, introduced into the sealing material of the seal. The formation of the pressure chamber by means of a groove reduces the deformation resistance of the seal. As a result, a greater deformation, in particular inflation, of the pressure chamber can be achieved at constant fluid pressure, which in turn increases the contact pressure. Preferably, inflation occurs through an overpressure in the pressure chamber. This can be achieved, for example, by flooding the valve housing, which in turn supplies the pressure chamber with fluid via the communication channels, whereas a line to be closed has a lower pressure, so that an overpressure prevails in the pressure chamber, which inflates the seal. However, even in embodiments and / orIn operating conditions in which an external overpressure acts on the pressure chamber, for example when a fluid-carrying line to be closed has a higher pressure than the flooded housing, the reduced deformation resistance of the seal due to the groove-shaped pressure chamber is advantageous, as this increases compression of the seal, which can also increase the contact pressure between the seal and the rotary valve and the housing. The increased tightness due to the groove-shaped pressure chamber in such operating conditions can also be referred to as backflow resistance. Preferably, the seal is designed to encircle a fluid passage opening of the housing and, in a position of the rotary valve closing the fluid passage opening, to seal an intermediate space between the rotary valve and the housing with respect to the fluid passage opening. The seal can be designed to reduce the contact pressure against the housingand / or the valve member when a higher pressure acts on the seal from the intermediate space than from the fluid passage opening, in particular from a fluid line adjoining it (higher internal pressure) and / or when a higher pressure acts on the seal from the fluid passage opening, in particular from a fluid line adjoining it, than from the intermediate space (higher external pressure). Preferably, the seal is designed to increase the contact pressure both at a higher external pressure and at a higher internal pressure. Preferably, the pressure chamber is designed to be flooded, in particular by means of the at least one communication channel, via the intermediate space between the housing and the rotary valve. Preferably, the increase in the contact pressure at a higher internal pressure is achieved by flooding the pressure chamber with the higher pressure, in particular whereby the seal is inflated like a balloon, in particular as before anddescribed below. Alternatively or additionally, the contact pressure can be increased at higher external pressure by deforming, in particular compressing, the seal in such a way that the seal is pressed in the radial direction (relative to the axis of rotation of the rotary valve) against the rotary valve and / or housing, in particular as a result of compression in the circumferential direction (relative to the axis of rotation of the rotary valve). A further advantage of flooding the pressure chamber is that, in flooded valve housings, part of the pressure acting on the seal from the fluid housing and pushing it towards the fluid line is compensated by the pressure prevailing in the pressure chamber. This can also reduce the risk of the seal slipping into the fluid line, which can lead to malfunctions and leaks. This problem occurs particularly in operating conditions in which the pressure in the housing is higher than in the line to be sealed.For example, with a fluid pressure of 3 bar in the housing and 1.5 bar in the line to be sealed, there is an increased risk in conventional systems that the seal will be pressed into the line. This problem was satisfactorily solved by the inventive solution of flooding the pressure chamber, which compensates for part of the pressure acting on the seal from the housing by the pressure acting in the pressure chamber. A further advantage of the inventive self-reinforcing seal by flooding the channel is that the valve drive can be designed smaller than in conventional systems, since less torque is required for adjustment as long as the contact force is not increased by the fluid pressure. For example, when adjusting the rotary valve, transition states occur in which both the line and the housing are flooded, so that the fluid pressure in the pressure chamber is transferred from the outside to theThe pressure acting in the pressure chamber is compensated. This allows adjustment of the rotary valve with low torque. As soon as the rotary valve is in its final position, in which a line is sealed, the pressure in this line drops, so that excess pressure is again created in the pressure chamber and the self-reinforcing effect of the seal is again generated. The pressure chamber preferably surrounds a fluid passage opening in the seal. The fluid passage opening can, in principle, take on any size and / or shape. For the preferred use described below in automotive fluid flow control systems such as automotive thermal management fluid control systems, in particular automotive cooling circuits, a circular, oval, or disc-shaped shape, as well as the dimensions described above, have proven advantageous for the fluid passage opening. The pressure chamber preferably surrounds the fluid passage opening alongits outer contour. Preferably, the pressure chamber is formed by a groove surrounding the fluid passage opening, in particular a V-shaped groove. Preferably, the pressure chamber, in particular the groove, tapers from a side of the seal facing the housing to a side of the seal facing the rotary valve. Particularly preferably, the pressure chamber is delimited by an inner leg facing the fluid passage opening and an outer leg facing away from the fluid passage opening. Preferably, the inner leg and the outer leg completely surround the fluid passage opening, in particular the inner leg along the outer contour of the fluid passage opening and preferably the outer leg through the pressure chamber at a distance along a contour correspondingly adapted to the contour of the inner leg. Preferably, the inner leg and the outer leg run in the side facing the rotary valve, in particular in the radial direction.towards the rotational axis of the rotary valve, towards each other, preferably wherein the tip, at which the inner leg and the outer leg converge, forms an inner sealing surface facing the rotary valve, which in the assembled state preferably forms a sealing contact between the rotary valve and the seal. Preferably, the inner sealing leg and the outer sealing leg are spread over an angle extending in the circumferential direction, relative to the rotational axis of the rotary valve, in particular extend away from each other in the radial direction, relative to the rotational axis of the rotary valve, in particular in opposite circumferential directions, relative to the rotational axis of the rotary valve. In particular, the previously described V-shaped course of the inner and outer sealing legs in the radial direction can ensure that both at higher internal pressure and at increased external pressure, an increase in the contact pressure of the seal against the rotary valveand / or the housing. In particular, the inner leg and the outer leg converge towards each other in a V-shape. Preferably, the inner leg and the outer leg merge into one another on the side facing the rotary valve and are spaced apart from one another on the side facing the housing. Preferably, the pressure chamber, in particular in the form of a groove, extends between the inner leg and the outer leg. Preferably, the inner leg and the outer leg are designed to bear sealingly against a housing of a rotary valve in the assembled state, so that, apart from the at least one communication channel, the pressure chamber is enclosed by the seal and the housing. Particularly preferably, the inner sealing leg and the outer sealing leg are designed to extend in the radial direction, in particular to widen towards the housing and / or to form a sealing contact on the housing with a groove extending parallel to the outer contour of the rotary valve.extending surface of the housing. In particular, the inner sealing leg and the outer sealing leg each have an outer sealing surface facing the housing, which preferably runs parallel to the outer contour of the rotary valve, in particular is curved such that they can be applied to a surface of the housing that curves in the circumferential direction around the rotary valve. The inventors have recognized that the tapering, in particular V-shaped tapering, of the pressure chamber, in particular by means of the previously described inner and outer legs, creates a self-reinforcing sealing effect even when an excess pressure acts on the pressure chamber from the outside (in relation to the internal pressure in the chamber), namely because the spaced-apart inner and outer legs facing the housing are pressed together by the excess pressure, thereby increasing the contact force between the seal and the housing and between the seal and the rotary valve.reinforce. To form the sealing contact, the inner leg preferably has an outer sealing surface facing the housing and an inner sealing surface facing the rotary valve, wherein the inner sealing surface and / or the outer sealing surface preferably surround the fluid passage opening. Preferably, the inner sealing surface and the outer sealing surface surround the fluid passage opening without interruption. This is to be understood in particular that the inner sealing surface and the outer sealing surface are designed to form a sealing contact with the rotary valve or with the housing that continuously surrounds the fluid passage opening in the assembled state, in particular such that fluid passage along the outer sealing surface and the inner sealing surface is avoided. Preferably, the at least one communication channel is connected to the pressure chamber via the outer leg. Particularly preferably, the seal has at least two, three, four, five or sixCommunication channels. Preferably, the communication channels are connected to the pressure chamber via the outer leg. Preferably, the communication channels are arranged distributed in the circumferential direction around the fluid passage opening, in particular arranged at equidistant intervals from one another. Preferably, a communication opening is provided in the outer leg to form the at least one communication channel. The communication opening can be designed as a recess in a sealing surface of the outer leg facing the housing. In such an embodiment, the communication opening is delimited in the assembled state on the one hand by the outer leg and on the other hand by the housing. As described in detail below, the communication channel further preferably extends between a base of the seal to be applied to the housing and the housing. In an alternative embodiment, however, the communication channel can alsoby an opening, in particular a channel, completely enclosed by the outer leg. The seal preferably has a foot to be placed against the housing with an active surface facing the rotary valve in order to press the foot against the housing via fluid pressure acting on the active surface when the housing is flooded with fluid, in particular to provide a contact pressure between the foot and the housing that counteracts a relative movement between the seal and the housing. This can increase the contact pressure against the housing and thus further prevent the risk of the seal slipping. Preferably, the foot completely surrounds the fluid passage opening. In the embodiments described in detail below with multiple fluid passage openings in a seal, the foot preferably surrounds all fluid passage openings. Preferably, the foot extends, starting from the outer leg in the circumferential direction,relative to the rotational axis of the rotary valve, by at least 50%, 100%, 150%, or 200% of the extent of the outer leg in the circumferential direction. Alternatively or additionally, the foot has a pressure-effective area, which corresponds to at least 50%, 100%, 150%, or 200% of the pressure-effective area of ​​the inner leg and / or outer leg of the seal, with respect to the pressure acting from the space between the rotary valve and the housing. The foot preferably extends parallel to the outer contour of the rotary valve and / or the housing. In particular, the previously described large pressure-effective area and geometry of the seal can prevent sliding of the seal relative to the housing and thus associated leaks. Preferably, the foot adjoins the previously described outer leg. Particularly preferably, the foot adjoins the end of the outer leg facing the housing. Preferably, the foot is adapted to the shape of the housing. In particular,The foot, the outer leg, and the inner leg can together form a curved contact surface for contact with the housing. The curved contact surface can be interrupted, in particular exclusively, by the fluid passage opening, the pressure chamber, and optionally the at least one communication channel. This allows a large contact surface to be formed, via which the foot can be pressed against the housing by the fluid pressure in order to prevent the seal from slipping and / or sliding. The communication channel preferably extends between the foot and the housing in the assembled state. Particularly preferably, the at least one communication channel can have a groove formed in the foot, which fluidically connects an intermediate space between the housing and the rotary valve with the pressure chamber. If there are several communication channels, these are preferably distributed in the circumferential direction around the fluid passage opening, in particular at equidistantspaced circumferentially around these. To form the sealing contact, the seal preferably has an outer sealing surface facing the housing and an inner sealing surface facing the rotary valve, which are made of the same material. In the assembled state of the seal, the sealing surfaces in contact with the rotary valve and the housing, in particular the outer sealing surface and the inner sealing surface of the seal, are preferably made of the same material, in particular made in one piece. The material is preferably an elastomer material. The entire seal is particularly preferably made of the same material, in particular elastomer material. The inner sealing surface and outer sealing surface are particularly preferably formed by the pressure of the previously described inner legs. The previously described inner sealing leg and outer sealing leg particularly preferably form a V-shaped structure,which surrounds the fluid passage opening. The pressure chamber is preferably formed between the inner sealing leg and the outer sealing leg. In particular, the outer leg and the inner leg merge into the inner sealing surface on the side of the seal facing the rotary valve. Particularly preferably, communication openings are provided on the side of the outer leg facing the housing, for example, recesses that form part of the communication channel or completely form the communication channel. The seal preferably has at least one support rib arranged in the pressure chamber, in particular to stabilize the pressure chamber against pressure acting on the pressure chamber from outside the pressure chamber, wherein the at least one support rib preferably extends between the inner leg and the outer leg. The seal preferably has a plurality of support ribs, preferably at least 2, 3, 4, 5, 6, 7, 8, 9,10, 11, 12, 13, 14, 15, or 16 support ribs. The support ribs are preferably arranged circumferentially around the fluid passage opening, in particular at equidistant intervals, within the fluid chamber. Particularly preferably, the support ribs divide the pressure chamber into several chamber sections. Particularly preferably, the support ribs extend from the side of the seal facing the rotary valve, in particular between the inner leg and the outer leg, to the side of the seal facing the housing. Preferably, the support ribs are designed such that a fluid connection is enabled between the chamber sections formed by the support ribs. For this purpose, the support ribs preferably do not extend completely to the outer sealing surface in order to enable a communication opening between the support ribs and the housing for the exchange of fluids between the chamber sections of the pressure chambers. In alternative embodimentsHowever, communication openings can also be formed in the support ribs to enable fluid communication between the chamber sections of the pressure chamber. The inventors have found that the support ribs counteract a collapse of the seal as a result of pressure acting on the pressure chamber from the outside. This can further increase the reliability of the seal. In particular, the support ribs can prevent the seal from being compressed so strongly at higher external pressure that fluid overcomes a sealing contact between the seal and the rotary slide and / or the housing, thereby leading to leakage. Preferably, the at least one communication channel is designed to fluidically connect the pressure chamber to the intermediate space between the housing and the rotary slide of the directional control valve. For this purpose, the seal preferably has, on a side facing the intermediate space, at least one, preferably a plurality of,Communication opening(s) through which fluid from the intermediate space can penetrate into the communication channel and reach the pressure chamber via the communication channel. For this purpose, at least one groove is preferably provided in the outer leg facing away from the fluid passage opening, which groove forms the at least one communication channel. Preferably, a plurality of grooves are provided, each forming a communication channel. Particularly preferably, the at least one groove is provided on the side of the outer leg facing the housing, in particular such that the outer leg, in the assembled state, completely surrounds the communication channel together with the housing. In alternative embodiments, the communication channel can be formed as a hole in the seal, in particular in the outer leg of the seal, which is completely surrounded by sealing material of the seal. Particularly preferably, the groove is not only in the outer leg,but additionally also introduced into the previously described foot, so that the communication channel extends along the outer leg and the foot. Preferably, the foot adjoins the end of the outer leg facing the housing in a flat manner, in particular in a disc shape, and extends in the direction opposite the fluid passage opening. Particularly preferably, the outer leg and the foot form an L-shape in cross-section, of which one leg forms the outer leg and the other leg forms the foot. In this case, one leg preferably extends towards the rotary valve and the other leg extends away from the fluid passage opening, in particular inclined by at least 10°, 20°, 30°, 40°, 50°, 60°, 70°, 80°, 90°, 100°, 110° or 120° to the first leg. Particularly preferably, the inner leg connects in cross-section to the outer leg of the previously described L and forms with it a V-shape that widens towards the housing. In one embodiment,the fluid passage opening is circular. In this embodiment, the pressure chamber preferably extends annularly around the fluid passage opening. The pressure chamber is preferably designed as an annular groove, which preferably tapers in a V-shape towards the side facing the rotary valve. Particularly preferably, the seal in this embodiment has a sealing surface having an uninterrupted annular shape and facing the housing. The sealing surface is preferably designed like the previously described inner sealing surface. In addition, the seal preferably has an outer sealing surface facing the rotary valve, which preferably extends annularly around the fluid passage opening in a uninterrupted manner. The inner sealing surface and the outer sealing surface are preferably formed by the previously described inner leg, in particular connected to one another. Preferably, this outer sealing surface and / or theInner sealing surface on the side of the seal facing the fluid passage opening, in particular the pressure chamber. In addition, the seal preferably has a sealing surface (interrupted sealing surface) that is interrupted in sections in the circumferential direction, in particular annular, and facing the housing. The interrupted sealing surface is interrupted in particular by the at least one previously described communication channel, preferably by a plurality of communication channels that are preferably spaced apart from one another in the circumferential direction, in particular at equidistant intervals from one another. This interrupted sealing surface is preferably formed on the end of the previously described outer leg facing the housing. Particularly preferably, the outer leg runs in the axial direction (relative to the axis of symmetry of the circular fluid passage opening) towards the inner leg, in particular such that the inner leg and theOuter legs form a V-shaped structure. Preferably, the previously described foot adjoins the interrupted annular sealing surface, which foot extends radially outwards, in particular relative to the fluid passage opening, and in particular extends the at least one communication channel along the foot. In particular, the at least one communication channel extends completely through the foot into the pressure chamber, so that fluid can enter the pressure chamber in the radial direction from the outside via the foot through the at least one communication channel. Preferably, the foot completely surrounds the pressure chamber, and in particular the outer leg, in the circumferential direction. The foot can in particular be planar. In an alternative embodiment, the fluid passage opening is oval. In this embodiment, the seal is preferably as previously described for the embodiment with a circular fluid passage opening.described, with the sole exception that the structures described as annular are oval, in particular the pressure chamber, the inner sealing surface, the outer sealing surface, and the partially interrupted sealing surface are oval. In a further embodiment, the seal has at least two, preferably at least three, fluid passages. The fluid passages can have a common flow direction. In the case of symmetrical fluid passages, the flow direction can be defined by the axis of symmetry, in particular run parallel to the axis of symmetry. In the case of non-symmetrical fluid passages, the common flow direction can be defined by the normal of the passage. In an embodiment with at least two fluid passages, these can be arranged offset from one another in the circumferential direction relative to the flow direction.In particular, in such an embodiment the seal can have a central axis around which the at least two fluid passages are arranged offset. For example, the at least two, preferably at least three, fluid passages can be designed in the shape of disc sections. In an embodiment with a plurality of fluid passages the seal preferably has a separate pressure chamber for each seal. Preferably each of the pressure chambers surrounds one of the fluid passages. Preferably each of the pressure chambers has at least one, preferably a plurality of communication channels in order to flood the pressure chamber with the fluid. Preferably communication channels are provided which fluidically connect each of the pressure chambers to the space between the housing and the rotary valve. Alternatively or additionally communication channels can be provided which fluidically connect the pressure chambers to one another.In a particularly preferred embodiment, the seal is disk-shaped and has at least two, preferably at least three, fluid passages arranged in the circumferential direction around the axis of symmetry of the disk. Preferably, in this embodiment, communication channels are provided which connect the pressure chamber in the radial outward direction with the intermediate space and / or communication channels which connect the pressure chambers to one another, in particular in the circumferential direction. Preferably, in such embodiments, the previously described foot can simultaneously form a connecting structure, in particular a web, between the individual fluid passages and pressure chambers, which is preferably, in particular exclusively, interrupted by the communication channels, in particular in the form of grooves. The invention further relates to a directional control valve for adjusting the flow of a fluid, such as aCoolant. The directional control valve is preferably a multi-way valve, particularly preferably a directional control valve with at least three ways, four ways, five ways, six ways, or seven ways. The directional control valve has a housing with at least one fluid passage opening, a fluid line adjoining the fluid passage opening, and a rotary slide valve arranged in the housing. Furthermore, the directional control valve has a seal according to the invention that is in sealing contact with the housing and the rotary slide valve and surrounds the fluid passage opening. Preferably, the previously described fluid passage opening of the seal is aligned with the fluid passage opening of the fluid line. Preferably, the geometry and size of the fluid passage opening of the seal essentially corresponds to the size and geometry of the fluid passage opening of the fluid line. With regard to size, "essential" particularly means deviations in the cross-section of a maximum of + / -40%, 30%, 20%, 10%, 5%, 3% or 1%. However, the fluid passage opening of the seal is particularly preferably at least as large as the fluid passage opening of the fluid line in order to avoid a constriction of the flow cross-section by the seal. Preferably, the hydraulic cross-section of the fluid passage opening in the housing, in the adjoining fluid line, in the seal and preferably in the rotary slide is substantially the same size. Particularly preferably, the hydraulic cross-section of fluid flowing through the directional control valve, in particular between at least two fluid lines adjoining fluid passage openings of the housing, is substantially constant. Preferably, the housing has a plurality of fluid passage openings, particularly preferably at least two, at least three, at least four, at least five or at least six fluid passage openings. Preferably, aFluid line connected. The housing can be cylindrical. The fluid passage openings can be introduced into the casing of the housing, in particular offset from one another in the circumferential direction. Alternatively or additionally, one or more fluid passage openings can be provided on one or both end faces of the housing. Preferably, a seal, in particular according to the invention, can be arranged between the housing and the rotary valve at several fluid passage openings, particularly preferably at each of the fluid passage openings formed in the casing and / or the end face of the housing. The rotary valve is preferably designed to establish and / or prevent a fluid connection between at least two, three or more fluid lines depending on the position. For this purpose, the rotary valve can have a fluid passage opening which, depending on the position of the rotaryslide valve can establish a fluid connection between at least two or at least three fluid lines. Furthermore, the rotary slide valve can have blocking sections with which it can close fluid lines from other fluid lines. The rotary slide valve is preferably cylindrical. The fluid passage opening can be designed as a recess in the cylinder. Preferably, the outer diameter of the rotary slide valve is smaller than the inner diameter of the housing. This provides a movement play between the rotary slide valve and the housing. Preferably, the seal(s) is / are arranged in this movement play. In particular, the seal is designed to be larger in the axial direction (the direction in which the fluid passage opening of the seal is flowed through in an open position) than the movement play. As a result, the seal is compressed in the assembled state between the rotary slide valve and the housing, whereby a contact forceThe previously described outer sealing surface of a seal preferably completely surrounds the respective fluid passage opening of the housing. The previously described inner sealing surface preferably forms a circumferential sealing contact with the rotary valve when the fluid line is in the blocked state. As previously described, the inner sealing surface and the outer sealing surface are preferably formed by the inner leg of the seal, which surrounds the fluid passage opening of the seal. Furthermore, the communication channel is preferably connected to the pressure chamber via the outer leg. Preferably, the outer leg extends from the inner sealing surface to the housing. Preferably, the outer leg forms a sealing surface with the housing that is interrupted by the communication channels but otherwise circumferential. The at least one communication channel is preferably delimited on the one hand by the outer leg and on the other hand by the housing. As previouslyAs described, a seal foot is connected to the end of the outer leg facing the housing, which foot extends in the direction opposite the fluid passage opening (in particular, extends radially outwards with respect to the fluid passage opening). Preferably, the communication channel extends through the foot and has a communication opening opposite the intermediate space between the housing and the rotary valve. This preferably allows fluid to flow from the intermediate space between the rotary valve and the housing via the communication channel into the pressure chamber. Preferably, the directional control valve is designed such that the intermediate space is always flooded during operation. This ensures that the pressure chamber can be flooded with fluid in every operating state. If the rotary valve closes a fluid passage opening in the housing with its blocking section, the pressure in the space adjoining the fluid passage opening can therebyFluid line, for example, when no more fluid is flowing through the fluid line or no more fluid is present. As a result, less pressure acts on the seal via the inner leg of the seal facing the fluid line than via the flooded pressure chamber. This inflates the pressure chamber, whereby the seal is pressed more strongly against the rotary valve and the housing, which in turn increases the contact force and thus the tightness. This provides a self-reinforcing seal. The inventors have found that the self-reinforcing function of the seal works particularly well when the directional control valve, in particular the flooded area between the housing and the rotary valve, is free of air pockets. This can prevent cavitation in particular and ensure reliable heat transport through the fluid. Preferably, a system comprising a directional control valve and an expansion tank is provided for this purpose, so that in the valveRemaining air can be collected in the expansion tank or removed from the directional control valve by applying negative pressure. The inner leg and the outer leg can be of approximately the same length. In other words, the inner leg and the outer leg can protrude approximately the same distance in the fluid passage direction. In an alternative embodiment, the inner leg can be longer than the outer leg. In this embodiment, a preferably annular or oval groove can be formed in the housing, in particular adapted to the shape of the inner leg, in which groove the inner leg can be precisely received in the assembled state of the seal 1. The inner leg can be received in the groove, in particular via a "tongue and groove" principle. In this embodiment, the seal can provide improved tightness in both effective directions of the pressure. A further aspect of the invention relates to a directional control valve, which, in particular, like the previouslyThe directional control valve described can be designed to regulate the flow of a fluid, such as a coolant. The directional control valve comprises a housing with a fluid passage opening, a fluid line adjoining the fluid passage opening, a rotary slide valve arranged in the housing, and a seal in sealing contact with the housing and the rotary slide valve and surrounding the fluid passage opening. The seal can be designed according to the previously described aspect of the invention, in particular with a pressure chamber and communication channel. According to this aspect of the invention, a support structure is provided in the connection area between the fluid passage opening of the housing and the fluid line, which support structure counteracts the seal from slipping into the fluid passage opening. The support structure can surround the fluid passage opening of the housing in a collar-like manner. In particular, the support structure can have an annular shape, in particular a hollow cylindrical shape, which preferablyhas the same diameter as the fluid passage opening. Preferably, the support structure is formed integrally with the housing. Preferably, the housing has an essentially cylindrical jacket-shaped inner surface which is interrupted by the fluid passage opening. Starting from the cylindrical jacket-shaped inner surface, the support structure preferably projects into the housing. Preferably, the support structure is adapted to the shape of the fluid passage opening in the housing. In particular, the shape of the support structure corresponds to the shape of the outer contour of the fluid passage opening. For example, in the case of a circular fluid passage opening, the support structure is preferably annular. In the case of an oval fluid passage opening, the support structure is preferably oval. Preferably, the seal bears against the support structure. In particular, the side of the seal facing the fluid passage opening bears against the support structure.Preferably, the seal is adapted to the shape of the support structure in the area in which it is in contact with the support structure. Preferably, the seal completely surrounds the support structure. Particularly preferably, the previously described inner leg of the seal rests against the support structure. In particular, the inner leg and the outer leg diverge in the direction of the housing, in particular in the radial direction, as described above, wherein a region extending from the spread end of the outer leg in the radial direction toward the rotary valve is in contact with the support structure. Particularly preferably, the inner leg rests against the support structure over at least 10%, 20%, or 30% of its extent, in particular starting from the housing in the radial direction toward the rotary valve, between the previously described inner sealing surface and the outer sealing surface. Particularly preferred are the support structure and seal according to the tongue-and-groove principle.coordinated with one another in order to prevent the seal from slipping into the fluid passage opening. Preferably, the seal has, starting from the inner leg, a projection, in particular a circumferential projection, which preferably rests on the support structure. Particularly preferably, the projection and the section adjacent to the support structure form an L-shape in cross-section. Particularly preferably, the projection has an inner contour facing the fluid passage opening, which preferably corresponds in shape and / or dimension to the fluid passage opening of the housing and the support structure. Preferably, in addition to the previously described support structure, which can also be described as an inner support structure, the directional control valve has an outer support structure, on which an end of the seal facing away from the fluid passage opening, in particular one of the previously described outer legs and / or the previouslyThe outer support structure can have a web extending inwards from the cylindrical inner surface of the housing. In particular, the web can extend radially inwards into the housing. Particularly preferably, the web can be T-shaped. This allows a recess to be formed, in particular between the roof of the T and the cylindrical inner surface of the housing, into which recess the outer leg, preferably the previously described foot of the seal, can engage. The inventors have recognized that, in particular, the combination of the inner and outer support structure can ensure that expansion of the seal, as a result of flooding the pressure chamber with fluid, is limited or prevented in the radial direction (or towards or away from the fluid passage opening). As a result, the expansion of the pressure chamber can be limited, in particular in the form of aExpansion in the flow direction, so that the expansion is used to increase the contact pressure on the rotary valve and the housing and thus strengthen the sealing contact. Preferably, the outer support structure is formed by a recess in the housing, in particular a recess, such as an undercut in the housing. Preferably, the recess is designed to accommodate the previously described foot, in particular such that the foot projects into the recess. In this case, the recess is preferably larger than the foot, so that fluid can flow around the foot along a space between the foot and the recess, in particular along the contour of the recess from a side of the foot facing the rotary valve to a side of the foot facing the housing, through the at least one communication channel. Preferably, the directional control valve is designed to form the housing, in particular a space between theHousing and the directional control valve. This can be achieved, for example, by the rotary valve having at least one fluid passage opening through which the fluid can flow into and out of the rotary valve, wherein the fluid passage opening of the rotary valve is preferably larger than the fluid passage opening of the housing and / or the seal. This ensures that even with perfect centering of the fluid passage opening of the rotary valve on that of the housing and the seal, a bypass channel always remains, through which, in addition to a primary fluid flow (between at least two fluid lines), a secondary fluid flow (into the space between the housing and the rotary valve) is admitted. This secondary fluid flow floods the space and thus, via the space, the pressure chambers, thereby providing the self-reinforcing seal. In embodiments in which the fluid passage openings of the housingare formed in the cylinder jacket of the housing, the fluid passage opening of the rotary valve can be dimensioned so large in the circumferential direction that two fluid passage openings of the housing that are adjacent to one another in the circumferential direction can be connected to one another. For example, in embodiments in which the fluid passage openings of the housing are spaced apart from one another by 30° in the circumferential direction, the fluid passage opening in the rotary valve can extend over at least 90°, so that 30° can be used to bridge the distance between the two openings and 30° for each opening in order to provide an overlapping flow cross-section with the respective lines. For this purpose, the rotary valve can, for example, have a cylindrical basic shape in which the fluid passage opening is designed as a disc-shaped recess. The fluid passage opening is preferably designed such that itcan be brought into fluid communication with the fluid passages of the housing via the cylinder jacket. In end face designs, the rotary valve can be designed as a circular disc, in particular, which has fluid passages extending axially. Here, too, the fluid passages in the rotary valve are preferably larger than the fluid passages in the housing in order to flood the space between the housing and the rotary valve. The invention further relates to a motor vehicle fluid flow control system, in particular a motor vehicle thermal management fluid control system, such as a motor vehicle cooling circuit, which has a directional control valve according to one or both of the previously described aspects of the invention. Further properties, features, and advantages of the invention will become clear below by describing preferred embodiments of the invention with reference to the accompanying exemplary drawings, in which: Figure 1a:a perspective front view of an embodiment of a seal according to the invention; Figure 1b: a perspective rear view of the seal from Figure 1a; Figure 1c: a perspective side view of the seal from Figure 1a; Figure 2a: a view of an embodiment of a four-way valve according to the invention; Figure 2b: a side sectional view of the directional control valve according to Figure 2a; Figure 2c: a sectional view from above of the four-way valve from Figure 2a; Figure 2d: an enlarged view of section a from Figure 2c; Figure 2e: the view according to Figure 2c with a changed position of the rotary slide valve; Figure 2f: the view according to Figure 2e with a further changed position of the directional control valve; Figure 3a: a perspective view of a further embodiment of the invention in the form of a three-way valve; Figure 3b: a top view of the three-way valve according to Figure 3a; Figure 4a: a perspective view of a rotary valve for aAnother embodiment of a four-way valve according to the invention; Figure 4b: a top view of a four-way valve with the rotary slide from Figure 4a; Figure 5a: a perspective view of another embodiment of the invention in the form of a six-way valve; Figure 5b: a sectional view from above of the six-way valve according to Figure 5a; Figure 5c: a perspective view from above of the six-way valve according to Figure 5a with a cover; Figure 6a: a perspective front view of another embodiment of the invention in the form of an oval seal; Figure 6b: a perspective rear view of the seal according to Figure 6a; Figure 7a: a front view of another embodiment of the invention in the form of an end face seal; Figure 7b: a rear view of the seal according to Figure 7a; Figure 8a: a perspective side view of a four-way valve with an inventive seal according to Figure 7a; Figure 8b: a sectional view of theFour-way valve according to Figure 8a; Figure 8c: a further sectional view of the four-way valve according to Figure 8a; Figure 8d: an enlarged view of a region from Figure 8c; Figure 9a: a side view of a further exemplary embodiment of a seal according to the invention; and Figure 9b: a side sectional view of the seal according to Figure 9a. Figures 1a to 1c show different views of an embodiment of a seal 1 according to the invention with a circular fluid passage opening 3. Figures 6a and 6b show different views of an alternative embodiment of a seal 1' according to the invention with an oval fluid passage opening 3'; the seals 1 and 1' are curved in order to be able to form a sealing contact between cylindrical jacket surfaces 5, 7 of cylindrical rotary slide valves 9 and housings 11. Such embodiments of seal 1, 1' can be referred to as a jacket design. Figures 7a and 7b showDifferent views of an alternative embodiment of a seal 1'' with three disk-section-shaped fluid passage openings 3''. The seal 1'' is designed to form a sealing contact between disk-shaped end faces 5', 7' of disk-shaped rotary valves 9'' and cylindrical housings 11''. Such embodiments of seal 1'' can be referred to as end face designs. Each of the illustrated seals 1, 1', 1'' has at least one pressure chamber 13, 13', 13'', which surrounds the respective fluid passage opening 3, 3', 3''. The seal 1'' accordingly has three pressure chambers 13'', each of which surrounds one of the three fluid passage openings 3''. Furthermore, each of the seals 1, 1', 1'' has a plurality of communication channels 15, 15', 15'' for flooding the respective pressure chambers 13, 13', 13'' with the fluid. The respective fluid passage opening 3, 3', 3'' defines aFlow direction D, in which fluid can flow through the seal in the assembled state with the rotary valve in the open position. The flow direction D is the direction that runs parallel to a normal of the respective fluid passage opening. In the case of embodiments 1, 1' with a curved fluid passage opening, the fluid passage opening 3, 3' is to be assumed to be a non-curved surface to determine the normal, i.e. as a circle in Figures 1a to 1c and as an oval in Figures 6a and 6b. To determine the geometry of the seal, an axis located in the geometric center of the respective fluid passage opening 3, 3', 3'' and extending parallel to the flow direction is referred to below as the central axis A. Wherever circumferential direction U or radial direction R is mentioned below, these directions refer to the center axis A. The respective communication channel 15, 15', 15'' of the seals 1, 1', 1'' encircles theFluid passage opening 3, 3', 3'' in the circumferential direction U completely. In the illustrated embodiments, the geometry of the pressure chamber 13, 13', 13'' is adapted to the geometry of the respective fluid passage opening 3, 3', 3''. Accordingly, the seal 1 has an annular pressure chamber 13. The seal 1' has an oval pressure chamber 13'. The respective pressure chambers 13'' of the seal 1'' have the shape of the disc-shaped outer contour of the fluid passage openings 3''. In all illustrated embodiments, the pressure chambers 13, 13' and 13'' are designed as a groove introduced into the sealing material of the respective seal 1, 1', 1''. In the illustrated embodiments, the grooves taper. In particular, the grooves taper in the axial direction A. In particular, the grooves taper in the axial direction A towards the side of the respective seal 1, 1', 1'' facing the rotary valves. In the preferred embodiments shownIn some embodiments, the grooves are V-shaped, in particular V-shaped in the direction of the side of the respective seal 1, 1', 1'' facing the rotary valves. Furthermore, the pressure chambers 13, 13', 13'' are here introduced into the respective seal 1, 1', 1'' in such a way that the pressure chambers are open on one side, in particular on the side of the directional control valve facing the housing 11. In particular, the pressure chambers 13, 13', 13'' are each delimited by an inner leg 17, 17', 17'' facing the respective fluid passage opening 3, 3', 3'' and an outer leg 19, 19', 19'' facing away from the fluid passage opening 3, 3', 3''. As shown, the inner leg 17, 17', 17" and the outer leg 19, 19', 19" preferably run towards each other, in particular in the axial direction A, in particular in the direction of the side of the seal 1, 1', 1" facing the rotary valve, in particular in a V-shape. At the housingOn the side of the seal 1, 1', 1' facing the 11, 11' side, the inner leg 17, 17', 17' and the outer leg 19, 19', 19' are spaced apart from one another in the radial direction R. In the preferred embodiments shown, the inner leg 17, 17', 17' and the outer leg 19, 19', 19' are spaced apart from one another on the side facing the housing along the entire length of the pressure chambers 13, 13', 13'. In particular, the inner leg 17, 17', 17" and the outer leg 19, 19', 19" completely encircle the fluid passage opening 3, 3', 3" and the pressure chamber 13, 13', 13" in the circumferential direction U. In addition, the outer leg 19, 19', 19" completely encircles the pressure chamber 13, 13', 13" in the circumferential direction U. Due to the distance of the respective inner leg 17, 17', 17" and the outer leg 19, 19', 19" in the radial direction R, a circumferential opening, in particular annular in the case of seal 1, oval in the case of seal 1' and disc-shaped in the case of seal 1"the pressure chamber 13, 13', 13'', which is closed by the housing 11, 11'' of the rotary slide valve when the respective seal 1, 1', 1'' is in the assembled state. As a result, the respective pressure chamber 13, 13', 13'' is completely enclosed by the sealing material and the housing, apart from the respective communication channels in the assembled state. Figure 2d shows a cross-sectional view of area A from Figure 2c of the seal 1 in sealing contact with the rotary slide valve 9 and the housing 11 of the directional control valve 21 according to Figures 2a to 2f. As can be seen therein, the inner leg 17 has an outer sealing surface 23 facing the housing 11 and an inner sealing surface 25 facing the rotary slide valve to form the sealing contact. The outer sealing surface 23 and the inner sealing surface 25 surround the fluid passage opening 3 in the circumferential direction U. In the seal 1, the inner sealing surface 25 and the outer sealing surface 23 surround the fluid passage opening 3 in a ring shape. In the seal 1'Corresponding inner sealing surfaces 25 and outer sealing surfaces 23 surround the fluid passage opening 3' along an oval contour. In the case of the seal 1'', corresponding inner sealing surfaces 25 and outer sealing surfaces 23 surround the respective fluid passage opening 3'' in the shape of disc sections. As can be seen in particular from the overlap region 27 in Figure 2d, the seal 1 has an excess in the axial direction A compared to the distance between the rotary valve 9 and the housing 11, in particular between the outer surface 5 of the rotary valve 9 and the outer surface 7 of the housing 11. As a result, the seal 1 is compressed in the assembled state, in particular in the axial direction A. This creates a contact pressure that establishes the sealing contact, in particular in the region of the sealing surfaces 23 and 25. To reinforce this sealing contact, a seal 1, 1', 1'' according to the invention, as described above, has communication channels 15, via which the pressure chamber 13, 13', 13'' is supplied with fluidcan be flooded. This allows fluid to flow from an intermediate space 31 between the rotary valve 9 and the housing 11 into the pressure chamber 13 via the communication channels 15. An exemplary flow path of the fluid from the intermediate space 31 into the pressure chamber 13 (secondary flow) is shown schematically by the dashed line 33. The fluid passage opening 3, which is partially visible in Figure 2d, is in a closed position in the operating state shown. This is characterized in that a blocking section 35 of the rotary valve 9 forms a circumferential sealing contact with the inner sealing surface 25 and the outer sealing surface 23 forms a circumferential sealing contact with the outer surface 7 of the housing 11. The two circumferential sealing contacts prevent fluid flow from the fluid line adjoining the fluid passage opening 3 into the intermediate space 31. By flooding the housing 11, in particular the intermediate space 31, for examplethrough one of the other fluid lines of the directional control valve, it can be ensured that a higher fluid pressure can be present in the pressure chamber 13 than in the side of the inner leg 17 facing the fluid passage opening 3. This creates an overpressure in the pressure chamber, whereby the pressure chamber can be inflated. This can increase the contact force, particularly with regard to the circumferential sealing surfaces 23 and 25, which increases the sealing contact and the tightness of the seal or directional control valve. This provides a self-reinforcing, fluid-force-assisted seal. As can be seen from Figure 2d, the communication channel 15 is connected to the pressure chamber 13 via the outer leg 19. In the assembled state, the communication channel 15 is completely enclosed by the sealing material of the seal 1 and the cylinder jacket surface 7 of the housing 11, apart from a communication opening with the pressure chamber 13 and with the intermediate space 31.In the present case, the communication channel 15 is formed by a groove, in particular a V-shaped groove, in the sealing material of the seal 1, which, in the assembled state, is closed off to form a channel by the housing 11, in particular by the cylindrical surface 7 of the housing 11. In alternative embodiments, the at least one communication channel can also be formed, for example, as a bore through the outer leg 19. The seals 1, 1', 1'' have a foot 37, 37', 37'' to be applied to the housing 11. The foot 37, 37', 37'' is arranged in the radial direction R preferably on the outside of the pressure chamber 13, preferably on the outer leg 19, 19', 19''. In particular, the foot 37, 37', 37'' can be connected in the radial direction R to the outside of the end of the seal 1, 1', 1'' facing the housing 11 and can extend from there preferably in the radial direction R. The foot 37, 37', 37'' can completely encircle the fluid passage opening 3, 3' in the circumferential direction U.In particular, the foot 37, 37' can completely encircle the pressure chamber 13, 13' and the outer leg 19, 19' in the circumferential direction U. The foot 37, 37' can be curved in order to be able to rest against a cylindrical surface 7 of the housing 11. The foot can have a square outer contour with rounded corners. In particular, the foot can have a rectangular outer contour with rounded edges, as in the case of seals 1 and 1'. In particular, the foot can have a square outer contour with rounded edges, as in the case of seal 1, or a rectangular outer contour with rounded edges with different edge lengths, as in the case of seal 1'. Alternatively, the foot 37'', as shown in the seal 1'', can have an annular shape, which partially surrounds the individual fluid passage openings 3'' and completely surrounds the arrangement of the multiple fluid passage openings 3''. Furthermore, the foot 37'' canEmbodiments with a plurality of fluid passage openings 3'' have, in addition to the outer contour 39, webs 41 extending to the center of the seal 1'', which webs in particular separate the individual fluid passage openings 3'' from one another in the circumferential direction (relative to the center M). Communication channels 43 can be provided in the webs 41, which connect the pressure chambers 13'' to one another. This can ensure fluid exchange between the pressure chambers 13'' of the different fluid passage openings 3''. Preferably, the communication channels 15, 15', 15'' are introduced into the foot 37, 37', 37'', in particular in the form of grooves in the respective foot 37, 37', 37''. The communication channels are preferably designed as V-shaped grooves. The communication channels 15, 15', 15'' can extend in the assembled state between the base 37, 37', 37'' and the housing 11, in particular from the housing and the respectiveFoot. Preferably, a seal 1 each has a plurality of communication channels 15, 15', 15'', which are arranged offset from one another in the circumferential direction U around the fluid passage opening 3, 3', 3'', in particular around the pressure chamber 13, 13', 13'' and / or the outer leg 19, 19', 19''. Preferably, the communication channels 15, 15', 15'' extend in the radial direction from the outside to the inside through the respective foot 37, 37', 37'' into the respective pressure chamber 13, 13', 13''. Preferably, the respective foot 37, 37', 37'' has an active surface 45 facing the rotary slide 9, via which the fluid pressure in the flooded housing presses the foot against the housing in order to provide a contact pressure between the foot 37, 37', 37'' and the housing 11, counteracting a relative movement between the seal 1, 1', 1'' and the housing 11. Furthermore, the foot 37, 37', 37'' preferably has aContact surface 47. Preferably, the contact surface 47, 47', 47'' is interrupted by the previously described communication channels 15, 15', 15'', particularly when designed as a groove in the respective foot 37, 37', 37''. Apart from the interruption by the communication channels 15, 15', 15'', the contact surface 47, 47', 47'' preferably corresponds essentially to the active surface 45, 45', 45''. Essentially is understood to mean a deviation of, in particular, a maximum of 20%, 15% or 10%. Taking into account the interruption of the contact surface 47, 47', 47'' by the communication channels 15, 15', 15'', the contact surface is preferably at least 40%, 50% or 60% and / or at most 90%, 80% or 70% of the effective surface 45, 45', 45''. In the seals 1, 1', 1'', a plurality of support ribs 49, 49', 49'' are provided in the respective pressure chambers 13, 13', 13''. The support ribs 49, 49', 49'' subdivide the respective pressure chambers13, 13', 13'' into chamber sections 51, 51', 51'' between which fluid exchange is preferably possible. For this purpose, the support ribs 49, 49', 49'' preferably do not extend completely in the axial direction to the ends of the previously described legs facing the housing, in order to form a flow cross-section between the respective support ribs 49 and the housing 11, in particular the cylindrical surface 7 of the housing 11. The support ribs 49, 49', 49'' preferably extend in the radial direction between the previously described inner leg 17, 17', 17'' and outer leg 19, 19', 19''. In particular, the support ribs 49, 49', 49'' are preferably distributed in the circumferential direction U, in particular at equidistant intervals, around the fluid passage opening 3, 3', 3'' and arranged spaced apart from one another in the respective pressure chamber 13, 13', 13''. Figures 2a - 2f show different views of an embodiment of a four-way valve 21 for adjusting theFlow of a fluid, such as a coolant. The four-way valve 21 comprises a housing 11 with four fluid passages 53, 55. The housing is cylindrical. Three fluid passages 53 are provided in the casing of the housing. The three fluid passages 53 provided in the casing are offset from one another in the circumferential direction U (relative to the axis of symmetry of the cylindrical housing), in particular offset from one another by 120°. The fluid passages 53 are provided as circular recesses in the casing of the housing 11. The fourth fluid passage 55 of the housing 11 is provided on the end face of the housing 11. The fluid passage 55 is also circular. The four-way valve 21 further comprises a fluid line 57, 59 connected to each of the fluid passage openings 53, 55. The fluid lines 57, 59 are each formed in the shape of a hollow cylinder.The fluid lines 57 connect to the fluid passage openings 53. The fluid line 59 connects to the fluid passage opening 55. The fluid lines 57 are arranged offset from one another in the circumferential direction (relative to the axis of symmetry of the cylindrical housing 11), in particular at equidistant distances from one another. In particular, the fluid lines are arranged in a star shape relative to one another. The fluid line 59 is arranged offset from the fluid lines 57 in the axial direction (parallel to the axis of symmetry of the cylindrical housing 11). The four-way valve 21 further has a rotary slide valve 9 arranged in the housing 11. The rotary slide valve 9 is cylindrical. The outer diameter of the rotary slide valve 9 is smaller than the inner diameter of the housing 11, so that there is play between the rotary slide valve 9 and the housing 11. Between the rotary valve 9 and the fluid lines 57 there is a seal 1, as shown in Figures 1a –1c, which are in sealing contact with the rotary valve 9 and the housing 11. The seals 1 each run around one of the three fluid passages 53. The fluid passages 53 of the seals 1 are each aligned with the fluid passages 53 in the housing 11. The rotary valve 9 is rotatably arranged in the housing 11. The rotary valve 9 has a drive pin 61, via which the rotary valve can be adjusted via a drive, in particular via a motor, such as an electric motor. The rotary valve 9 has, on its side facing the fluid passage 55, a fluid passage 63 which is aligned with the fluid passage 55 of the housing. The fluid passage 63 is arranged coaxially to the rotation axis 65 of the rotary valve 9. In particular, the fluid passage opening 63 is circular and arranged coaxially to the fluid passage opening 55 in the housing. With the rotary valve 9 shown, theFluid passage opening 63 is always activated, in particular in such a way that, regardless of the position of the rotary valve, fluid exchange between the rotary valve 9 and the fluid line 59 is always permitted. The rotary valve 9 further has a second fluid passage opening 67 introduced into the casing of the rotary valve 9. The fluid passage opening 67 is connected to the fluid passage opening 63, so that fluid entering the rotary valve via the fluid passage opening 63 can leave the rotary valve via the fluid passage opening 67. In other words, the rotary valve 9 is designed in such a way that fluid can enter the rotary valve via its end face and exit via openings in the casing, and vice versa. As can be seen in particular from Figures 2c, 2e and 2f, the fluid passage opening 67 is designed larger than the fluid passage openings 53 of the housing 11 and the fluid lines 57. As a result, the fluid line 59 can be used fora primary flow can be connected to one of the fluid lines 57 and, at the same time, a secondary flow from one of the fluid lines 57 or 59 can be admitted via the intermediate space 31 between the rotary slide valve 9 and the housing 11 (cf. Figure 2c and Figure 2f). Furthermore, the fluid passage opening 67 in this exemplary embodiment is designed so large that two of the fluid lines 57 can be connected to the fluid line 59 simultaneously. This allows, for example, fluid flows from two lines to be guided into one line, or a fluid flow from one line to be divided into two lines. For this purpose, the fluid passage opening 67 is designed to be larger in the circumferential direction (relative to the axis of symmetry of the cylindrical rotary slide valve) than the distance between two fluid lines 57 in the circumferential direction. The directional control valve 21 is designed accordingly to close the housing 11, in particular the intermediate space 31 between the housing 11 and theRotary valve 9. Figures 3a and 3b show an embodiment of a three-way valve 21 iv . The three-way valve 21 iv is largely similar to the four-way valve 21, so the following will focus on its differences. The three-way valve 21 ivhas three fluid lines 57 that connect to fluid passage openings 53 provided in the cylindrical housing 11. The fluid lines 57 are arranged offset from one another by 90° in the circumferential direction (relative to the axis of symmetry of the cylindrical housing 11). At two fluid passage openings 53, in particular at fluid passage openings 53 that are aligned with one another, a seal 1 according to the invention is arranged between the housing 11 and the rotary valve 9. The third fluid passage opening 59 is designed without a seal. As a result, regardless of the position of the rotary valve 9, fluid can flow via the fluid line 59 into the space between the rotary valve 9 and the housing 11, thus allowing a secondary fluid flow to flood the pressure chambers 13, 13', 13''.A fluid passage opening is provided in the rotary valve 9, which extends approximately 90° in the circumferential direction relative to the casing of the rotary valve 9. In particular, the fluid passage opening 67 of the rotary valve 11 is formed in the shape of a circular segment in the axial direction (relative to the axis of rotation of the rotary valve 9). Figures 4a and 4b show an alternative embodiment of a four-way valve. v, with four fluid passage openings 53 arranged offset from one another in the circumferential direction (relative to the axis of symmetry of the cylindrical housing 11), as well as fluid lines 59 adjoining them. Each fluid line 59 is aligned with a fluid passage opening 53 of the housing. The fluid passage openings 53 are offset from one another by 90° in the circumferential direction. The rotary slide valve 9, in turn, has two fluid passage openings 67, each of which extends circumferentially over 90° of the casing of the rotary slide valve 9. This allows two pairs of fluid lines 59 to be interconnected independently of one another. A seal 1 is arranged at each of the fluid passage openings 53 between the rotary slide valve 9 and the housing 11. Figures 5a-5c show an embodiment of a directional control valve viwith six fluid passages arranged offset from one another in the circumferential direction (relative to the axis of symmetry of the cylindrical housing 11). Figure 5c shows an embodiment of a rotary slide valve 9 with six fluid passages 53 which are arranged offset from one another in the circumferential direction (relative to the axis of symmetry of the cylindrical rotary slide valve 9), in particular are arranged at equidistant intervals from one another, in particular are incorporated in the casing of the cylindrical rotary slide valve 9. A seal 1 according to Figures 1a - 1c is attached to each of the six fluid passages 53. Figures 8a - 8d show different views, sectional views and enlarged views of an embodiment of a four-way valve in which four fluid lines 57'', 59'' connect to the housing 11. Three of the fluid lines 57 are connected to the cylindrical housing 11 via the front side thereof.For this purpose, three fluid passage openings 55' are provided in the front side, which are arranged offset from one another in the circumferential direction (relative to the axis of symmetry of the cylindrical housing 11), in particular offset by 120° from one another. A disk-shaped rotary slide valve 9'' is provided to close and open the fluid passage openings 55''. Fluid passage openings 67'' are provided in the disk-shaped rotary slide valve 9'', which can be arranged in alignment with the fluid passage openings 55'' by adjusting the rotary slide valve 9'' to expose the fluid passage openings 55''. The rotary slide valve 9'' has blocking sections 35'' to block the fluid passage openings 55''. The housing further comprises a fluid passage opening 53'' formed in the casing of the housing 11'', to which a fluid line 59'' is connected.A cylindrical intermediate space is provided between the disc-shaped rotary valve 9'' and the cylindrical housing 11'', which can be flooded with the fluid adjusted by the directional control valve. One or more primary fluid streams can be connected between the fluid lines 57'' and 59'' via the intermediate space 31'', and one or more secondary fluid streams can flow via the respective communication channels 15'' into the pressure chambers 13'' of the seal 1'' according to Figures 7a and 7b. The seal 1'' is arranged between the disc-shaped rotary valve 9'' and the end face of the housing 11''. As previously described, according to one aspect of the invention, the housings 11, 11'' have a support structure 75, 75'' in the connection area between the respective fluid passage openings 53, 55'', which counteracts slipping of the respective seal 1, 1'' into the fluid passage opening 53, 55''.The support structure 75, 75'' is preferably designed as a collar surrounding the fluid passage opening 53, 55''. In particular, the support structure 75'' can be designed as a structure, in particular an annular structure, that projects inwards into the housing relative to the surfaces of the housing 11, 11'' with which the seal 1, 1'' is in sealing contact. Furthermore, the directional control valve preferably has, in addition to the previously described support structure, which can also be referred to as the inner support structure 75, 75'', an outer support structure 77, 79, 81. The outer support structure 77 can, as can be seen from Figure 2d, for example, be designed as a recess 77 formed in the housing 11, into which the foot 37, 37', 37'' of the seal 1 projects.This ensures, in particular, that as a result of excess pressure building up in the pressure chamber 13, the resulting expansion does not lead to a spreading of the inner leg 17 and outer leg 19, but rather to an inflation of the pressure chamber 13 in the axial direction A, which reinforces the sealing contact, particularly in the region of the sealing surfaces 23, 25. Figure 8d shows an alternative embodiment of the outer support structure 79, 81. In this, the outer surface 79 of the housing, on the one hand, and a pin 81 of the rotary valve, on the other hand, can function as an outer stop 79, 81. Figures 9a and 9b show a further exemplary embodiment of a seal 1''' according to the invention. The seal 1''' differs from the seal 1 in Figures 1a to 1c in that on the side of the seal 1''' facing the housing, the inner leg 17''' is longer than the outer leg 19'''.An annular groove adapted to the longer inner leg 17''' can be formed in the housing 11 (not shown in Figures 9a and 9b), in which the inner leg 17''' is precisely received when the seal 1''' is in the assembled state. The inner leg 17''' can be received in the groove using a "tongue and groove" principle. In this embodiment, the seal 1''' can provide improved sealing in both directions of pressure. The features disclosed in the above description, the figures and the claims can be important both individually and in any combination for the implementation of the invention in the various embodiments.

[0002] List of reference symbols: 1, 1', 1'', 1''' Seal 3, 3', 3'', 3''' Fluid passage opening 5 Shell surface of the rotary valve 7 Shell surface of the housing 9, 9'' Rotary valve 11, 11'' Housing 13, 13', 13'', 13''' Pressure chamber 15, 15', 15'', 15''' Communication channel 17, 17', 17'', 17''' Inner leg 19, 19', 19'', 19''' Outer leg 21, 21', 21'', 21''' Directional valve 23 Outer sealing surface 25 Inner sealing surface 27 Overlap area 31, 31'' Intermediate space 33 Secondary fluid flow 35, 35', 35'' Blocking section 37, 37', 37'', 37''' Foot 39 Outer contour 41 Web 43 Communication channel 45, 45', 45'' Effective surface 47, 47', 47'' Contact surface 49, 49', 49'', 49''' Support ribs 51, 51', 51'', 51''' Chamber sections 53, 53'' Fluid passage opening 55, 55'' Fluid passage opening 57, 57'' Fluid line 59, 59'' Fluid line 61 Drive pin 63 Fluid passage opening 65 Rotation axis of the rotary valve 67, 67'' Fluid passage opening 75,75'' inner support structure 77 outer support structure 79 casing surface / outer support structure 81 journal / outer support structure D flow direction A central axis U circumferential direction R radial direction,

Claims

1 / 4 Woco Industrietechnik GmbH W31801WO CLAIMS 1. Seal (1, 1', 1'', 1''') for forming a sealing contact with a housing (11, 11'') and a rotary slide valve (9, 9'') of a directional control valve (21) arranged in the housing (11, 11'') for adjusting the flow of a fluid, such as a coolant, characterized in that 5 the seal (1, 1', 1'', 1''') has a pressure chamber (13, 13', 13'', 13''') and at least one communication channel (15, 15', 15'', 15''') for flooding the pressure chamber (13, 13', 13'', 13''') with the fluid.

2. Seal (1, 1', 1'', 1''') according to claim 1, characterized in that the pressure chamber (13, 13', 13', 13''') surrounds a fluid passage opening of the seal (1, 1', 10 1'', 1'''), in particular along the outer contour of the fluid passage opening. 3.Seal (1, 1', 1'', 1''') according to claim 2, characterized in that the pressure chamber (13, 13', 13'', 13''') is delimited by an inner leg (17, 17', 17'', 17''') facing the fluid passage opening and an outer leg (19, 19', 19'', 19''') facing away from the fluid passage opening.

4. Seal (1, 1', 1'', 1''') according to claim 3, characterized in that the at least one communication channel (15, 15', 15'', 15''') is connected to the pressure chamber (13, 13', 13'', 13''') via the outer leg (19, 19', 19'', 19''').

5. Seal (1, 1', 1'', 1''') according to claim 3 or 4, characterized in that the inner leg (17, 17', 17'', 17''') has, for forming the sealing contact, an outer sealing surface (23) facing the housing (11, 11'') and an inner sealing surface (25) facing the rotary valve (9, 9''), wherein the inner sealing surface (25) and / or the outer sealing surface (23) preferably encircle the fluid passage opening.Seal (1, 1', 1'', 1''') according to one of the preceding claims, characterized in that the pressure chamber (13, 13', 13'', 13''') extends from a. 2 / 4 of the side of the seal (1, 1', 1'', 1''') facing the housing (11, 11'') tapers, in particular in a V-shape, to a side of the seal (1, 1', 1'', 1''') facing the rotary slide (9, 9'').

7. Seal (1, 1', 1'', 1''') according to one of the preceding claims, characterized in that, to form the sealing contact, the seal (1, 1', 1'', 1''') has an outer sealing surface (23) facing the housing (11, 11'') and an inner sealing surface (25) facing the rotary slide (9, 9''), which are made of the same material.Seal (1, 1', 1'', 1''') according to one of the preceding claims, characterized in that the seal (1, 1', 1'', 1''') has a foot (37, 37') to be applied to the housing (11, 11'') with an active surface to be turned towards the rotary slide (9, 9''), via which foot the fluid pressure presses the foot (37, 37') against the housing (11, 11'') when the housing (11, 11'') is flooded with the fluid, in particular in order to provide a contact pressure between the foot (37, 37') and the housing (11, 11'') counteracting a relative movement between the seal (1, 1', 1'', 1''') and the housing (11, 11'').

9. Seal (1, 1', 1'', 1''') according to claim 8, characterized in that the at least one communication channel (15, 15', 15'', 15''') extends in the assembled state between the foot (37, 37') and the housing (11, 11'') and / or that the foot (37, 37') adjoins the outer leg (19, 19', 19'', 19''') according to one of claims 3 to 5. 10.Seal (1, 1', 1'', 1''') according to one of the preceding claims, characterized in that the seal (1, 1', 1'', 1''') has at least one support rib (49, 49', 49'', 49''') 25 arranged in the pressure chamber (13, 13', 13'', 13'''), in particular in order to stabilize the pressure chamber (13, 13', 13'', 13''') against pressure acting on the pressure chamber (13, 13', 13'', 13''') from outside the pressure chamber (13, 13', 13'', 13'''), preferably wherein the at least one support rib (49, 49', 49'', 49''') is located between the inner leg (17, 17', 17'', 17''') and the outer leg (19, 19', 19'', 19''') according to one of claims 3 to 5 30.

11. Seal (1, 1', 1'', 1''') according to one of the preceding claims, characterized in that the at least one communication channel (15, 15', 15'', 15''') is designed to fluidly connect the pressure chamber (13, 13', 13'', 13''') with a. 3 / 4 gap (31, 31'') between the housing (11, 11'') and the rotary slide (9, 9'').

12. Directional control valve (21) for adjusting the flow of a fluid, such as a coolant, comprising - a housing (11, 11'') with a fluid passage opening, - a fluid line connected to the fluid passage opening, - a rotary slide (9, 9'') arranged in the housing (11, 11''), and - a seal (1, 1', 1'', 1''') according to one of the preceding claims, which seal is in sealing contact with the housing (11, 11'') and the rotary slide (9, 9'') and surrounds the fluid passage opening. 13.Directional control valve (21), in particular according to claim 12, for adjusting the flow of a fluid, such as a coolant, comprising - a housing (11, 11") with a fluid passage opening, - a fluid line adjoining the fluid passage opening, - a rotary slide valve (9, 9") arranged in the housing (11, 11"), and - a seal (1, 1', 1'', 1''') in sealing contact with the housing (11, 11") and the rotary slide valve (9, 9") and encircling the fluid passage opening, characterized by - a support structure (75, 75") arranged in the connection region between the fluid passage opening and the fluid line, which support structure counteracts the seal (1, 1', 1'', 1''') from slipping into the fluid passage opening. 14.Directional control valve (21) according to claim 13, characterized in that the support structure (75, 75'') surrounds the fluid passage opening in a collar-like manner, in particular wherein the seal (1, 1', 1'', 1'''), in particular the inner leg (17, 17', 17'', 17''') according to one of claims 3 to 5, bears against the support structure (75, 75'').

15. Directional control valve (21) according to claim 12 or 14, characterized by an outer support structure (77, 79, 81) on which an end of the seal (1, 1', 1'', 1''') facing away from the fluid passage opening, in particular an outer leg (19, 19', 19'', 19''') according to one of claims 3 to 5 or a foot (37, 37') according to one of claims 8 to 9, is supported.

16. Directional control valve (21) according to one of claims 12 to 15, characterized in that the directional control valve (21) is designed to support the housing (11, 11''), in particular a. 4 / 4 intermediate space (31, 31'') between the housing (11, 11'') and the directional control valve (21) to be flooded.

17. Directional control valve (21) according to one of claims 12 to 16, characterized in that the rotary slide valve (9, 9'') has at least one fluid passage opening through which the fluid can flow into and out of the rotary slide valve (9, 9''), wherein the fluid passage opening of the rotary slide valve (9, 9'') is larger than the fluid passage opening of the housing (11, 11'') and / or the seal (1, 1', 1'', 1''').

18. Motor vehicle fluid flow control system, in particular motor vehicle thermal management fluid control system, such as motor vehicle cooling circuit, comprising a directional control valve (21) designed according to one of claims 10 12 to 17 and optionally a line system connected to the directional control valve (21).

Images