CN113302423A

CN113302423A - Valve assembly with at least one reversing valve and clutch device with such a valve assembly

Info

Publication number: CN113302423A
Application number: CN202080009633.2A
Authority: CN
Inventors: M·魏甘特; M·维默肖夫
Original assignee: GKN Automotive Ltd
Current assignee: GKN Automotive Ltd
Priority date: 2019-01-17
Filing date: 2020-01-17
Publication date: 2021-08-24
Anticipated expiration: 2040-01-17
Also published as: WO2020148430A1; DE102019101133A1; CN113302423B

Abstract

The invention relates to a valve assembly with: at least one directional control valve (1) having a control piston (4) which is arranged in a valve space (3) of the at least one directional control valve (1) so as to be movable along a valve axis (X), wherein the at least one directional control valve (1) has at least two valves which are arranged axially offset from one anotherAn annular groove (9,10,11) which is in liquid-conducting connection with the valve space (3); and at least one connecting channel (18,19,38,39), wherein the at least one connecting channel (18,19,38,39) opens into one of the annular grooves (9,10,11) of the at least one switching valve (1) via one opening (26,27), and wherein the at least one connecting channel (18,19,38,39) has a central axis (L)₁₈,L₁₉,L₃₈,L₃₉) The central axis extends in a non-planar manner with respect to the valve axis (X). The invention further relates to a clutch device having such a valve assembly.

Description

Valve assembly with at least one reversing valve and clutch device with such a valve assembly

Technical Field

The invention relates to a valve assembly having at least one directional control valve with a control piston which is arranged displaceably along a valve axis in a valve space of the directional control valve, wherein the directional control valve has at least two annular grooves which are arranged offset from one another in the axial direction and which are in fluid-conducting connection with the valve space; and at least one connecting channel which opens into one of the annular grooves via the opening. The invention further relates to a clutch device having such a valve assembly.

Background

DE102012222698a1 discloses a valve assembly with a directional valve in which a control piston is arranged in a valve space so as to be movable along a valve axis. The switching valve has a plurality of annular grooves arranged offset from one another in the axial direction in the valve body which delimits the valve space, said annular grooves being in liquid-conducting connection with the valve space. One coupling channel opens into the respective annular groove, which is designed as a radial bore and thus extends perpendicularly to the valve axis.

DE102016000401a1 discloses a cartridge valve (cartidventil) in which the connections P, A and T are formed perpendicular to the valve axis. The valve is screwed into the hydraulic control block.

DE102007048324a1 discloses a valve device in which the connections P, A and T have a substantially funnel-shaped coupling section. The funnel-shaped coupling section opens into the valve space in a subsequently drilled coupling bore, which is preferably designed as a radial bore. Two openings may also be associated with each coupling portion.

Disclosure of Invention

The invention is based on the following tasks: a valve assembly is provided in which the maximum volume flow of a working medium supplied to a valve space can be increased or the pressure loss in the valve assembly can be reduced without structurally modifying a conventional reversing valve.

In order to solve this problem, a valve assembly of the type mentioned at the outset is proposed, in which the at least one coupling channel has a central axis which runs in a manner that is non-planar to the valve axis, and in which the ratio between the diameter of the circumferential surface of the at least one coupling channel and the axial extent of the respective annular groove can be 2 to 1.

When the two axes are neither parallel to each other nor have a common point of intersection, the two axes are non-planar with respect to each other. The central axis and the valve axis are straight. Such a groove is understood to be an annular groove, i.e. the groove can extend annularly around the valve axis or be formed concentrically to the valve axis. "at least one linking channel" shall include a linking channel or a plurality of linking channels; the same shall also apply to "at least one reversing valve", "at least one fluid channel", etc. The at least one directional control valve can be associated with exactly one connecting channel or a plurality of connecting channels, in particular two, three, four, five, six or more than six connecting channels.

Advantageously, in the at least one connecting channel, in which the axis runs non-coplanar to the valve axis, both the flow cross section of the respective opening and the axial distance from the adjacent annular groove are greater than in connecting channels arranged radially to the valve axis. Because of the orientation of the different surfaces, the extent or extension of the respective access opening in the circumferential direction of the respective annular groove increases. Thereby, it is possible to increase the maximum volume flow of the working medium and to reduce leakage losses in the valve assembly and the accompanying pressure losses. In contrast, in the case of radially arranged bores, the volume flow (within structurally predetermined limits) can only be increased by increasing the bore diameter. But this results in: on the one hand, the axial distance of the radial bores from one another must be reduced, and on the other hand the axial distance of the radial bores from the adjacent annular groove must be reduced, which in turn increases the leakage losses in the valve assembly and the associated pressure losses. By the ratio between the diameter of the circumferential surface of the at least one connecting channel and the axial extent of the respective annular groove, which may be from 2 to 1, on the one hand the respective annular groove can be supplied with a sufficiently high volume flow of working medium and on the other hand a sufficiently large distance from the adjacent annular groove can be maintained, whereby leakage losses are reduced.

In addition to the at least one connecting channel, the axis of which extends non-planarly with respect to the valve axis, the valve assembly can have at least one fluid channel, which opens into one of the annular grooves of the at least one directional control valve and the axis of which extends radially with respect to the valve axis. For better differentiation, the at least one channel, the axis of which extends radially with respect to the valve axis, is also referred to as a fluid channel, and the at least one channel, the axis of which extends non-planarly with respect to the valve axis, is referred to as a coupling channel.

Preferably, the at least one coupling channel is a pump coupling or a working coupling. In a manner known per se, the pump connection of the at least one directional control valve can be connected to a pump, while the working connection of the at least one directional control valve can be connected to a component to be controlled, for example to a cylinder of a clutch unit. In principle, however, it is also possible for the connecting channel to be a tank connection or an unloading connection which connects the at least one directional control valve to the tank. In the preferred case of a plurality of said connecting channels, at least a partial number of the connecting channels can open into different annular grooves of the at least one reversing valve and/or into the same annular groove of the at least one reversing valve. In particular, the coupling channel is a pump coupling and/or a working coupling.

According to one aspect, it can be provided that at least such an annular groove, into which the at least one connecting channel opens, is open toward the radially outer circumferential surface of the at least one directional control valve. The respective inlet opening can thus be formed by the annular groove of the respective connecting channel and the part of the wall opening that overlaps in particular in the axial direction. The wall opening of the corresponding coupling channel may also be referred to as discharge opening. The at least one connecting channel can thus be guided past the respective radially outwardly open annular groove and can open out radially into the annular groove. This enables the use of conventional or commercially common reversing valves without requiring structural modifications to the at least one reversing valve. In particular, all of the annular grooves of the at least one directional control valve can be open toward the radially outer circumferential surface of the at least one directional control valve. In addition, the annular grooves may be each bounded radially on the inside by a groove base which runs around in the circumferential direction, wherein in the groove base of the respective annular groove at least one through-opening is formed for the connection of the respective annular groove to the guide liquid of the valve space. In principle, however, the at least one directional control valve may also have an annular groove which is open radially inward toward the valve space. In such a reversing valve, the at least one connecting channel can flow into the respective annular groove via an opening formed in the groove base or can be arranged at a through-opening formed in the groove base.

Furthermore, the center axis of the at least one connecting channel can lie in a plane, wherein the valve axis extends perpendicular to the plane. Thereby, the extension or extension of the respective access opening in the circumferential direction around the valve axis is maximized. The access opening may have the shape of a long hole.

According to one embodiment, the at least one directional control valve can each have a valve body which delimits a valve space. The valve body may have at least two of the annular grooves of the at least one diverter valve. The valve body can also be designed as a sleeve.

According to one aspect, the minimum distance between the valve axis of the at least one directional control valve and the center axis of the at least one connecting channel may be greater than the inner radius of the at least one directional control valve. In other words, the center axis of the at least one connecting channel can be outside the valve space of the at least one directional control valve. As a result, the largest possible distance of the at least one connecting channel leading into one of the annular grooves from the adjacent annular groove is obtained, which is advantageous with regard to possible porosity problems. In this way, a particularly thick wall thickness between the components of the valve assembly that guide the working medium is achieved. This is particularly advantageous when the housing is made of cast material, since leakage losses can thereby be minimized or, at best, avoided altogether. Preferably, the central axis of the at least one connecting channel is outside the radially outer circumferential surface of the at least one directional control valve. In particular, the minimum distance between the center axis of the at least one connecting channel and the radially outer circumferential surface of the at least one switching valve is greater than 0.5 times the inner radius of the at least one connecting channel and/or less than 1 time the inner radius of the at least one connecting channel. Particularly good results with regard to minimizing leakage losses are achieved if the minimum distance between the center axis of the at least one connecting channel and the radially outer circumferential surface of the at least one directional control valve is between 0.6 and 0.95 times the inner radius of the at least one connecting channel.

Furthermore, a housing with at least one housing bore may be present, wherein the at least one directional control valve is received in each of the at least one housing bore. According to one possibility, the control piston can be arranged directly displaceably in the respective housing bore. This type of directional valve may also be referred to as a direct-acting directional valve. In a preferred manner, the at least one directional control valve has a valve body, so that the respective directional control valve can be inserted into the respective housing bore by means of the valve body, which is structurally separate from the housing. The housing can be screwed, for example, to a drive motor of a motor vehicle. The housing can also receive a pump, in particular a hydraulic pump, for the working medium. Preferably, the housing is designed for receiving a plurality of directional valves.

The housing can be designed in multiple parts or in one piece. The housing is preferably made of a cast material, wherein the housing can in principle also be made of a solid material or of a plastic material. In particular in the case of cast housings, it is advantageous if the at least one connecting channel is spaced as far as possible from the adjacent annular groove or further connecting channels or fluid channels, in order to avoid or minimize leakage losses or porosity problems.

In a preferred manner, the at least one coupling channel is formed in the housing, in particular completely in the housing. Suitably, the at least one coupling channel is configured as a cylindrical bore in the housing. In this way, the at least one connecting channel can be designed particularly simply in the housing. In principle, the at least one connecting channel can also be formed in or extend into the valve body of the at least one reversing valve. The valve body of the at least one directional control valve can likewise be made of a cast material or a plastic material, wherein the valve body is preferably made of a metallic solid material.

In particular, the at least one housing bore is delimited by a bore wall. At least one wall opening of the at least one coupling channel may be arranged in a wall of the respective housing bore. The at least one wall opening of the at least one coupling channel may be formed by an intersection curve of a circumferential surface of the at least one coupling channel with a wall of a bore. The resulting intersection curve may also be referred to as a penetration curve. The circumferential surface of the channel wall of the at least one connecting channel may be cylindrical, at least in the region of the intersecting curves. The housing bore is expediently designed cylindrical at least in the region of the at least one wall opening. The at least one wall opening may have a greater extension in a circumferential direction around the valve axis than in the axial direction. In particular, the axial extension of the at least one wall opening corresponds at least to 1 time and/or at most to 2 times the axial extension of the respective annular groove. Thereby, the at least one coupling channel is spaced as far as possible from an adjacent annular groove or further coupling channel or fluid channel, thereby avoiding or minimizing leakage losses or porosity problems.

According to one aspect, the at least one connecting channel may be arranged such that the minimum distance between the valve axis and the center axis of the at least one connecting channel is such that the radially outer annular edge of the respective annular groove is in the circumferential surface of the at least one connecting channel or touches it. The distance between the respective center axis of the at least one connecting channel and the associated annular groove is set or predetermined during the production of the respective connecting channel. By reducing the above-mentioned minimum spacing and maintaining the diameter of the at least one coupling channel, the resulting access opening, which results from the overlap of the annular groove and the wall opening of the coupling channel, is increased. However, the distance from the axially adjacent annular groove is also reduced, as a result of which the leakage losses can be increased. These factors, which are related to each other, should be taken into account in the design of the valve assembly. Particularly good results are achieved if the ratio between the groove height of the respective annular groove and the diameter of the circumferential surface of the at least one connecting channel is from 1 to 2 to 1. Accordingly, the diameter of the circumferential surface of the at least one connecting channel can be at most as large as twice the groove height of the respective annular groove into which the respective connecting channel opens. Furthermore, the diameter of the circumferential surface of the at least one connecting channel can be at least as large as the groove height of the respective annular groove into which the respective connecting channel opens. In the range produced by the maximum ratio and the minimum ratio, the diameter of the circumferential surface of the at least one connecting channel or the groove height of the respective annular groove can be adapted. Typically, the diameter of the circumferential surface of the at least one coupling channel is preset or adapted. This can be preset, for example, by drilling, when the at least one connecting channel is produced. For example, the height of the groove or the axial extension of the annular groove may be about 3.4 mm, while the diameter of the circumferential surface of the at least one coupling channel may be about 6.5 mm. Preferably, the diameter of the peripheral surface of the at least one coupling channel is less than or equal to 6.5 mm.

In a further preferred embodiment, a plurality of connecting channels is present. The connecting channels can have flow cross sections that are not as large or are as large. In order to further increase the volume flow or to reduce the pressure loss, a plurality of connecting channels, preferably two, three or four connecting channels, can open into one of the annular grooves, that is to say into the same annular groove. The connecting ducts can open into the respective annular groove distributed in the circumferential direction around the valve axis, for example on two diametrically opposite sides of the respective annular groove. Furthermore, at least two of the coupling channels may be axially spaced apart from each other. In this way, the at least two connecting ducts can open into two different annular grooves of the at least two annular grooves of the at least one reversing valve. In particular, the center axes of the at least two axially spaced connecting channels are arranged in axially spaced planes, wherein the valve axis can extend perpendicular to the planes. Thereby, the flow cross section of the access opening can be maximized. Furthermore, the coupling channels can be arranged distributed in the circumferential direction around the valve axis in order to increase the wall thickness of the housing between the individual coupling channels spaced apart from one another in the axial direction. In particular, when cast material is used for the housing, a wall thickness which is as large as possible is advantageous in order to minimize or, at best, completely avoid leakage losses.

Preferably, less than three of the central axes of the connecting channels, in particular less than two of the central axes of the connecting channels, are in each of the planes. It follows that each of the annular grooves can be connected in a liquid-conducting manner to exactly only one of the connecting channels or to exactly two of the connecting channels.

In particular, the at least one connecting channel may comprise at least one first connecting channel which opens into a first or lower annular groove of the at least two annular grooves arranged axially offset from one another, and at least one second connecting channel which opens into a second or intermediate annular groove of the at least two annular grooves arranged axially offset from one another. In this way, two of the annular grooves of the at least one reversing valve are each connected to at least one connecting channel. In order to increase the wall thickness between the connecting channels or the annular grooves, the center axes of the at least one first connecting channel can be arranged offset from one another, in particular 90 degrees from one another, in the circumferential direction about the valve axis relative to the center axis of the at least one second connecting channel. In each case, only exactly one connecting channel can open into the at least two annular grooves of the at least one reversing valve, which are spaced apart from one another in the axial direction, i.e. exactly one first connecting channel opens into the first annular groove and exactly one second connecting channel opens into the second annular groove, the two connecting channels can also be oriented parallel to one another. This results in a maximum distance between the two connecting channels, so that the wall thickness between the connecting channels is also maximum.

Preferably, two of the first connecting channels open into the first or lower annular groove and two of the second connecting channels open into the second or middle annular groove. In order to maximize the wall thickness and therewith minimize leakage losses, the central axes of the first coupling channels may be arranged parallel to each other. Furthermore, the center axes of the second connecting channels can also be arranged parallel to one another. Furthermore, the center axes of the first connecting channels can be arranged offset from one another, in particular offset by 90 degrees, with respect to the center axis of the second connecting channels about the valve axis.

According to a further embodiment, at least two of the directional control valves can be arranged adjacent to one another, wherein at least two of the connecting channels of adjacent directional control valves can each form a continuous connecting bore, the center axes of which coincide. In this way, a plurality of directional control valves arranged next to one another or one after the other with respect to a common center axis can be connected to a connection bore in a fluid-conducting manner.

The working medium may be, for example, a hydraulic liquid or compressed air or another fluid. The at least one directional control valve may be, for example, an 3/3 directional control valve, wherein other fluid valves or directional control valves are also possible. In the case of the 3/3 reversing valve, the at least one reversing valve can accordingly have three annular grooves arranged offset from one another in the axial direction. Preferably, the valve assembly has at least two of the directional control valves, in particular exactly two or exactly three or exactly four of the directional control valves. The directional control valves are preferably embedded in the same housing, which has its own housing bore for each of the directional control valves.

The object is further achieved by a clutch unit for a motor vehicle having the valve assembly described above. The mentioned solutions can be considered as alternatives or supplements to each other. It goes without saying here that all features mentioned in connection with the valve assembly can be transferred to the clutch unit and, conversely, all features mentioned in connection with the clutch unit can be transferred to the valve assembly.

Preferably, the valve assembly has at least two of the directional valves. The switching valve can be hydraulically connected on the input side via a pump connection to a pump line for the working medium and on the output side via a working connection to the friction clutch. The two friction clutches can jointly form a dual clutch unit, so that the torque can be variably distributed to the two output shafts of the drive shaft of the motor vehicle. The pump may be a hydraulic pump and the working medium may be a hydraulic liquid. In principle, it is also possible to use a compressed air generator as a pump in order to use compressed air as the working medium.

In particular, the valve assembly may have a third directional control valve for controlling the total pressure of the working medium for the valve assembly. The third directional control valve can be connected on the input side to the pump line via the pump connection and on the output side to the at least two further directional control valves via the working connection. By means of the third valve, the required pilot pressure of the downstream, in particular of the at least two reversing valves mentioned above, can be set. In this connection, the third directional valve can also be referred to as a pilot control valve, while the directional valve following in the flow direction is referred to as a main valve.

According to one aspect, the valve arrangement may have a fourth directional control valve, wherein the fourth directional control valve may be hydraulically connected on the input side via a pump connection to the pump and on the output side via the working connection to the shifting clutch. The fourth directional valve may likewise be a main valve which is downstream in the flow direction from the third directional valve which operates as a pilot control valve.

Further advantages, features and details emerge from the following description, in which at least one embodiment is described in detail, with reference to the figures, if possible. The features described and/or shown in the figures can constitute the subject matter of the invention by themselves or in any meaningful combination. If possible also independently of the claims, in particular additionally to the subject matter of one or more separate applications. Identical, similar and/or functionally identical components are provided with the same reference numerals.

Drawings

In the drawings:

FIG. 1 illustrates in longitudinal cross-section a valve assembly according to the present invention according to one embodiment of the present invention;

FIG. 2 shows a part-section of the valve assembly from FIG. 1, shown simplified, in a cross-sectional view along section line II-II shown in FIG. 1;

FIG. 3 shows an enlarged fragmentary section from the valve assembly of FIG. 1 in a longitudinal cross-sectional view;

FIG. 4 shows an enlarged partial view of a valve assembly according to a further embodiment in longitudinal section;

fig. 5 shows a schematic view of a clutch device according to the invention according to an embodiment of the invention; and

fig. 6 shows a clutch device according to a further embodiment of the invention.

Detailed Description

Fig. 1 to 3 show a valve assembly according to an embodiment of the present invention. The valve assembly can be used in a manner known per se for controlling one or more cylinders. Fig. 1 shows a fluid valve, in this case a directional valve 1, wherein in principle other fluid valves can also be provided. The directional valve 1 is designed as an 3/3 directional valve. The valve assembly is shown here with exactly one switching valve 1, wherein, depending on the application, the valve assembly can also have a plurality of, in particular two, three or four, fluid valves or switching valves 1, as is shown, for example, in the clutch device in fig. 5 or 6.

The directional valve 1 is inserted into a housing bore 16 of a housing 17. The housing 17 may be a one-piece formed housing that is preferably made of a cast material. The housing 17 (which may also be referred to as a hydraulic block) may also be milled from a solid material or made from a plastic material. A plurality of housing bores 16 can be formed in the housing 17 in order to be able to accommodate a plurality of directional control valves 1.

The reversing valve 1 has a valve body 2, which can also be referred to as a sleeve. The valve body 2 has a cylindrical basic shape which extends along the valve axis X or which defines the valve axis X. The valve body 2 is open on both end sides and delimits a radially inner valve space 3. The control piston 4 is movably arranged in the valve space 3 along a valve axis X.

The directional valve 1 can be (simplified) divided into three

longitudinal sections

5, 6, 7. In the first or lower longitudinal section 5, the control piston 4 is supported with its end face on a spring, in particular a helical spring 8, which engages in a housing bore 16 of a housing 17. The spring 8 acts with a preload force in the axial direction on the control piston 4 away from the spring 8. By means of the spring 8, the control piston 4 is prestressed in its position shown in fig. 1 against the actuator 15. A further helical spring 32 is inserted into the housing bore 16, on which the stepped lower end side of the valve body 2 is supported. Two

coil springs

8,32 arranged concentrically to the valve axis X are in turn supported at the bottom 31 of the housing bore 16, wherein the inner diameter of the coil spring 32 is greater than the outer diameter of the coil spring 8.

In the second longitudinal section 6 (which may also be referred to as the central longitudinal section), the 3/3 reversing valve has three

annular grooves

9,10,11, respectively, which are arranged offset from one another in the axial direction, in order to be able to connect the reversing valve 1 to the hydraulic connections (pump connection, tank connection and working connection). The

annular grooves

9,10,11 are open toward a radially outer cylindrical circumferential surface 12 of the reversing valve 1. Radially inwardly, the

annular grooves

9,10,11 are each bounded by a groove base 13. At least two through openings 14 are formed in the groove base 13 of the respective

annular groove

9,10,11 for the connection of the respective

annular groove

9,10,11 to the guide liquid of the valve space 3. Preferably, each of the

annular grooves

9,10,11 is connected with more than two, in particular three, four, five, six or more than six, of the through openings 14, respectively, which are arranged equally distributed in the circumferential direction around the valve axis X.

In the third or upper longitudinal section 7 of the directional valve 1, the valve space 3 is limited by an actuator 15, which is placed on the end face of the valve body 2. The actuator 15 can preferably be an electromagnetic actuator, wherein the directional valve 1 can in principle also be actuated electrically or mechanically or by pressure.

Two connecting

channels

18,19 are formed in the housing 17 (here), said connecting channels opening into the first or lower annular groove 9. The two

coupling channels

18,19 are pump coupling parts. Depending on how many volume flows of the working medium the valve assembly is designed for, only one

single pump connection

18 or 19 or more than the two illustrated

pump connections

18,19 may also be provided. The connecting

channels

18,19 are (in this case) designed as cylindrical bores in the housing 17, each of which runs along its own center axis L₁₈,L₁₉Extending and arranged heteroplanarly with respect to the valve axis X. Two central axes L₁₈,L₁₉In a common first plane E, which extends perpendicularly to the valve axis X. The connecting

channels

18,19 can be designed as blind holes.

The walls 21 of the housing bore 16 are restricted from being drilled or otherwise cut away or pierced during manufacture of the connecting

channels

18, 19. In this way, two

wall openings

22,23 are produced in the wall 21, each of which is formed by an intersection curve which is formed by the wall 21 of the cylindrical structure at least in the region of the

wall openings

22,23 when the cylindrical

circumferential surfaces

24,25 of the respective

cylindrical connecting ducts

18,19 are penetrated. The

wall openings

22,23 have a greater extension in the circumferential direction around the valve axis X than in the axial direction.

In the enlarged part shown in fig. 3, it can be seen that the first annular groove 9 and the

wall openings

22,23 of the directional valve 1 overlap one another in the axial direction. The opening

openings

26,27 are formed by the overlapping sections of the

respective wall openings

22,23 and the first annular groove 9, as is shown in fig. 2 to 4. The connecting channel 18 opens into the first annular groove 9, which is open radially outward, via the opening 26, and the connecting channel 19 opens into the first annular groove 9, which is open radially outward, via the opening 27.

The flow cross section of the

opening

26,27 is in particular linked to the groove height of the first annular groove 9 and the diameter d of the connecting

channel

18,19₁₈,d₁₉It is related. Particularly good results are obtained when the groove height of the first annular groove 9 corresponds to the diameter d of the connecting

channels

18,19₁₈,d₁₉In the range of 1:2 to 1: 1. By way of example, the groove height or axial extension of the first annular groove 9 may be about 3.4 mm, while the diameter d of the

peripheral surfaces

24,25 of the

respective coupling channels

18,19₁₈,d₁₉About 6.5 mm.

Furthermore, the flow cross-section of the

opening

26,27 and the center axis L of the connecting

channel

18,19 in the housing 17₁₈,L₁₉And is oriented with respect to the central axis L₁₈,L₁₉Minimum distance A relative to valve axis X₁,A₂It is related. In fig. 3 and 4, the center axis L is shown by way of example₁₉Two different minimum spacings with respect to the valve axis X. The same applies for both embodiments if the center axis L is used₁₉In a first plane E, the valve axis X is oriented perpendicularly to the first plane, and the outer diameter d of the connecting channel 19₁₉Are the same. Furthermore, the central axis L of the connecting

channels

18,19₁₈,L₁₉Outside the radially outer circumferential surface 12 of the reversing valve 1. The statements made with regard to the connection channel 19 also apply in the same way to the connection channel 18.

As can be seen in fig. 3, in the central axis L of the connecting channel 19₁₉Minimum distance A from valve axis X₁It can be provided that the radially outer

annular edges

28,29 of the first annular groove 9 touch the circumferential surface 25 of the connecting channel 19. The axial extension of the wall opening 23 thus corresponds to the axial extension of the annular groove 9 or to 1 time the groove height. As is also shown in figure 3 of the drawings,in the central axis L of the connecting channel 19₁₉The minimum distance A from the radially outer circumferential surface 12 of the directional valve 1₁At least corresponding to the inner radius r of the connecting channel 18₁₈About 0.9 times. The axial overlap of the wall opening 23 and the first annular groove 9 results in an opening 27, which may have the shape of an elongated hole. Furthermore, a maximum distance P of the connecting channel 19 from the adjacent annular groove 10 is obtained, which is advantageous with regard to possible porosity problems.

In order to increase the flow cross section of the opening 27, the central axis L can be arranged as shown in fig. 4₁₉Minimum distance A from valve axis X₂And becomes smaller. The axial extension of the wall opening 23 corresponds here to approximately 2 times the axial extension or groove height of the first annular groove 9. Also shown in fig. 4 is the central axis L of the connecting channel 19₁₉The minimum distance A from the radially outer circumferential surface 12 of the directional valve 1₂At least corresponding to the inner radius r of the connecting channel 18₁₈About 0.7 times. The axial overlap of the wall opening 23 and the first annular groove 9 likewise results in an opening 27, which may have the shape of an elongated hole.

Central axis L₁₉A distance A from the first annular groove 9₁Or A₂The smaller the flow cross section of the opening 27 that is produced. However, the distance P from the adjacent annular groove 10 is also reduced, as a result of which leakage losses can occur. These factors, which are related to each other, should be taken into account in the design of the valve assembly.

Two connecting

channels

38,39, which may also be referred to as working connections, open into the second or central annular groove 10. The working

connections

38,39 are offset by 90 degrees with respect to the two

pump connections

17,18, respectively, so that the working

connections

38,39 are not shown in the sectional view and are shown in fig. 1 with dashed lines only to illustrate the orientation of the working connections. The explanations given above for the coupling channels 18,19 (pump couplings) apply in a similar manner to the working

couplings

38, 39. Accordingly, the working

connections

38,39 can be designed as cylindrical bores in the form of blind bores, the center axes of which are arranged non-coplanar with respect to the valve axis X. The working

coupling parts

38,39 may be arranged on a second flat plateIn a plane E' which is parallel to the first plane E and axially spaced therefrom, the central axis L of the

pump connection

18,19₁₈,L₁₉In the first plane. In order to maximize the distance between the

pump coupling parts

18,19 and the working

coupling parts

38,39, they are arranged offset from one another in the circumferential direction about the valve axis X.

A fluid channel 30, which may also be referred to as a tank connection, opens into the third or upper annular groove 11. The tank coupling 30 can be connected to an unloading hole 20 formed in the housing 17, as shown in fig. 1. The tank coupling 30 may be connected with a not-shown tank via the unloading hole 20. The relief openings 20 are arranged radially with respect to the valve axis X or, like the connecting

channels

18,19,38,39, likewise are arranged non-coplanar with respect to the valve axis X. The directional valve 1 projects into the relief bore 20 in its first or lower longitudinal section 5. During operation of the directional valve 1, a minimum amount of working medium which arrives from the valve space 3 via the control piston 4 downwards or towards the

springs

8,32 can thus be received and guided back into the tank via the relief opening 20.

Although in the embodiment of the invention shown in fig. 1 to 4 the first annular groove 9 is connected to the

pump connection

18,19 or the second annular groove 10 is connected to the working

connection

38,39, the center axis L of the pump connection and the working connection being₁₈,L₁₉,L₃₈,L₃₉Each arranged in a manner that is different from the plane of the valve axis X, it can, however, also be provided in principle that only one of the

annular grooves

9,10 is also supplied by means of at least one connecting channel arranged in a manner that is different from the plane of the valve axis X. In addition or as an alternative to the

pump connections

18,19 or the working

connections

38,39, in principle such fluid ducts can also open into the

annular grooves

8, 9,10 that their central axes have a common intersection point with the valve axis X and enclose an angle, which may be 90 degrees, for example.

Fig. 5 shows a schematic illustration of an exemplary embodiment of a clutch device. The clutch device has a clutch unit 33, of which only the clutch actuator for actuating a disk clutch, not shown in detail, is shown in fig. 5 in a simplified manner. The clutch device also has at least one valve assembly, as already described in connection with fig. 1 to 4. The valve arrangement provided in the clutch device corresponds to the greatest extent to the valve arrangement according to fig. 1 to 4, and reference is made to the description of the valve arrangement according to fig. 1 to 4 in this respect in the same respect. The same or modified details are provided with the same reference numerals as in fig. 1 to 4.

The directional control valve 1 is connected on the input side via two

pump connections

18,19 to a hydraulic pump 34, which is driven by means of a motor 35. The hydraulic pump 34 is in turn coupled on the input side to a tank 36 for a working medium, wherein a filter 37 can be arranged between the hydraulic pump 34 and the tank 36. The directional valve 1 is connected on the working side via two working

connections

38,39 to the clutch actuator 33 and on the output side via the housing connection 30 to the housing 36.

Fig. 6 shows a partial section of a further exemplary embodiment of the clutch device in a simplified illustration. The present exemplary embodiment corresponds to the exemplary embodiment according to fig. 5 to the greatest extent, and reference is made to the description of the exemplary embodiment according to fig. 5 in this respect in the same respect. The same or modified details are provided with the same reference numerals as in fig. 1 to 4 or fig. 5. But only some details are provided with reference numerals for the sake of clarity.

The difference between the two embodiments according to fig. 5 and 6 is that the clutch device according to fig. 6 has a plurality of directional control valves 1, in this case four directional control valves 1.1,1.2,1.3, 1.4. The directional valves 1.1,1.2,1.3,1.4 are arranged in a common housing 17, wherein each of the directional valves 1.1,1.2,1.3,1.4 is inserted into its own housing bore 16. The directional valves 1.1,1.2,1.3,1.4 are connected to the tank via a common discharge opening 20.

The clutch unit can also have a (not shown) dual clutch unit with two friction clutches for variably distributing the torque to two (not shown) output shafts of a drive shaft of the motor vehicle. The two directional control valves 1.1,1.2 can actuate one of the two friction clutches. The third directional control valve 1.3 can be connected to a shifting clutch (not shown) of the clutch unit. The fourth additional directional control valve 1.4 can be used as a pilot control valve for regulating the pilot pressure of the downstream directional control valves 1.1,1.2, 1.3. In this connection, the upstream directional control valve 1.4 can also be referred to as a pilot control valve and the downstream directional control valves 1.1,1.2,1.3 in the flow direction are referred to as main valves.

In the sectional plane selected in fig. 6, it can be seen that the connecting

ducts

38,39 opening into the second annular groove 10 and the connecting

ducts

18,19 opening into the first annular groove 9 are oriented in the pilot control valve 1.4 in a manner rotated by 90 ° in relation to the remaining valves 1.1,1.2, 1.3.

List of reference numerals

1 reversing valve

2 valve body

3 valve space

4 control piston

5 first longitudinal section

6 second longitudinal section

7 third longitudinal section

8 helical spring

9 annular groove

10 ring groove

11 annular groove

12 peripheral surface

13 groove bottom

14 through opening

15 actuator

16 shell hole

17 casing

18 connecting channel or pump connection

19 connecting channel or pump connection

20 relief hole

21 pore wall

22 wall opening

23 wall opening

24 peripheral surface

25 peripheral surface

26 into the opening

27 into the opening

28 ring edge

29 circular edge

30 fluid passage or tank connection

31 bottom part

32 helical spring

33 Clutch Unit

34 Hydraulic pump

35 Motor

36 case body

37 filter

38 connecting channel or working connection

39 connecting channel or working connection

d diameter

Distance A

E plane

L central axis

P pitch

X valve axis.

Claims

1. A valve assembly with:

at least one directional control valve (1) having a control piston (4) which is arranged in a valve space (3) of the at least one directional control valve (1) so as to be movable along a valve axis (X), wherein the at least one directional control valve (1) has at least two annular grooves (9,10,11) which are arranged axially offset from one another and which are in liquid-conducting connection with the valve space (3); and

at least one connecting channel (18,19,38,39), wherein the at least one connecting channel (18,19,38,39) opens into one of the annular grooves (9,10,11) of the at least one switching valve (1) via one opening (26,27), and wherein the at least one connecting channel (18,19,38,39) has a central axis (L)₁₈,L₁₉,L₃₈,L₃₉) Said central axis extending in a non-planar manner with respect to said valve axis (X); and is

Wherein the diameter (d) of the circumferential surface (24,25) of the at least one coupling channel (18,19,38,39) is₁₈,d₁₉) And the axial extension of the respective annular groove (9,10) is in a ratio of 2:1 to 1: 1.

2. Valve assembly according to claim 1, characterized in that the at least one reversing valve (1) has a valve body (2) which delimits the valve space (3), wherein the valve body (2) has at least two of the annular grooves (9,10,11) of the at least one reversing valve (1).

3. Valve assembly according to claim 1 or 2, characterized in that the central axis (L) of the at least one coupling channel (18,19,38,39)₁₈,L₁₉,L₃₈,L₃₉) Outside the valve space (3) of the at least one reversing valve (1).

4. Valve assembly according to any one of claims 1 to 3, characterized in that the central axis (L) of the at least one coupling channel (18,19,38,39)₁₈,L₁₉,L₃₈,L₃₉) Outside the radially outer circumferential surface (12) of the at least one directional control valve (1).

5. A valve assembly according to any one of claims 1 to 4, characterized in that the annular groove (9,10,11) of the at least one reversing valve (1) is configured open towards the radially outer circumferential surface (12) of the at least one reversing valve (1).

6. Valve assembly according to claim 4 or 5, in which the central axis (L) of the at least one coupling channel (18,19,38,39) is₁₈,L₁₉,L₃₈,L₃₉) A minimum distance (A1; A2) is larger than the inner radius (r) of the at least one connecting channel (18,19,38,39)₁₈，r₁₉) Is smaller than 0.5 times and/or is smaller than the inner radius (r) of the at least one coupling channel (18,19,38,39)₁₈，r₁₉) 1 times of the total weight of the composition.

7. Valve assembly according to one of claims 1 to 6, characterized in that there is a housing (17) with at least one housing bore (16) in which the at least one directional control valve (1) is received, wherein the at least one coupling channel (18,19,38,39) is preferably configured in the housing (17).

8. Valve assembly according to claim 7, wherein the housing (17) consists of a cast material.

9. Valve assembly according to claim 7 or 8, characterized in that the at least one housing bore (16) is limited by a bore wall (21), wherein at least one wall opening (22,23) of the at least one coupling channel (17,18,38,39) is arranged in the bore wall (21), wherein the at least one wall opening (22,23) of the at least one coupling channel (17,18,38,39) is formed by the intersection curve of a channel wall (24,25) of the at least one coupling channel (18,19) with the bore wall (21).

10. Valve assembly according to one of claims 1 to 9, characterized in that the at least one coupling channel (18,19,38,39) comprises at least one first coupling channel (18,19) which opens into a first annular groove (9) of the at least two annular grooves (9,10,11) arranged axially offset from one another and at least one second coupling channel (38,39) which opens into a second annular groove (10) of the at least two annular grooves (9,10,11) arranged axially offset from one another.

11. Valve assembly according to claim 10, characterized in that the centre axis (L) of the at least one first coupling channel (18,19)₁₈,L₁₉) Is arranged in a first plane (E) and the central axis (L) of the at least one second connecting channel (38,39)₃₈,L₃₉) Is arranged in a second plane (E '), wherein the valve axis (X) extends perpendicular to the plane (E, E').

12. Valve assembly according to claim 10 or 11, characterized in that the centre axis (L) of the at least one first coupling channel (18,19)₁₈,L₁₉) The central axis (L) relative to the at least one second connecting channel (38,39)₃₈,L₃₉) Along the surroundingThe circumferential directions of the valve axes (X) are arranged offset by, in particular, 90 degrees with respect to one another.

13. Valve assembly according to claim 10 or 11, wherein one first connecting channel (18;19) opens into the first annular groove (9) and one second connecting channel opens into the second annular groove (10), wherein the center axis (L) of the first connecting channel (18;19)₁₈；L₁₉) Arranged parallel to the central axis of the second coupling channel.

14. Valve assembly according to one of claims 10 to 12, characterized in that two of the first connecting channels (18,19) open into the first annular groove (9) and two of the second connecting channels (38,39) open into the second annular groove (10), wherein the center axes (L) of the two first connecting channels (18,19)₁₈,L₁₉) Are parallel to each other, and wherein the middle axes (L) of the two second coupling channels (38,39)₃₈,L₃₉) Parallel to each other.

15. A clutch device with:

a dual clutch assembly consisting of two clutch units (33) which are designed as force-fitting clutches for variably distributing the torque to the left and right drive shafts; and

a valve assembly designed according to any one of claims 1 to 14;

wherein the valve assembly has at least two of the directional valves (1.1,1.2) which are connected in a fluid-conducting manner on the input side to a pump (34) for a working medium and on the output side to one of the clutch units (33).