DE102022127145A1 - Fluid pressure assisted seal for a directional control valve and directional control valve - Google Patents

Abstract

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, wherein the seal has a pressure chamber and at least one communication channel for flooding the pressure chamber with the fluid, wherein the pressure chamber runs around a fluid passage opening of the seal, in particular runs along the outer contour of the fluid passage opening.

Description

The invention relates to a seal for forming a sealing contact with a housing and a rotary slide valve arranged in the housing of a directional control valve for adjusting the flow of a fluid, such as a coolant. The invention also relates to a directional control valve with a seal. The invention also 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.

Multi-way valves of this type are used, for example, in motor vehicles for thermal management and are used in particular to conduct coolants such as water or oils in order to cool, heat or generally control the temperature of components, particularly in the engine compartment. Multi-way valves of this type are usually equipped with a rotary slide 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 slide valve. For this purpose, the rotary slide valve is arranged in a housing so that it can rotate. In order to allow rotation in the housing, play is provided between the rotary slide valve and the housing, which creates a gap between the rotary slide valve and the housing. In order to prevent leakage via this gap between separate fluid channels, seals are arranged between the rotary slide valve and the housing, which seal the fluid lines from the gap.

To ensure the most reliable seal possible, a high contact pressure is required that is matched to the fluid pressure. A high contact force can be achieved, for example, by using springs. However, this increases the complexity and thus the costs and susceptibility to failure as well as the installation space of the directional control valve.

Alternatively, a high contact pressure can be achieved by using seals with a particularly high oversize compared to the play between the rotary valve and the housing. However, this leads to a high level of force being required when assembling and operating the rotary valve.

Out of WO 2022/025513 It is known to solve this problem by means of a sealing arrangement with a hard and sliding contact surface facing the rotary valve and a soft contact surface facing the housing. This allows the required assembly force to be reduced 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 member during operation can be reduced, which reduces the costs and installation space required for the actuator.

The disadvantage of this solution, however, is that the different mechanical requirements for the two sealing surfaces require either complex two-part structures or technically demanding manufacturing processes, such as the one in WO 2022/025513 mentioned “two-shot extrusion process”.

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 valve and the housing can be increased without increasing the complexity of the rotary valve and/or the effort required for assembly and operation.

This object is solved 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 valve of a directional control valve arranged in the housing for adjusting the flow of a fluid, 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 for forming such a sealing contact with the housing and the rotary slide valve is preferably designed in such a way that a fluid line adjoining the housing can be sealed by means of the seal with respect to an intermediate space between the rotary slide 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 slide 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 foot of the seal. The sealing body preferably has elastic, in particular elastomeric, material and is in particular completely formed from it.

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 also have an oval shape, for example. 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 previously described diameter, particularly preferably the same width as the diameter. Another 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 several passage openings, for example at least two, three, four, five or six passage openings. In this embodiment, the seal can, for example, be circular, 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, in particular a V-shaped groove, made in the sealing material of the seal. The pressure chamber, in particular the groove, preferably completely surrounds the fluid passage opening. The pressure chamber can be completely or partially enclosed by the sealing material of the seal, apart from the communication channel. The pressure chamber is preferably introduced into the seal in such a way that in the assembled state, in particular apart from the at least one communication channel, it is completely enclosed by the sealing material and the housing. 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 pressure between the seal and the rotary valve and the housing. The seal is designed in particular 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 designed in such a way that the pressure chamber is inflated, in particular in a balloon-like manner, by the 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 increasing 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 self-reinforcement of the contact pressure. This makes it possible, on the one hand, to reduce the excess between the seal and the play of movement between the rotary valve and the housing, which requires less force to assemble the seal. During operation, the fluid pressure is then used to increase the contact pressure in such a way that leakage is reduced, and in particular avoided. It has proven particularly advantageous that the contact pressure is also automatically increased when the fluid pressure is higher. This means that the seal according to the invention can be used for different pressure conditions and always provides the required contact pressure. The fluid pressure itself therefore ensures a contact pressure that is appropriate to the fluid pressure. This makes it possible, in particular, to avoid unnecessarily high contact forces at low fluid pressures or insufficient contact forces at high fluid pressures. This also means that the drive power of the motors for the rotary valve can be individually adapted to the pressure conditions.

The inventors have also found that the fluid pressure-assisted contact force means that contact pressure devices such as springs are not required and that leakage can still be reliably avoided. The seal can therefore preferably be used in directional control valves without separate contact pressure devices such as springs. The directional control valves described below are therefore particularly preferably directional control valves that are free of contact pressure devices such as springs 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. Forming 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 with constant fluid pressure, which in turn increases the contact force. Inflation is preferably carried out by an overpressure in the pressure chamber. This can be achieved, for example, by flooding the valve housing, which in turn fills the pressure chamber with excess pressure. the communication channels are supplied with fluid, whereas a line to be closed has a lower pressure, so that an overpressure prevails in the pressure chamber, which inflates the seal. But even in embodiments and/or operating conditions in which an overpressure from the outside acts on the pressure chamber height, for example if 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 also allows the contact force between the seal and the rotary valve and the housing to be increased. The increased tightness due to the groove-shaped pressure chamber with regard to such operating conditions can also be referred to as backflow resistance.

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 for 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 pushed 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 with the pressure acting in the pressure chamber.

A further advantage of the self-reinforcing seal according to the invention by flooding the channel is that the valve drive can be designed smaller than with conventional systems, since less torque is required for adjustment as long as the contact pressure is not increased by the fluid pressure. For example, when adjusting the rotary slide, transition states occur in which both the line and the housing are flooded, so that the fluid pressure in the pressure chamber is compensated by the pressure acting on the pressure chamber from the outside. This means that the rotary slide can be adjusted with little torque. As soon as the rotary slide is in its final position, in which a line is again 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 once again created.

The pressure chamber preferably runs around a fluid passage opening of the seal. The fluid passage opening can basically take on any size and/or shape. For the preferred use described below in vehicle fluid flow control systems such as vehicle thermal management fluid control systems, in particular vehicle cooling circuits, a circular, oval or disc-shaped shape as well as the dimensions described above have proven to be advantageous as the shape of the fluid passage opening.

The pressure chamber preferably runs around the fluid passage opening along its outer contour. The pressure chamber is preferably formed by a groove, in particular a V-shaped groove, running around the fluid passage opening. The pressure chamber, in particular the groove, preferably tapers from a side of the seal facing the housing to a side of the seal facing the rotary valve. The pressure chamber is particularly preferably delimited by an inner leg facing the fluid passage opening and an outer leg facing away from the fluid passage opening. The inner leg and the outer leg preferably run around the fluid passage opening completely, in particular the inner leg along the outer contour of the fluid passage opening and preferably the outer leg spaced through the pressure chamber along a contour adapted to the contour of the inner leg. The inner leg and the outer leg preferably run towards each other on the side facing the rotary valve. In particular, the inner leg and the outer leg run 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, which is in particular groove-shaped, extends between the inner leg and the outer leg. Preferably, the inner leg and the outer leg are designed to seal 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.

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 there is an excess pressure acting on the pressure chamber from the outside (in relation to the internal pressure in the chamber), namely because the spaced apart The inner and outer legs are pressed together by the excess pressure, thereby increasing the contact force between the seal and the housing as well as between the seal and the rotary valve.

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. The inner sealing surface and the outer sealing surface preferably 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 surrounds the fluid passage opening without interruption in the assembled state, in particular in such a way 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 six communication 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 also preferably extends between a foot of the seal to be placed on the housing and the housing. In an alternative embodiment, however, the communication channel can also be formed by an opening, in particular a channel, completely enclosed by the outer leg.

The seal preferably has a foot to be placed on 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 force against the housing and thus further prevent the risk of the seal slipping. The foot preferably runs completely around the fluid passage opening. In the embodiments described in detail below with several fluid passage openings in a seal, the foot preferably runs around all of the fluid passage openings.

The foot preferably adjoins the previously described outer leg. The foot particularly preferably adjoins the end of the outer leg facing the housing. The foot is preferably 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 makes it possible to form a large contact surface via which the foot can be pressed against the housing via the fluid pressure in order to prevent the seal from slipping.

In the assembled state, the communication channel preferably extends between the base and the housing. Particularly preferably, the at least one communication channel can have a groove formed in the base, which fluidically connects an intermediate space between the housing and the rotary valve to the pressure chamber. If there are several communication channels, these are preferably distributed in the circumferential direction around the fluid passage opening, in particular distributed at equidistant intervals in the circumferential direction around it.

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. 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 runs around the fluid passage opening. The pressure chamber is preferably formed between the inner sealing leg and the outer sealing leg. In particular 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 in order 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. The support ribs particularly preferably divide the pressure chamber into several chamber sections. The support ribs particularly preferably extend from the side of the seal facing the rotary slide valve, in particular between the inner leg and the outer leg, to the side of the seal facing the housing. The support ribs are preferably designed in such a way that a fluid connection is made possible 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 embodiments, however, communication openings can also be formed in the support ribs in order 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 once again increase the reliability of the seal.

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 at least one, preferably a plurality of, communication opening(s) on a side facing the intermediate space, 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 introduced into the outer leg facing away from the fluid passage opening, which forms the at least one communication channel. Preferably, several grooves are provided, each of which forms a communication channel. Particularly preferably, the at least one groove is introduced 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 designed as a hole in the seal, in particular in the outer leg of the seal, which is completely surrounded by the sealing material of the seal. Particularly preferably, the groove is not only made in the outer leg, but also in 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 to 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. Preferably, one leg 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 adjoins the outer leg of the previously described L in cross-section and forms with it a V-shape widening towards the housing.

In one embodiment, the fluid passage opening is circular. In this embodiment, the pressure chamber preferably extends in a ring 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 slide valve. In this embodiment, the seal particularly preferably has a sealing surface facing the housing that has an uninterrupted ring shape. The sealing surface is preferably designed like the inner sealing surface described above. In addition, the seal preferably has an outer sealing surface facing the rotary slide valve, which preferably extends in an uninterrupted ring around the fluid passage opening. The inner sealing surface and the outer sealing surface are preferably formed by the inner leg described above, in particular connected to one another. This outer sealing surface and/or the inner sealing surface preferably extend 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 faces the housing. The interrupted sealing surface is interrupted in particular by the at least one communication channel described above, preferably by a plurality of communication channels that are preferably spaced apart from one another in the circumferential direction, in particular spaced apart from one another at equidistant intervals. This interrupted sealing surface is preferably formed at the end of the outer leg described above that faces the housing. The outer leg particularly preferably runs towards the inner leg in the axial direction (opposite the axis of symmetry of the circular fluid passage opening), in particular such that the inner leg and the outer leg form a V-shaped structure.

The previously described foot preferably adjoins the interrupted annular sealing surface, which extends outwards in the radial direction, in particular opposite 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 from the outside in the radial direction via the foot through the at least one communication channel. The foot preferably runs completely around the pressure chamber, and in particular the outer leg, in the circumferential direction. The foot can in particular be designed to be planar.

In an alternative embodiment, the fluid passage opening is oval. In this embodiment, the seal is preferably designed as previously described for the embodiment with a circular fluid passage opening, 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 passage openings. The fluid passage openings can have a common flow direction. In the case of symmetrical fluid passage openings, 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 passage openings, the common flow direction can be defined by the normal of the passage opening. In an embodiment with at least two fluid passage openings, 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 passage openings are arranged offset. For example, the at least two, preferably at least three, fluid passage openings can be designed in the shape of disc sections. In the case of an embodiment with several fluid passage openings, the seal preferably has its own pressure chamber for each seal. Each of the pressure chambers preferably runs around one of the fluid passage openings. 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 intermediate 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 passage openings which are 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 to the intermediate space in the radial direction outwards 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 passage openings 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 a coolant. 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 connected to the fluid passage opening and a rotary slide arranged in the housing. The directional control valve also has a rotary slide connected to the housing and the rotary slide. slide valve and encircling 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. In terms of size, essentially means in particular 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 narrowing of the flow cross section through 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 valve is essentially 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.

The housing preferably 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. A fluid line is preferably connected to each of the fluid passage openings. 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 in the casing of the housing. 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 front side 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 rotary valve, can establish a fluid connection between at least two or at least three fluid lines. Furthermore, the rotary valve can have blocking sections with which it can close fluid lines from other fluid lines. The rotary valve is preferably cylindrical. The fluid passage opening can be designed as a recess in the cylinder. The outer diameter of the rotary valve is preferably smaller than the inner diameter of the housing. This provides a movement play between the rotary valve and the housing. The seal(s) is/are preferably 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 valve and the housing, thereby providing a contact force. The 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 blocked. 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.

The outer leg preferably extends from the inner sealing surface to the housing. The outer leg preferably forms a sealing surface with the housing that is interrupted by the communication channels but otherwise runs all the way around. 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 previously described, a foot of the seal 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). The communication channel preferably extends through the foot and has a communication opening opposite the gap between the housing and the rotary valve. This preferably allows fluid to flow from the gap between the rotary valve and the housing into the pressure chamber via the communication channel. The directional control valve is preferably designed in such a way that the gap 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 fluid line connected to the fluid passage opening can drop, for example if no more fluid is flowing through the fluid line or if no more fluid is present. The pressure on the seal via the inner leg of the seal facing the fluid line is lower than that exerted by the flooded pressure chamber. This causes the pressure chamber to inflate, which in turn presses the seal 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 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 inclusions. This can prevent cavitation in particular and ensure reliable heat transport through the fluid. A system consisting of a directional control valve and an expansion tank is preferably provided for this purpose, so that air remaining in the valve 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 direction of fluid passage. In an alternative embodiment, the inner leg can be longer than the outer leg. In this embodiment, a groove, preferably annular or oval, can be formed in the housing, in particular to the shape of the inner leg, in which the inner leg can be accommodated with a precise fit when the seal 1 is mounted. The inner leg can be accommodated in the groove in particular using a "tongue and groove" principle. In this embodiment, the seal can provide improved tightness in both directions of pressure.

A further aspect of the invention relates to a directional control valve, which can be designed in particular like the previously described directional control valve, for adjusting the flow of a fluid, such as a coolant. The directional control valve comprises a housing with a fluid passage opening, a fluid line connected to 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 encircling 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 prevents the seal from slipping into the fluid passage opening. The support structure can encircle the fluid passage opening of the housing in the shape of a collar. In particular, the support structure can have a ring shape, which preferably has the same diameter as the fluid passage opening. The support structure is preferably formed in one piece with the housing. The housing preferably has an essentially cylinder-shaped inner surface, which is interrupted by the fluid passage opening. Starting from the cylinder jacket-shaped inner surface, the support structure preferably projects into the housing. The support structure is preferably 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 ring-shaped. In the case of an oval fluid passage opening, the support structure is preferably oval.

The seal preferably rests on the support structure. In particular, the side of the seal facing the fluid passage opening rests on the support structure. The seal is preferably adapted to the shape of the support structure in the area in which it is in contact with the support structure. The seal preferably runs completely around the support structure. The previously described inner leg of the seal particularly preferably rests on the support structure. The inner leg particularly preferably rests on the support structure over at least 10%, 20%, or 30% of its extension between the previously described inner sealing surface and the outer sealing surface. The support structure and seal are particularly preferably coordinated with one another according to the tongue-and-groove principle in order to prevent the seal from slipping into the fluid passage opening. Starting from the inner leg, the seal preferably has a projection, in particular a circumferential projection, which projects towards the fluid passage opening and preferably rests on the support structure. The projection and the section resting on the support structure particularly preferably 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 previously described foot, is supported. The outer support structure can extend inwards from the cylinder-shaped inner surface of the rotary slide valve. extending web. In particular, the web can extend inwards into the housing in a radial direction. The web can particularly preferably be T-shaped. As a result, a recess can be formed, in particular between the roof of the T and the cylinder-jacket-shaped inner surface of the housing, into which 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 the flooding of the pressure chamber with fluid, in the radial direction (or towards or away from the fluid passage opening) is limited or prevented. As a result, the expansion of the pressure chamber can take place in particular in the form of an expansion 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.

The directional control valve is preferably designed to flood the housing, in particular an intermediate space between the housing and the directional control valve. This can be achieved, for example, by the rotary slide valve having at least one fluid passage opening through which the fluid can flow in and out of the rotary slide valve, wherein the fluid passage opening of the rotary slide valve is preferably larger than the fluid passage opening of the housing and/or the seal. This ensures that even when the fluid passage opening of the rotary slide valve is perfectly centered 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 intermediate space between the housing and the rotary slide valve) is permitted. This secondary fluid flow floods the intermediate space and thus the pressure chambers via the intermediate space, thereby providing the self-reinforcing seal.

In embodiments in which the fluid passage openings of the housing are formed in the cylinder jacket of the housing, the fluid passage opening of the rotary slide 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 slide 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 slide valve can, for example, have a cylindrical basic shape in which the fluid passage opening is formed as a disc-shaped recess. The fluid passage opening is preferably designed in such a way that it can be brought into fluid connection with the fluid passage openings of the housing via the cylinder jacket.

In the case of end face designs, the rotary valve can be designed as a circular disk in particular, which has fluid passage openings running through it in the axial direction. Here too, the fluid passage openings in the rotary valve are preferably larger than the fluid passage openings in the housing in order to provide flooding of 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.

• 1a: eine perspektivische Vorderansicht auf eine Ausführungsform einer erfindungsgemäßen Dichtung;
• 1b: eine perspektivische Rückansicht auf die Dichtung aus 1a;
• 1c: eine perspektivische Seitenansicht auf die Dichtung aus 1a;
• 2a: eine Ansicht auf eine erfindungsgemäße Ausführungsform eines Vierwegeventils;
• 2b: eine seitliche Schnittansicht auf das Wegeventil gemäß 2a;
• 2c: eine Schnittansicht von oben auf das Vierwegeventil aus 2a;
• 2d: eine vergrößerte Ansicht des Abschnitts a aus 2c;
• 2e: die Ansicht gemäß 2c mit einer veränderten Stellung des Drehschiebers;
• 2f: die Ansicht gemäß 2e mit einer abermals veränderten Stellung des Wegeventils;
• 3a: eine perspektivische Ansicht auf eine weitere erfindungsgemäße Ausführungsform in Form eines Dreiwegeventils;
• 3b: eine Ansicht von oben auf das Dreiwegeventil gemäß 3a;
• 4a: eine perspektivische Ansicht eines Drehschiebers für eine weitere erfindungsgemäße Ausführungsform eines Vierwegeventils;
• 4b: eine Ansicht von oben auf ein Vierwegeventil mit dem Drehschieber aus 4a;
• 5a: eine perspektivische Ansicht auf eine weitere erfindungsgemäße Ausführungsform in Form eines Sechswegeventils;
• 5b: eine Schnittansicht von oben auf das Sechswegeventil gemäß 5a;
• 5c: eine perspektivische Ansicht von oben auf das Sechswegeventil gemäß 5a mit Deckel;
• 6a: eine perspektivische Vorderansicht auf eine weitere erfindungsgemäße Ausführungsform in Form einer ovalen Dichtung;
• 6b: eine perspektivische Rückansicht auf die Dichtung gemäß 6a;
• 7a: eine Vorderansicht auf eine weitere erfindungsgemäße Ausführungsform in Form einer Stirnflächendichtung;
• 7b: eine Rückansicht auf die Dichtung gemäß 7a;
• 8a: eine perspektivische Seitenansicht auf ein Vierwegeventil mit einer erfindungsgemäßen Dichtung gemäß 7a;
• 8b: eine Schnittansicht des Vierwegeventils gemäß 8a;
• 8c: eine weitere Schnittansicht des Vierwegeventils gemäß 8a;
• 8d: eine vergrößerte Ansicht eines Bereichs aus 8c
• 9a: eine Seitenansicht auf eine weitere beispielhafte Ausführungsform einer erfindungsgemäßen Dichtung; und
• 9b: eine seitliche Schnittansicht auf die Dichtung gemäß 9a.

In the following, further properties, features and advantages of the invention will become clear by describing preferred embodiments of the invention with reference to the accompanying exemplary drawings, in which:

• 1a : a perspective front view of an embodiment of a seal according to the invention;
• 1b : a perspective rear view of the seal from 1a ;
• 1c : a perspective side view of the seal from 1a ;
• 2a : a view of an embodiment of a four-way valve according to the invention;
• 2 B : a side sectional view of the directional control valve according to 2a ;
• 2c : a top view of the four-way valve from 2a ;
• 2d : an enlarged view of section a from 2c ;
• 2e : the view according to 2c with a changed position of the rotary valve;
• 2f : the view according to 2e with a further changed position of the directional control valve;
• 3a : a perspective view of a further embodiment according to the invention in the form of a three-way valve;
• 3b : a top view of the three-way valve according to 3a ;
• 4a : a perspective view of a rotary slide valve for a further embodiment of a four-way valve according to the invention;
• 4b : a top view of a four-way valve with the rotary slide made of 4a ;
• 5a : a perspective view of a further embodiment according to the invention in the form of a six-way valve;
• 5b : a sectional view from above of the six-way valve according to 5a ;
• 5c : a perspective view from above of the six-way valve according to 5a with lid;
• 6a : a perspective front view of a further embodiment according to the invention in the form of an oval seal;
• 6b : a perspective rear view of the seal according to 6a ;
• 7a : a front view of a further embodiment according to the invention in the form of a face seal;
• 7b : a rear view of the seal according to 7a ;
• 8a : a perspective side view of a four-way valve with a seal according to the invention according to 7a ;
• 8b : a sectional view of the four-way valve according to 8a ;
• 8c : another sectional view of the four-way valve according to 8a ;
• 8d : a magnified view of an area 8c
• 9a : a side view of another exemplary embodiment of a seal according to the invention; and
• 9b : a side sectional view of the seal according to 9a .

The 1a to 1c show different views of an embodiment of a seal 1 according to the invention with a circular fluid passage opening 3. 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 valves 9 and housings 11. Such embodiments of seal 1, 1' can be referred to as jacket design. The 7a and 7b show different views of an alternative embodiment of a seal 1'' with three disk-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 seals 1, 1', 1'' shown 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 a flow 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 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 in order to determine the normal, i.e. in the 1a to 1c as a circle and at the 6a and 6b as an oval shape. 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 as the center axis A. Wherever circumferential direction U or radial direction R is mentioned below, these directions each refer to the center axis A.

The respective communication channel 15, 15', 15'' of the seals 1, 1', 1'' completely encircles the fluid passage opening 3, 3', 3'' in the circumferential direction U. In the embodiments shown, 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 disk-shaped outer contour of the fluid passage openings 3''. In all of the embodiments shown, the pressure chambers 13, 13' and 13'' are designed as a groove made in the sealing material of the respective seal 1, 1', 1''. In the embodiments shown guide shapes, 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 shown, 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 towards each other in the axial direction A, in particular towards each other in the direction of the side of the seal 1, 1', 1'' facing the rotary valve, in particular towards each other in a V-shape. On the side of the seal 1, 1', 1''' facing the housing 11, 11'', 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 course 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 surrounds the pressure chamber 13, 13', 13'' in the circumferential direction U. The distance between the respective inner leg 17, 17', 17'' and the outer leg 19, 19', 19'' in the radial direction R defines a circumferential opening in the pressure chamber 13, 13', 13'', which is particularly annular in the case of seal 1, oval in the case of seal 1' and disc-shaped in the case of seal 1'' and which is closed by the housing 11, 11'' of the rotary valve when the respective seal 1, 1', 1'' is installed. 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 installed state.

2d shows a cross-sectional view of area A from 2c the seal 1 in sealing contact with the rotary valve 9 and the housing 11 of the directional control valve 21 according to the 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 valve to form the sealing contact. The outer sealing surface 23 and the inner sealing surface 25 encircle 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 encircle the fluid passage opening 3 in a ring shape. In the seal 1, corresponding inner sealing surfaces 25 and outer sealing surfaces 23 encircle the fluid passage opening 3' along an oval contour. In the seal 1'', corresponding inner sealing surfaces 25 and outer sealing surfaces 23 encircle the respective fluid passage opening 3'' in the shape of a disc section. As can be seen in particular from the overlap area 27 in 2d can be removed, 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 force which creates the sealing contact, in particular in the area 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'' can be flooded with fluid. As a result, fluid can pass 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 example of the flow path of the fluid from the intermediate space 31 into the pressure chamber 13 (secondary flow) is shown schematically with the dashed line 33. The 2d The fluid passage opening 3, which can be seen in sections, is in a closed position in the operating state shown. This is characterized in that a blocking section 35 of the rotary slide 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 jacket 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 example through 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, as a result of which the pressure chamber can be inflated. This allows the contact pressure to be increased, particularly with regard to the circumferential sealing surfaces 23 and 25, which increases the sealing contact and the tightness of the seal or the directional control valve. This provides a self-reinforcing, fluid-force-assisted seal.

How 2d can be removed, 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 cylinder jacket 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 placed on 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 connect in the radial direction R to the outside of the end of the seal 1, 1', 1'' facing the housing 11 and 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 be placed against a cylinder jacket 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'' can have an annular shape, as shown in the case of seal 1'', which runs around the individual fluid passage openings 3'' in sections and completely runs around the arrangement of the multiple fluid passage openings 3''. Furthermore, in embodiments with multiple fluid passage openings 3'', the foot 37'' can have, in addition to the outer contour 39, webs 41 extending to the center of the seal 1'', which 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''. Preferably, the communication channels are designed as V-shaped grooves. The communication channels 15, 15', 15'' can extend between the foot 37, 37', 37'' and the housing 11 in the assembled state, in particular be enclosed by the housing and the respective foot.

Preferably, a seal 1 has a plurality of communication channels 15, 15', 15'', which are arranged offset from one another in the circumferential direction U, in particular 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''.

The communication channels 15, 15', 15'' preferably 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''. The respective foot 37, 37', 37'' preferably has an active surface 45 facing the rotary slide valve 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 that counteracts a relative movement between the seal 1, 1', 1'' and the housing 11. Furthermore, the foot 37, 37', 37'' preferably has a contact surface 47 on the side facing the housing.

Preferably, the contact surface 47, 47', 47'' is interrupted by the previously described communication channels 15, 15', 15'', in particular when they are 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 effective surface 45, 45', 45''. Essentially is to be understood as a deviation of in particular a maximum of 20%, 15% or 10%. Taking additional account of 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'' divide the respective pressure chamber 13, 13', 13'' into chamber sections 51, 51'', 51'' between which preferably a fluid outlet exchange is 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 cylinder jacket 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 at a distance from one another in the respective pressure chamber 13, 13', 13''.

The 2a - 2f show different views of an embodiment of a four-way valve 21 for adjusting the flow of a fluid, such as a coolant. The four-way valve 21 comprises a housing 11 with four fluid passage openings 53, 55. The housing is cylindrical. Three fluid passage openings 53 are provided in the casing of the housing. The three fluid passage openings 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 each offset by 120° from one another. The fluid passage openings 53 are provided as circular recesses in the casing of the housing 11. The fourth fluid passage opening 55 of the housing 11 is provided on the front side of the housing 11. The fluid passage opening 55 is also circular. The four-way valve 21 also has a fluid line 57, 59 connecting to each of the fluid passage openings 53, 55. The fluid lines 57, 59 are each designed as 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 with respect 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 comprises 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 a movement play between the rotary slide valve 9 and the housing 11. Between the rotary slide valve 9 and the fluid lines 57 there is a seal 1, as shown in the 1a - 1c shown, which are in sealing contact with the rotary slide 9 and the housing 11. The seals 1 each run around one of the three fluid passage openings 53. The fluid passage openings 53 of the seals 1 are each aligned with the fluid passage openings 53 in the housing 11.

The rotary valve 9 is arranged rotatably 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 a fluid passage opening 63 on its side facing the fluid passage opening 55, which is aligned with the fluid passage opening 55 of the housing. The fluid passage opening 63 is arranged coaxially to the axis of rotation 65 of the rotary valve 9. In particular, the fluid passage opening 63 is circular and coaxially arranged to the fluid passage opening 55 in the housing. With the rotary valve 9 shown, the fluid passage opening 63 is always switched to active, in particular in such a way that fluid exchange between the rotary valve 9 and the fluid line 59 is always permitted regardless of the position of the rotary valve. The rotary valve 9 further comprises 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 front side and exit via openings in the casing and vice versa. As can be seen in particular from the 2c , 2e and 2f can be removed, the fluid passage opening 67 is designed to be larger than the fluid passage openings 53 of the housing 11 and the fluid lines 57. As a result, the fluid line 59 for a 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 permitted via the intermediate space 31 between the rotary slide 9 and the housing 11 (cf. 2c and 2f) Furthermore, the fluid passage opening 67 in this embodiment is designed to be so large that two of the fluid lines 57 can be connected to the fluid line 59 at the same time. This means that, for example, fluid flows from two lines can be guided into one line or a fluid flow from one line can 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 to flood the housing 11, in particular the intermediate space 31 between the housing 11 and the rotary slide valve 9.

The 3a and 3b show an embodiment of a three-way valve 21iv. The three-way valve 21iv is very similar to the four-way valve 21, so that the differences between them will be discussed in particular below. The three-way valve ^21iv has three fluid lines 57, which connect to fluid passage openings 53 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 slide valve 9. The third fluid passage opening 59 is designed free of 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 over approximately 90° in the circumferential direction relative to the casing of the rotary valve 9 into the latter. In particular, the fluid passage opening 67 of the rotary valve 11 is designed 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) and fluid lines 59 connected to these. 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 9 in turn has two fluid passage openings 67, which each extend over 90° of the casing of the rotary slide 9 in the circumferential direction. This allows two pairs of fluid lines 59 to be connected to one another independently of one another. A seal 1 is arranged at each of the fluid passage openings 53 between the rotary slide 9 and the housing 11.

The 5a-5c show an embodiment of a directional control valve ^vi with six fluid passage openings arranged offset from one another in the circumferential direction (relative to the axis of symmetry of the cylindrical housing 11). 5c shows an embodiment of a rotary valve 9 with six fluid passage openings 53, which are arranged offset from one another in the circumferential direction (relative to the axis of symmetry of the cylindrical rotary valve 9), in particular are arranged at equidistant distances from one another, in particular are introduced into the jacket of the cylindrical rotary valve 9. At each of the six fluid passage openings 53, a seal 1 according to the 1a - 1c appropriate.

The 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 connect to the cylindrical housing 11 via the front side. 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 are arranged offset from one another by 120°. A disk-shaped rotary slide 9'' is provided for closing and opening the fluid passage openings 55''. Fluid passage openings 67'' are provided in the disk-shaped rotary slide 9'', which can be arranged in alignment with the fluid passage openings 55'' to expose the fluid passage openings 55'' by adjusting the rotary slide 9''. To block the fluid passage openings 55'', the rotary slide valve 9'' has blocking sections 35''. The housing also has a fluid passage opening 53'' made in the casing of the housing 11'', to which a fluid line 59'' is connected. Between the disk-shaped rotary slide valve 9'' and the cylindrical housing 11'', a cylindrical intermediate space is provided, which can be flooded with the fluid that is set by the directional control valve. One or more primary fluid flows between the fluid lines 57'' and 59'' can be connected to one another via the intermediate space 31'', and one or more secondary fluid flows can be fed via the respective communication channels 15'' into the pressure chambers 13'' of the seal 1'' according to 7a and 7b The seal 1'' is arranged between the disc-shaped rotary valve 9'' and the front side 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 the respective seal 1, 1'' from slipping 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 collar that is opposite the surfaces of the housing 11, 11'' with which the seal 1, 1'' are in sealing contact and a structure, in particular annular structure, protrudes inwards into the housing.

Furthermore, the directional control valve preferably has an outer support structure 77, 79, 81 in addition to the previously described support structure, which can also be referred to as inner support structure 75, 75''. The outer support structure 77 can, for example, be made of 2d can be seen, be designed as a recess 77 formed in the housing 11, into which the foot 37, 37', 37'' of the seal 1 projects. This can ensure in particular that as a result of excess pressure forming in the pressure chamber 13, the resulting expansion does not lead to a spreading of the inner leg 17 and outer leg 19, but to an expansion of the pressure chamber 13 in the axial direction A, which strengthens the sealing contact, in particular in the area of the sealing surfaces 23, 25. 8d an alternative embodiment of the outer support structure 79, 81 can be removed. 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.

In the 9a and 9b another exemplary embodiment of a seal 1''' according to the invention is shown. The seal 1''' differs from the seal 1 in the 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'''. In the housing 11 (in the 9a and 9b not shown) an annular groove adapted to the longer inner leg 17''' can be formed, in which the inner leg 17''' is precisely received when the seal 1''' is mounted. 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 tightness 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 realization of the invention in the various embodiments.

List of reference symbols:

1, 1', 1'', 1''

poetry

3, 3', 3'', 3''`

Fluid passage opening

5

Surface of the rotary valve

7

Housing surface

9, 9''

Rotary valve

11, 11''

Housing

13, 13', 13'', 13''''

Pressure chamber

15, 15', 15'', 15'''

Communication channel

17, 17', 17'', 17'''

Inner thigh

19, 19', 19'', 19'''

Outer thigh

21, 21', 21'', 21'''

Way valve

23

External sealing surface

25

Internal sealing surface

27

Overlap area

31, 31''

Space

33

Secondary fluid flow

35,35', 35''

Restricted section

37, 37', 37'', 37'''

Foot

39

Outer contour

41

web

43

Communication channel

45, 45', 45''

Effective area

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

Rotary valve axis of rotation

67, 67''

Fluid passage opening

75, 75''

internal support structure

77

external support structure

79

Housing surface / external support structure

81

Tenon / external support structure

D

Flow direction

A

Central axis

U

Circumferential direction

R

Radial direction

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions.

Cited patent literature

• WO 2022025513 [0005, 0006]

Claims (18)

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 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. Seal (1, 1', 1'', 1''') according to Claim 1 , characterized in that the pressure chamber (13, 13', 13', 13'''') runs around a fluid passage opening of the seal (1, 1', 1'', 1'''), in particular runs along the outer contour of the fluid passage opening. 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. 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'''). Seal (1, 1', 1'', 1''') according to Claim 3 or 4 , characterized in that the inner leg (17, 17', 17'', 17''') has an outer sealing surface (23) facing the housing (11, 11'') and an inner sealing surface (25) facing the rotary slide (9, 9'') for forming the sealing contact, wherein the inner sealing surface (25) and/or the outer sealing surface (23) preferably run around 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''`) tapers, in particular in a V-shape, from a side of the seal (1, 1', 1'', 1''') facing the housing (11, 11'') to a side of the seal (1, 1', 1'', 1''') facing the rotary slide valve (9, 9''). Seal (1, 1', 1'', 1''') according to one of the preceding claims, characterized in that 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'') for forming the sealing contact, 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 placed against the housing (11, 11'') with an active surface facing the rotary slide (9, 9''), via which, when the housing (11, 11'') is flooded with the fluid, the fluid pressure presses the foot (37, 37') against the housing (11, 11''), 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''). 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') is connected to the outer leg (19, 19', 19'', 19''') according to one of the Claims 3 until 5 connects. 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''') 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 the Claims 3 until 5 extends. 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''') to an intermediate space (31, 31'') between the housing (11, 11'') and the rotary slide valve (9, 9''). 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 valve (9, 9'') arranged in the housing (11, 11''), and - a seal (1, 1', 1'', 1''') according to one of the preceding claims, which is in sealing contact with the housing (11, 11'') and the rotary slide valve (9, 9'') and runs around the fluid passage opening. Directional control valve (21), in particular according to Claim 12 , to adjust the flow of a Fluids, 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 valve (9, 9'') arranged in the housing (11, 11''), and - a seal (1, 1', 1'', 1''') which is in sealing contact with the housing (11, 11'') and the rotary slide valve (9, 9'') and surrounds 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 counteracts the seal (1, 1', 1'', 1''') from slipping into the fluid passage opening. Directional valve (21) after Claim 13 , characterized in that the support structure (75, 75'') surrounds the fluid passage opening in the form of a collar, in particular wherein the seal (1, 1', 1'', 1'''), in particular the inner leg (17, 17', 17'', 17''') according to one of the Claims 3 until 5 , rests against the support structure (75, 75''). Directional valve (21) after Claim 12 or 14 , characterized by an outer support structure (77, 79, 81) to 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 the Claims 3 until 5 or a foot (37, 37') after one of the Claims 8 until 9 , supports. Directional control valve (21) according to one of the Claims 12 until 15 , characterized in that the directional control valve (21) is designed to flood the housing (11, 11''), in particular an intermediate space (31, 31'') between the housing (11, 11'') and the directional control valve (21). Directional control valve (21) according to one of the Claims 12 until 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'''). Motor vehicle fluid flow control system, in particular motor vehicle thermal management fluid control system, such as motor vehicle cooling circuit, comprising a Claims 12 until 17 designed directional control valve (21) and, if necessary, a line system connected to the directional control valve (21).

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