CN107965484B

CN107965484B - Valve and hydraulic control device with such a valve

Info

Publication number: CN107965484B
Application number: CN201710905045.7A
Authority: CN
Inventors: F·P·布雷斯赫尔; M·G·维特
Original assignee: BorgWarner Inc
Current assignee: BorgWarner Inc
Priority date: 2016-10-19
Filing date: 2017-09-28
Publication date: 2021-03-23
Anticipated expiration: 2037-09-28
Also published as: DE102016012472A1; CN107965484A; KR20180043168A

Abstract

The invention relates to a valve having a valve housing, an inlet pressure chamber for applying an inlet pressure, an outlet pressure chamber for applying an outlet pressure, a first blocking element which is displaceable in the longitudinal direction between the inlet pressure chamber and the outlet pressure chamber, a passage which extends in the longitudinal direction and connects the inlet pressure chamber and the outlet pressure chamber, and a second blocking element which is assigned to the inlet pressure chamber and is opposite the first blocking element, the first closing element is designed such that it is moved by the outlet pressure from an open position, in which it is spaced apart from the second closing element by a distance when the through-channel forms a fluid connection between the inlet pressure chamber and the outlet pressure chamber, into a closed position, in which the second closing element bears against the valve seat of the first closing element when the through-channel is closed. The invention also relates to a hydraulic control device having such a valve.

Description

Valve and hydraulic control device with such a valve

Technical Field

The invention relates to a valve for a clutch device and a hydraulic control device having such a valve.

Background

A hydraulic control for a dual clutch device is known from DE 102013012538 a 1. In each case one shut-off valve is provided in each of the two lines of the actuator of the hydraulic control device, by means of which the output pressure acting on the respective actuator can be maintained even if the input pressure of the shut-off valve decreases. The blocking process of one of the shut-off valves can be released by applying pressure via the supply pressure of the other shut-off valve.

Disclosure of Invention

The object of the invention is to create a shut-off valve or a valve for a hydraulic control device of a clutch device, which has a particularly compact and simple construction and can reliably ensure shut-off or closing. The object of the invention is also to provide a hydraulic control device with such an advantageous valve, which has particularly low leakage losses.

This object is achieved by a valve and a hydraulic control device. The valve has a valve housing, an inlet pressure chamber, which can be acted upon by an inlet pressure, an outlet pressure chamber, which can be acted upon by an outlet pressure, a first blocking element, which is displaceable in the longitudinal direction of the valve between the inlet pressure chamber and the outlet pressure chamber and has a longitudinal passage for connecting the inlet pressure chamber and the outlet pressure chamber, and a second blocking element, which is assigned to the inlet pressure chamber and is opposite the first blocking element, the effective piston surface of the first blocking element facing the outlet pressure chamber being greater than the effective piston surface of the first blocking element facing the inlet pressure chamber, so that the first blocking element can be displaced by the outlet pressure from an open position, in which the first blocking element is at a distance from the second blocking element via the passage for fluid connection between the inlet pressure chamber and the outlet pressure chamber, into a closed position In the closed position, the second blocking element bears against a valve seat of the first blocking element with the through-passage closed, wherein the valve seat encloses an inlet of the through-passage facing the inlet pressure chamber. The hydraulic control for the clutch device has at least one valve according to the invention, wherein the at least one valve is connected behind the second line section or is integrated into the second line section. Advantageous embodiments of the invention are described below.

The valve according to the invention has a valve housing. An inlet pressure chamber is provided in the valve housing, to which inlet pressure can be applied, for which purpose, for example, an inlet or inlet opening is provided in the valve housing, which inlet opening is connected to the inlet pressure chamber. Furthermore, an output pressure chamber is provided in the valve housing, from which an output pressure can be output, which is supplied, for example, to a control actuator of the clutch device, for which purpose an output or output opening can be provided in the valve housing, through which the output pressure is supplied. The valve also has a first blocking element, also referred to as a first blocking piston, which is movable in the longitudinal direction of the valve. The first blocking element is arranged between the outlet pressure chamber and the outlet pressure chamber of the valve housing. The first blocking element does not completely separate the inlet pressure chamber from the outlet pressure chamber, but rather has a channel running through it in the longitudinal direction, which serves to connect the outlet pressure chamber to the outlet pressure chamber, at least in the open position of the first blocking element. The longitudinal through-channel preferably means a central or central through-channel. Furthermore, the inlet pressure chamber is assigned not only a first blocking element, but also a second blocking element, which is arranged opposite the first blocking element. In this way, both the first and the second closing member can exert an input pressure in the input pressure chamber, for which purpose the second closing member is also referred to as a second closing piston, depending on the selected embodiment variant. The first closing element is designed such that it is moved by the outlet pressure of the outlet pressure chamber from an open position (in which the first closing element is spaced apart from the second closing element by a distance while forming a fluid connection between the inlet pressure chamber and the outlet pressure chamber via the through-channel) into a closed position (in which the second closing element bears against the valve seat of the first closing element while the through-channel is closed). The effective piston surface of the first blocking element facing the output pressure chamber is preferably larger than the effective piston surface of the first blocking element facing the input pressure chamber, so that the first blocking element is moved into the closed position as a function of the pressure by the output pressure being built up in the output pressure chamber in the open position of the first blocking element, whereby the output pressure can be maintained without the input pressure being maintained. The advantage of this valve is that, by virtue of the displaceable first blocking element and the through-passage, a relatively simple and compact valve structure is formed, so that not only can its production process be simplified, but it can also be arranged in a space-saving and flexible manner inside the hydraulic control device.

In order to lock the valve in the closed position of the first closing member as leak-free and reliable as possible, in a preferred embodiment the second closing member is arranged in the interior of the valve housing in a displaceable or gapped manner in the transverse direction, i.e. transversely to the longitudinal direction of the valve. This has the advantage that possible manufacturing tolerances of the valve seat of the first closing element can be compensated for in a particularly simple and reliable manner, on the one hand, for the second closing element and, on the other hand, for the first closing element. The advantage is also that the first blocking element is guided in the longitudinal direction in the valve housing by a guide which is as free as possible from play, while the second blocking element which is displaced in the transverse direction or has play can thus be reliably aligned in line with the first blocking element or the passage of the first blocking element.

In an advantageous embodiment according to the invention, the second closing element is supported in a laterally resilient manner on the valve housing. For the purpose of elastic support, special spring elements can be used here, but the inlet pressure chamber can also be sealed by means of an elastic sealing ring, the sealing method of which will be explained in more detail below.

In a further preferred embodiment of the valve according to the invention, the second blocking element is inclined relative to the longitudinal axis of the valve, if necessary relative to the longitudinal axis of the first blocking element. This ensures a particularly secure closing of the valve in its closed position, while the second closing member can be brought into a particularly secure contact with the valve seat of the first closing member even if there are major manufacturing tolerances or the first and second closing members cannot be precisely aligned.

In order to ensure a particularly simple construction of the valve, and at the same time to ensure lateral displaceability and/or tiltability of the second blocking element relative to the longitudinal axis of the valve, in a particularly preferred embodiment of the valve according to the invention the second blocking element is displaceable in the longitudinal direction. This makes it possible to install the second closing element in the valve housing relatively simply, and furthermore, to implement the safety function in the event of a pressure drop, pressure loss or pressure loss, which is explained in more detail below.

In a further advantageous embodiment of the valve according to the invention, the second blocking element, which is movable in the longitudinal direction, can be supported on its side remote from the first blocking element or on a support element. It is thereby ensured that the second blocking element, although it can be displaced in the longitudinal direction, when it is supported, makes it possible for the longitudinally displaceable first blocking element to reach its closed position, in which the second blocking element bears against the valve seat of the first blocking element when the through-passage is closed.

In principle, the mutually opposite support surfaces of the support part and the second blocking part can be arranged parallel to one another and/or form a plane, and the support surface of the second blocking part can be supported completely on the support surface of the support part. In order to achieve the above-described inclination and/or transverse displaceability relative to the longitudinal axis of the valve, the mutually opposing bearing surfaces of the support and the second blocking element are designed such that the second blocking element supported on the support can be inclined relative to the longitudinal axis of the valve. In this way, one of the bearing surfaces rolls, for example, on the other bearing surface when the second blocking element is tilted. Thus, for example, two bearing surfaces of the support part and the second blocking part which are arranged completely parallel to one another can be avoided. In this embodiment, it is preferred that the support surface of the second blocking element is arched and/or crowned in the direction of the support element. Alternatively or additionally, the support surface of the support element can be arched and/or crowned in the direction of the second blocking element.

In a particularly advantageous embodiment of the valve according to the invention, the support element is moved from a first end position in which the second blocking element is supported on the support element and moves the first blocking element into the open and closed position to a second end position in which the second blocking element is supported on the support element and does not move the first blocking element into the closed position. The latter can, for example, ensure that the first blocking element is no longer moved as far as possible in the direction of the second blocking element in order to approach the second blocking element and to cause the second blocking element to close the passage of the first blocking element. At the same time, a safety function can be achieved by means of the support element moving between the two end positions, which safety function can open the valve itself when there is no sufficiently high pressure as a result of a pressure drop, pressure loss or pressure deficit, in order to reopen the valve by means of this pressure.

In a further advantageous embodiment of the valve according to the invention based on the above-described embodiment, a stop is provided at which the first blocking element is supported at a distance from the second blocking element supported in the second end position of the support element. Such a stop element projects outwardly, for example, on the first closure element, in order to be able to be supported in the longitudinal direction on a step of the valve housing.

In order to automatically implement the safety function in the event of a pressure drop or pressure loss, in a further particularly preferred embodiment of the valve according to the invention, a fastening pressure chamber is assigned to the support element, which fastening pressure chamber serves to fasten the support element in the first end position by applying the input pressure, for which purpose the support element is moved from the first end position into the second end position when the value of the input pressure is less than a defined lower limit value of the input pressure. It is therefore no longer necessary to specifically control the support element by means of an additional, if necessary electrical control device, but instead the support element (also referred to as support piston) is moved from the second end position into the second end position by a loss or drop in the supply pressure in order to open the valve.

In a further preferred embodiment of the valve according to the invention, the first closing member is pretensioned in its open position. In this case, it is preferred if a spring device is provided for pretensioning in the open position. The spring device may comprise one or more spring elements, for which preferably at least one helical compression spring is provided. In this embodiment, it is preferred that the spring device (if appropriate a helical spring) is supported on one side on the first closing element and on the other side on the second closing element in order to hold the second closing element, if appropriate, in a snug manner on the support element and in such a way that, in the open position, the first closing element and the second closing element are spaced apart from one another.

In a further advantageous embodiment of the valve according to the invention, the second closing element is supported or connected to the valve housing in a manner sealing the inlet pressure chamber. Preferably, the sealing is effected by means of an intermediate sealing ring or an annular sealing ring. In order to achieve the above-described displaceability of the two blocking elements in the transverse direction, it is preferred in this embodiment to provide the intermediate sealing ring or the annular sealing ring with a plastic or elastic construction.

In order to ensure a secure closure of the valve in the closed position of the first closing member, the second closing member has a projection extending in the longitudinal direction for abutting against the valve seat. In contrast, the projecting projection may be annular or may be a central flange. For this embodiment, the longitudinally projecting collar is preferably of conical or spherical crown shape. For an annular flange, its conical or spherical crown-like structure may constitute the area enclosed by the ring, whereas for a centrally projecting flange, its flange itself is conical or spherical crown-like.

In principle, the valve seat can be circumferential, with an angled edge forming the inlet of the through-passage to the inlet pressure chamber. In a further advantageous embodiment of the valve according to the invention, the valve seat is conical or spherical. Alternatively or additionally, the valve seat encloses the through-passage inlet opening facing the inlet pressure chamber.

In order to move the first closing member from the closed position, which blocks the outlet pressure, into the open position again, in a further advantageous embodiment of the valve according to the invention, an opening pressure chamber is assigned to the first closing member. The opening pressure chamber may apply an opening pressure during sliding of the first latch from the closed position to the open position. In this case, the opening pressure chamber is preferably formed by an annular chamber between the first closing element and the valve housing. In addition, it is advantageous if the opening pressure chamber is arranged between the valve housing, to which the first closing element is guided in a sliding manner, and the sealing ring between the first closing element and the valve housing.

In a further preferred embodiment of the valve according to the invention, the first blocking element is slid from the open position into the closed position only when the value of the output pressure exceeds a predetermined upper limit value of the output pressure. The predetermined upper limit value of the output pressure is predetermined, for example, primarily by the spring device described above for pretensioning the blocking element in the open position and/or the effective piston surface (also referred to as pressure application surface or working surface) of the first blocking element.

In accordance with a further advantageous embodiment of the valve according to the invention, the value of the inlet pressure of the first closing member in the closed position, while maintaining the closed position, falls below the value of the outlet pressure, preferably to the above-mentioned predetermined lower limit value of the inlet pressure.

The hydraulic control device of the clutch device according to the invention has at least one valve according to the invention. In this respect, it is preferred that the hydraulic control device is designed for a dual clutch device having two clutches. In addition, in the present embodiment, it is preferable that the clutch device or the dual clutch device is designed as a multiple disk clutch device or a dual multiple disk clutch device.

In an advantageous embodiment of the control device according to the invention, the control device has a pressure supply for supplying at least one valve inlet pressure. The control device also has a first line section connected to the pressure supply, which line section is connected to one of the two line sections via a swivel joint, wherein the two line sections and the swivel joint are used to transmit hydraulic fluid. In this case, the at least one valve is arranged such that it is located behind the second line section or is integrated in the second line section. This has the advantage that the output pressure which is maintained in the closed position of the first blocking element does not act in the region of the swivel joint which has a high leakage. Instead, the already reduced or reducible inlet pressure acts on the swivel joint region in order to avoid major leakage losses. Furthermore, in this embodiment, the first pipe section is preferably of fixed design, for example arranged in a fixed housing, while the second pipe section is rotatable relative to the first pipe section, for example by arranging it in a rotatable component, for example a clutch hub or the like. The compact design of the valve has the advantage that, in particular, a space-saving design can be realized in the rotating part (for example, in the clutch hub). In this embodiment, it is preferred that at least one valve has a structure that can rotate with the second line section.

In a particularly preferred embodiment of the control device according to the invention, the control device has a first valve and a second valve according to the invention. In this case, a first input pressure is applied to the input pressure chamber of the first valve, a second input pressure is applied to the input pressure chamber of the second valve, and the first output pressure is reduced in the output pressure chamber of the first valve and the second output pressure is reduced in the output pressure chamber of the second valve, so that a dual clutch device or the like can be operated thereby. In this embodiment, the control device preferably also has a first actuator for the first clutch, which actuator is controlled by the first output pressure, and a second actuator for the second clutch, which actuator is controlled by the second output pressure. The actuators may be, for example, piston-cylinder arrangements in which cylinders are applied with respective output pressures in order to move the pistons of the respective actuators.

In a particularly advantageous embodiment of the control device according to the invention based on the above-described embodiment, the opening pressure chamber of the first valve is supplied with the second input pressure and the opening pressure chamber of the second valve with the first input pressure if, for example, the clutch is alternately closed or opened, in order to achieve a uniform transition between the first output pressure and the second output pressure during the setting.

In order to provide a particularly compact design of the control device and a simple production process, in a further preferred embodiment of the control device according to the invention at least one valve is inserted into a longitudinal bore (optionally a blind bore) of the hub. Where the hub is tubular, it is preferred that the at least one valve is inserted into a longitudinal bore in the wall of the tubular hub. In this case, the longitudinal bore can also be a blind bore, into which the necessary conduits for supplying hydraulic fluid are connected. In this embodiment, the longitudinal bore is preferably closed by means of a seal, for which only one seal is required if the longitudinal bore is formed by a blind bore. For maintenance reasons, it is furthermore preferred to make the seal detachable, i.e. connected to the hub or the tubular hub by a detachable fastening means.

Drawings

The invention is explained in more detail below with reference to the drawing according to an exemplary embodiment. Wherein:

figure 1 shows a schematic view of an embodiment of the hydraulic control device according to the invention,

FIG. 2 shows a side view of a first valve of the schematic drawing of the control device from FIG. 1, with the first blocking element in the open position and the support element in the first end position,

FIG. 3 shows the valve of FIG. 2, with the first blocking member in the closed position and the support member in the first end position,

fig. 4 shows the valve of fig. 2 with the blocking member in the open position and the support member in the second end position.

Detailed Description

Fig. 1 shows an embodiment of a hydraulic control device 2 for a clutch device, in particular for a dual clutch device. The double clutch device, which is not shown in detail, is preferably formed by a double multiplate clutch device, whereas the double multiplate clutch device is preferably a wet double multiplate clutch device.

In general, the control device 2 essentially comprises a pressure supply device 4 which supplies an input pressure which is described in more detail below, a first line section 6 which is connected to the pressure supply device 4, a second line section 8 which is located downstream of the first line section 6 and is in fluid connection with the first line section via a swivel joint 10, a first actuator 12 which is located downstream of the second line section 8, and a second actuator 14 which is located downstream of the second line section 8, wherein the first actuator 12 is assigned to a first clutch of a double clutch device which is not shown in more detail here, and the second actuator 14 is assigned to a second clutch of a double clutch device which is not shown in more detail here.

As with the pressure supply 4, the first pipe section 6 is of fixed construction, for which purpose the first pipe section 6 is built into the stationary housing 6 (fig. 2). In contrast, the second pipe 8 is rotatable relative to the first pipe segment 6 by at least partially embedding the second pipe segment in the hub (here the clutch hub 18).

Furthermore, the control device 2 has a first valve 20 and a second valve 22, for which both valves are either located behind the second line section 8, so that they are arranged between the second line section 8 and the

actuator

12 or 14, or, as shown in fig. 1, both valves are built into the second line section 8. At the same time, both valves rotate with the second pipe section 8 or the clutch hub 18. In order to simplify the construction of the control device 2, the two valves are each inserted into a longitudinal bore 24 of the clutch hub 18, more precisely into a hub wall 26 of the clutch hub 18 of tubular construction, as shown in fig. 2 for the first valve 20 example. Furthermore, as shown in fig. 2, the blind-hole-shaped longitudinal bore 24 is closed at its open end by a seal 28, which is preferably detachably fastened to the clutch hub 18.

The first actuator 12 and the second actuator 14 are each a simple piston-cylinder arrangement consisting of a

cylinder

30, 32 and a

piston

34, 36 slidably arranged in the

cylinder

30, 32. The

pistons

34, 36 are each assigned a

return spring

38, 40, the return springs 38, 40 causing the first actuator 12 and the second actuator 14 to be opened or moved in the pressureless state into an open position in which a first clutch, not shown in detail here, and a second clutch, not shown in detail here, are opened.

The

piston

34 or 36 can be acted upon by a hydraulic first output pressure a against the force of a

return spring

38 or 40₁Or hydraulic second output pressure A₂Moving to the closed position. For this purpose, the first actuator 12 or the second actuator 14 is connected via

lines

42, 44 which are connected on one side to the

input

46 or 48 of the first or

second actuator

12 or 14 and on the other side to the

outputs

50, 52 of the first valve 20 or the second valve 22. The structure of the first and

second valves

20, 22 is described in more detail subsequently with reference to fig. 2 to 4. At a distance from the pipeline42 or 44, the two

inputs

54, 56 or 58, 60 of the first or

second valve

20, 22 are connected to a

line

62 or 64, respectively, which extends via the two line sections 8, the swivel joint 10 and the first line section 6 to a first or second proportional valve 66 or 68 of the pressure supply device 4.

The two proportional valves 66, 68 each have an input 70 or 72, an output 74 or 76 (to which the

line

62 or 64 is connected) and a

second output

78 or 80, to which the

second outputs

78, 80 are respectively assigned or connected to an open hydraulic fluid container 82. The two proportional valves 66, 68 are each formed by an electromagnetically controlled solenoid valve with a variable actuating force. The proportional valves 66, 68 each have an electromagnet, and the proportional valve 66 or 68 is regulated by the magnetic flux of the electromagnet. The adjusting force of the solenoid acts counter to the restoring force of the spring elements of the respective proportional valve 66, 68, for which purpose the first proportional valve 66 and the second proportional valve 68 are pretensioned by means of associated spring elements into a closed position, in which the flow of the input 70 or 72 and the

output

74 or 76 of the respective proportional valve 66, 68 is blocked. In addition, the

second output

78 or 80 of the respective proportional valve 66, 68 is in fluid connection with the

first output

74 or 76 of the respective proportional valve 66, 68 in the closed position described above. The proportional valve 66 can thus be controlled by the magnetic flux of the associated electromagnet, by means of which solenoid valves 66, 68 more or less can be adjusted to the open position.

The hydraulic first input pressure E, regulated by the first proportional valve 66, is reduced at the output 74 of the first proportional valve 66 via the line 62₁While the hydraulic second input pressure E, regulated by a second proportional valve 68, is reduced via the line 64₂. The first valve 20 is arranged between the line 42 and the line 62 in such a way that, if the first valve or its first blocking element, which is described in more detail below, is moved into the closed position, the flow from the line 42 to the line 62 is blocked or the flow from the input 46 of the first actuator 12 to the output 7 of the first proportional valve 66 is prevented. More specifically, the first valve 20 blocks flow from its input 50 to its

inputs

54, 56. In a corresponding manner, the second valve 22 is arranged inBetween line 44 and line 64, it is also provided that if second valve 22 or its first blocking element, described in greater detail below, is moved into the closed position, this second valve blocks the flow of line 44 in the direction of line 64 or the flow of input 48 of second actuator 14 to output 76 of second proportional valve 68. More specifically, if the second valve or its first blocking element, described in more detail below, is moved to the closed position, the flow from the output 52 to the

inputs

58, 60 of the second valve 22 is blocked. It should also be noted that a filter (no reference numeral) is mounted in each of the

conduits

62, 74.

At the input 70 of the first proportional valve 66 and at the input 72 of the second proportional valve 68, there is a hydraulic main pressure P, which is also referred to as the system pressure. For this purpose, the inputs 70, 72 are connected to lines 84, 86, respectively, which are connected together on their side remote from the respective proportional valve 66 or 68 to a line connection 88, for which a filter (without reference numeral) is arranged in the lines 84, 86, respectively. The hydraulic main pressure P at the inputs 70, 72 is generated by a hydraulic pump 90 attached to the pipe connection 88, which hydraulic pump delivers hydraulic liquid from a hydraulic liquid container 92 via a filter (no reference numeral). In order to avoid inadmissibly high excess pressures at the inputs 70, 72 or to limit the hydraulic main pressure P, an overpressure valve 94 is provided, which is formed here by a spring-loaded check valve and is assigned to the line connection 88. On its side remote from the pipe connection point 88, the excess pressure valve 94 is connected to a hydraulic fluid reservoir 96.

The first valve 20 can be supplied with a second supply pressure E₂Is unblocked and the second valve 22 is acted upon by the first input pressure E₁The cutoff is released. For this purpose, a first control line 98 is provided, which is connected to a line connection point 100 of the line 64 and at the same time to a control input 102 of the first valve 20; furthermore, a second control line 104 is provided, which is connected to a line connection point 106 of the line 62 and to a control input 108 of the second valve 22. In this connection, the first valve 20 applies a second supply pressure E2 via the first control line 98 and the second valve 22 via the second control line 98The second control conduit 104 applies a first input pressure E1. It should be noted that in principle, a choke valve or the like can also be provided in the

control lines

98, 104 in order to reduce the second or first inlet pressure E, which releases the blocking of the first or

second valve

20 or 22₂Or E₁。

In the following, the construction of the two valves and their connection in the hydraulic control device 2 is explained in more detail with reference to fig. 2 by way of example for the first valve 20, for which purpose the embodiment of the first valve 20 is also applicable in a corresponding or similar manner to the second valve 22.

In fig. 2, the

axial directions

110, 112 of the double clutch devices, which are controlled by the control device 2 and of which only the clutch hub 18 is shown in fig. 2, the

radial directions

114, 116 of the double clutch devices, and the

circumferential directions

118, 120 of the double clutch devices, which are opposite one another, are indicated by corresponding arrows, and furthermore, the rotational axes of the double clutch devices, which extend in the

axial directions

110, 112, are also shown in fig. 2.

The first valve 20 extends in mutually opposite

longitudinal directions

124, 126, for which purpose a longitudinal axis 128 of the first valve 20 extending in the

longitudinal directions

124, 126 is parallel to the rotational axis 122 of the dual clutch device. The first valve 20 has a substantially tubular valve housing 130 and a first longitudinal section 132, a second longitudinal section 134 located behind the longitudinal section 132 in the longitudinal direction 124, and a third longitudinal section 136 located behind the second longitudinal section 134 in the longitudinal direction 124, the second longitudinal section 134 having a smaller inner diameter than the first and third longitudinal sections 132, 236, also referred to as a guide section 134. An input 54 in the form of an input opening is provided in the first longitudinal section 132, and both an output 50 in the form of an output opening and a control input 102 in the form of a control input opening are provided in the third longitudinal section 136.

The input end 54 is connected to an input pressure chamber 138, which is thereby subjected to a first input pressure E₁. Furthermore, an outlet pressure chamber 140 is provided in the valve housing 130, from which the first outlet pressure a of the first actuator 12 is reduced via the outlet 50₁. In the valve housing 130, a first closing element 142, also referred to as a "closing element", is furthermore providedA first lockout piston. A first essentially tubular blocking element 142 is arranged in the

longitudinal direction

124, 126 between the inlet pressure chamber 138 and the outlet pressure chamber 140, for which purpose the first blocking element 142 is moved in the

longitudinal direction

124, 126 over the second longitudinal section 134 of the valve housing 130. At the same time, the first blocking element 142 also has a conduit 144 running through the

longitudinal directions

124, 126, which, at least in the open position of the first blocking element 142 shown in fig. 2, serves to establish a fluid connection between the inlet pressure chamber 138 and the outlet pressure chamber 140. Furthermore, the first blocking element 142 is displaced transversely to the

longitudinal direction

124, 126 in the second longitudinal section 134 of the valve housing 130 as far as possible without play, which is preferably such that the clearance of the first blocking element transversely to the second longitudinal section 134 is at least smaller than the clearance of the second blocking element in the transverse direction, which is explained below. The first blocking element 142 has a laterally projecting stop 146, which (described in more detail below) is supported in the longitudinal direction 126 at the end of the second longitudinal section 134 facing the longitudinal direction 124, the stop 146 being a tubular structure in the embodiment shown.

Furthermore, in the third longitudinal section 136 of the valve housing 130, a tubular opening pressure chamber 148 is provided, which is adjacent to the first blocking element 142, to the outside, to the valve housing 130, to the ends of the longitudinal section 126 and the second longitudinal section 134, and to an outwardly projecting first projection 150 in the longitudinal direction 124 and on the first blocking element 142, for which purpose the first projection 150 is also of tubular design, and has a recess for the inner seal 52, wherein the seal 152 seals the opening pressure chamber 148 against the outlet pressure chamber 140. The opening pressure chamber 148 is assigned a control input 102, so that a second input pressure E in the form of a pressure is applied to the opening pressure chamber 148₂The opening pressure of (a).

In addition, a second blocking element 154 is arranged in the first longitudinal section 132 of the valve housing 130, which second blocking element belongs to the inlet pressure chamber 138. The second latch member 154 is arranged relative to the first latch member 142 along the longitudinal direction 126. The second blocking element 154 is arranged in the valve housing 130 in a slidable manner in the

longitudinal directions

124, 126, for which purpose the second blocking element 154 is supported on a support 156, which is explained in more detail below, on its side remote from the first blocking element 142, i.e. in the longitudinal direction 126. Thus, the second latch member 154 has a base section 158 that extends substantially to the envelope-like inner wall of the valve housing 130. A central second projection 160 extending in the longitudinal direction 124 is provided on the base section 158, for which purpose the second projection 160 is conical or, as shown in fig. 2, has a spherical cap shape extending in the direction of the first blocking element 142. Furthermore, the second blocking element 154 is arranged in the first longitudinal section 142 of the valve housing 130 in a laterally displaceable or gapped manner, wherein the second blocking element 154 is supported resiliently in the lateral direction on the valve housing 130. At the same time, the base section 158 of the second blocking element 154 on its side pointing outward toward the first longitudinal section 132 is designed such that the second blocking element 154 is inclined relative to the longitudinal axis 128 of the first valve 20 and relative to the longitudinal axis of the first blocking element 142, differently from the base direction according to fig. 2. In order to achieve a sealing of the inlet pressure chamber 138 on the one hand and a transverse elastic arrangement of the second blocking element 154 in the valve housing 130 on the other hand, the blocking element 154 or its base section 158 is supported on the first longitudinal section 132 of the valve housing 130 by means of an intermediate plastic or elastic sealing ring or annular sealing ring 162.

The oppositely directed support surfaces 164, 166 of the support 157 and the second blocking member 154 in the

longitudinal direction

110, 112 are designed or arranged such that they are not or are not completely parallel to one another, but rather are designed such that the second blocking member 154 supported on the support 156 is inclined relative to the longitudinal axis of the first valve 20 and relative to the longitudinal axis of the first blocking member 142. It is thereby possible, for example, for the

support surface

164 or 166 to roll on its

support surface

166 or 164 in order to reach the desired tilting position. In the embodiment shown, the support surface 166 of the second blocking element 154 is arched or arched forward and/or crowned in the direction of the support element 156, while the support surface 164 is a plane that is not curved or arched. In principle, the shape of the support surfaces 164, 166 can also be reversed. Furthermore, in principle, both support surfaces 164, 166 can be designed in the form of an arch, a forward arch and/or a spherical crown.

Thus, the input pressure chamber 138 is oriented in the longitudinal direction 124Essentially adjacent to the valve housing 130 and the first blocking element 142, the second blocking element 154 and the first longitudinal section 132 of the valve housing 130 in the longitudinal direction 126 and in the transverse direction, for which purpose the input pressure chamber 138 can apply an input pressure E via the input 54₁. Furthermore, a spring device 168, which in the above-described embodiment is formed by a helical spring or a helical compression spring, is arranged in the inlet pressure chamber 138 and serves to pretension the first blocking element 142 in the open position shown in fig. 2. In this case, the spring device 168 is supported in the longitudinal direction 126 on the base section 158 of the second blocking part 154, wherein the projecting second projection 160 extends in the longitudinal direction 124 in the spring interior region of the helical spring or of the helical compression spring of the spring device 168, while the spring device 168 is supported in the longitudinal direction 124 on the first blocking part 142. Furthermore, the spring arrangement 168, when supported on the first blocking element 142, is such that a section of the first blocking element 142 extends in the longitudinal direction 112 in the spring interior region of the helical spring or of the helical compression spring. At the same time, the spring device 168 serves, on the one hand, to pretension the second blocking element 154 in the longitudinal direction 126 on the support element 156 and, on the other hand, to pretension the first blocking element 142 in the longitudinal direction 124 in order to force it into the open position.

The first blocking element 142 is designed such that it passes the outlet pressure a₁From the open position according to fig. 2, in which the first blocking element is spaced apart by the through-channel 144 and the second blocking element 154 with the fluid connection between the inlet pressure chamber 138 and the outlet pressure chamber 140, to the closed position according to fig. 3, in which the second blocking element 154 bears against the valve seat 170 of the first blocking element 142 with the through-channel 144 closed. More precisely, the second projecting projection 160 bears against a valve seat 170 of the first blocking element 142 in the closed position of the first blocking element 142 according to fig. 3, for which purpose the valve seat 170 encloses an inlet 172 of the through-channel 144 facing the inlet pressure chamber 138 and is conical or spherical in shape. Furthermore, in the closed position (fig. 3), the protruding second protrusion 160 extends at least partially into the through-passage 144 in the longitudinal direction 124.

Before explaining the working principle of the first valve 20 in detailThe support member 156 and its peripheral region will first be described in detail below. The support 156 is essentially formed by a piston which is movable in the

longitudinal direction

124, 126, the aforementioned support 164 of which faces the second blocking member 154 so as to be supportable on the second blocking member 154. In the longitudinal direction 126, the side 174 of the support 156 (also referred to as the support piston) faces in the longitudinal direction 126, in contrast, toward a stationary pressure chamber 176, to which a first input pressure E is applied via the above-mentioned input 56₁. Furthermore, as shown in fig. 2, the support member 156 is not arranged in the valve housing 130, but rather is arranged in a movable manner in the longitudinal bore 24 essentially in the clutch hub 18 described above, for which purpose the support member 156 has an outer sealing ring 178 in order to seal the stationary pressure chamber 176 from the surroundings. The support member 156 is movable from a first end position, shown in fig. 2 and in which the support member 156 is supported in the longitudinal direction 124 at the end of the valve housing 130, to a second end position, shown in fig. 4 and in which the support member 156 is supported in the longitudinal direction 126 at the clutch hub 18, here in the longitudinal bore 24 by means of the support ring 180. However, the support 156 can alternatively be arranged in the valve housing 130, can be movable therein, and can be supported in the first end position along the longitudinal direction 124 on, for example, a stop or a step of the valve housing 130.

In addition to the above-described embodiments, it should be noted that the support 156 has an annular first effective piston surface F facing the fixed pressure chamber 176₁The second blocking element 154 has an annular second effective piston surface F facing the inlet pressure chamber 138₂The first blocking element 142 has an annular third effective piston surface F facing the inlet pressure chamber 138₃The first blocking element 142 has an annular fourth effective piston surface F facing the opening pressure chamber 148₄And the first blocking element 142 has an annular fifth effective piston surface F facing the outlet pressure chamber 140₅. For this purpose: f₁ > F₂> F₁ > F₂ > F₃. As described further below, the first lockout member 142 is moved to either the aforementioned closed or open positions due to the pressure in the input pressure chamber 138, the output pressure chamber 140, the opening pressure chamber 148, and the fixed pressure chamber 76, in combination with the force of the spring device 168In position, no other drive means is required to move the first latch 142, the second latch 154, or the support 156. Hereinafter, the operation thereof will be further explained in detail.

The reason for this is that the two

actuators

12 and 14 are initially not controlled, so that the partial clutch, which is usually an open clutch, is opened. It should also be noted that the clutch can also be a normally closed clutch, which can be fixed in the open position by means of a valve or a hydraulic control device 2 using little energy. If the actuator 12 is now actuated to close the first clutch, the first input pressure E is then₁To this end, the inlet pressure chamber 138 and the fixed pressure chamber 176 exert a first inlet pressure E via the line 62 and the

inlet

54 or 56 and the line 62₁. If the first input pressure E₁Reaches the preset lower limit value of the input pressure, the first input pressure E is₁Acts on the fixed pressure chamber 176 and presses the support 156 securely into the first end position shown in fig. 2, in which the second blocking element 154 is supported in the longitudinal direction 126 on the support 156 and allows the first blocking element 142 to be moved both into the open position according to fig. 2 and into the closed position according to fig. 3. By virtue of the first blocking element 142 in the open position according to fig. 2, the inlet pressure chamber 138 is connected to the outlet pressure chamber 140 via a through-channel 144, so that the first inlet pressure E is increased₁The first output pressure A is also simultaneously increased₁The pressure is reduced at the output 42 and the actuator 12 is controlled, while the belonging first clutch is closed.

According to the third and fifth effective piston surfaces F₃And F₅The first output pressure A₁Will cause the first latch 142 to be at the first output pressure A₁Is greater than a predetermined upper limit value of the output pressure, from the open position according to fig. 2 in the longitudinal direction 126 to the closed position according to fig. 3. The displacement process is carried out against the respective first input pressure E due to the input pressure chamber 138₁Combined with the third effective piston face F₃And due to the return force edge of the spring means 168The force of the longitudinal direction 124 on the first latch 142.

If the first blocking element 142 reaches the closed position according to fig. 3, a first input pressure E is provided by the pressure supply device 4₁Is lowered while the closed position remains unchanged. Thus, the first input pressure E₁Falls below the first output pressure A₁To be lower than a predefined lower input pressure limit value, so that the support 156 is subjected to the reduced first input pressure E₁Is securely fixed in the fixed pressure chamber 176 in the first end position according to fig. 2 and 3.

With the above-described embodiment of the first valve 20, not only is a reliable and leak-free closure possible in the region of the first and

second blocking elements

142, 154 possible leakage losses in the region of the rotary joint 10 can be avoided in the control device 2, but also a reduced first inlet pressure E can be provided in the line 62₁。

If the first actuator 12 for opening the subordinate first clutch is disengaged and the second actuator 14 is controlled to close the subordinate second clutch, regardless of the first input pressure E₁Or the second input pressure E₂Need to be improved. At the same time, irrespective of the first input pressure E in the input pressure chamber 138₁Also the opening pressure in the opening pressure chamber 148 rises, which is equal to the second input pressure E₂. The second valve 22 is implemented in the manner described with reference to the first valve 20, the spring force of the spring means 168, the first input pressure E from the input pressure chamber 138₁Combined with the third effective piston face F₃The force developed and the second input pressure E₂Incorporating a fourth effective piston face F in the opening pressure chamber 148₄The force developed and the first blocking element 142 opposing the first output pressure A from the output pressure chamber 140₁Combined with a fifth effective piston face F₅Acts on the first blocking member 142 and moves the first blocking member 142 in the longitudinal direction 124 and brings it into the open position of fig. 2 again.

If a pressure loss or pressure of the pressure supply means 4 occurs due to the closed position in fig. 3The force drops and a first input pressure E is caused₁If the value of (b) is below the predetermined input pressure limit value or even drops to zero, the immovable support 156 has the disadvantage that the first blocking element 142 is continuously held in its closed position according to fig. 1 and the first actuator 12 and the associated first clutch are continuously controlled. To avoid this, the support 156 is moved in the

longitudinal directions

124, 126 in the manner described above. If the first input pressure E of the fixed pressure chamber 176₁Is lower than a predetermined lower limit value of the input pressure, determined by the first input pressure E in the fixed pressure chamber 176₁Combined with the first effective piston face F₁The resulting force acting on the support 156 in the longitudinal direction 124 is insufficient to secure the support 156 in the first end position shown in fig. 3 while in the opposite longitudinal direction 126 due to the first output pressure a in the output pressure chamber 140₁The force acting on the first blocking element 142 is greater than the first output pressure A due to the passage 144₁A force acting on the second latch 154. Thereby, the support 156 is moved in the longitudinal direction 126 towards the second end position according to fig. 4. In the second end position, the second blocking element 154, when supported on the support element 156, is such that the first blocking element 142 is no longer moved into its closed position, while the stop block 146 is supported in the longitudinal direction 126 at the end of the second longitudinal section 134 of the valve housing 130. In other words, if there is a pressure loss or a pressure drop or no pressure at all in the pressure supply 4, a safety function can be achieved in which the first valve 20 opens and thus the first clutch opens.

Finally, it should be noted that the support 156 and the second blocking element 154 can in principle also be formed integrally with one another. However, the lateral tiltability and displaceability of the second blocking element 154 is limited or made difficult by this, so that a two-part construction is preferably used. In the case of a two-part construction, it is preferred that a chamber 182 is provided between the mutually facing support surfaces 164, 166, which chamber is vented or emptied via at least one emptying or venting opening 184.

List of reference numerals

2 control device

4 pressure supply device

6 first pipeline section

8 second pipe section

10 swivel joint

12 first actuator

14 second actuator

16 fixed shell

18 clutch hub

20 first valve

22 second valve

24 longitudinal hole

26 hub wall

28 seal

30 cylinder

32 air cylinder

34 piston

36 piston

38 return spring

40 return spring

42 pipeline

44 pipeline

46 input terminal

48 input terminal

50 output terminal

52 output terminal

54 input terminal

56 input terminal

58 input terminal

60 input terminal

62 pipeline

64 pipeline

66 first proportional valve

68 second proportional valve

70 input terminal

72 input terminal

74 output terminal

76 output terminal

78 second output terminal

80 second output terminal

82 hydraulic fluid container

84 pipeline

86 pipeline

88 pipe connection point

90 hydraulic pump

92 hydraulic fluid container

94 excess pressure valve

96 hydraulic fluid container

98 first control conduit

100 pipe connection point

102 control input

104 second control conduit

106 pipe connection points

108 control input terminal

110 axial direction

112 axial direction

114 radial direction

116 radial direction

118 in the circumferential direction

120 circumferential direction of

122 rotating shaft

124 longitudinal direction

126 longitudinal direction

128 longitudinal axis

130 valve shell

132 first longitudinal segment

134 second longitudinal segment

136 third longitudinal segment

138 input pressure chamber

140 output pressure chamber

142 first latch

144 through passage

146 stop block

148 open the pressure chamber

150 first projection

152 sealing device

154 second latch

156 support piece

158 base segment

160 second projection

162 sealing ring

164 bearing surface

166 bearing surface

168 spring device

170 valve seat

172 inlet

174 side surface

176 fixed pressure chamber

178 sealing ring

180 support ring

182 chamber

184 exhaust/purge opening

A₁First output pressure

A₂Second output pressure

E₁First input pressure

E₂Second input pressure

F₁First effective piston face

F₂Second effective piston face

F₃Third effective piston face

F₄Fourth effective piston face

F₅Fifth effective piston face

P hydraulic line pressure.

Claims

1. Valve having a valve housing (130), an inlet pressure chamber (138) which can be acted upon by an inlet pressure, an outlet pressure chamber (140) which can be acted upon by an outlet pressure, a first blocking element (142) which is movable in the longitudinal direction (124, 126) of the valve between the inlet pressure chamber (138) and the outlet pressure chamber (140), and a second blocking element (154) which is assigned to the inlet pressure chamber (138) and is opposite the first blocking element (142), the first blocking element (142) having a passage (144) which runs in the longitudinal direction (124, 126) and connects the inlet pressure chamber (138) to the outlet pressure chamber (140), wherein the effective piston surface of the first blocking element (142) facing the outlet pressure chamber (140) is greater than the effective piston surface of the first blocking element (142) facing the inlet pressure chamber (138), whereby the first blocking element (142) can be moved by the outlet pressure from an open position, in which the first blocking element (142) is at a distance from the second blocking element (154) by way of the through-channel (144) with a fluid connection between the inlet pressure chamber (138) and the outlet pressure chamber (140), to a closed position, in which the second blocking element (154) bears against a valve seat (170) of the first blocking element (142) with the through-channel (144) closed, wherein the valve seat (170) encloses an inlet (172) of the through-channel (144) facing the inlet pressure chamber (138).

2. Valve according to claim 1, characterized in that the second blocking element (154) is arranged so as to be displaceable or in a gapped manner in a transverse direction of the valve, i.e. transversely to the longitudinal direction (124, 126) of the valve, so that the second blocking element (154) can be tilted relative to the longitudinal axis (128) of the valve.

3. The valve of claim 2, wherein the second latch member (154) is resiliently supported in a transverse direction.

4. The valve of claim 1, wherein the second latch (154) is movable in a longitudinal direction (124, 126).

5. The valve according to claim 4, characterized in that the second blocking element (154) is supported or can be supported on a support element (156) on its side remote from the first blocking element (142).

6. The valve according to claim 5, characterized in that mutually opposite bearing surfaces of the support (156) and of the second blocking element (154) are designed such that the second blocking element (154) supported on the support (156) can be tilted relative to a longitudinal axis (128) of the valve.

7. The valve according to claim 6, characterized in that the bearing surface (166) of the second blocking element (154) is arched or crowned in the direction of the support element (156) and/or the bearing surface (164) of the support element (156) is arched or crowned in the direction of the second blocking element (154).

8. The valve according to claim 5, wherein the support (156) is movable from a first end position, in which the second blocking member (154) is supported on the support (156) such that the first blocking member (142) is movable to an open and a closed position, to a second end position, in which the second blocking member (154) is supported on the support (156) such that the first blocking member (142) is not movable to the closed position, wherein the support (156) is movable from the first end position to the second end position when the value of the input pressure is smaller than a preset lower input pressure limit.

9. The valve according to claim 8, characterized in that a stop block (146) is provided at which the first blocking element (142) is supported or can be supported at a distance from a second blocking element (154) which is supported on the support (156) in the second end position.

10. Valve according to claim 8, characterized in that a fixed pressure chamber (176) is assigned to the support (156), which fixed pressure chamber can be supplied with an input pressure for fixing the support (156) in the first end position.

11. The valve according to claim 1 or 2, wherein the first blocking member (142) is pretensioned into the open position.

12. Valve according to claim 11, wherein a spring means (168) is provided for pretensioning into the open position.

13. Valve according to claim 12, wherein the spring means (168) is a helical compression spring.

14. The valve according to claim 12, wherein the spring arrangement (168) is supported or supportable on one side on the first blocking member (142) and on the other side on the second blocking member (154).

15. The valve according to claim 1 or 2, wherein the second blocking member (154) is supported or connected to the valve housing (130) with sealing of the input pressure chamber (138).

16. The valve according to claim 15, wherein the second closing element (154) is supported or connected to the valve housing (130) by means of an intermediate or annular sealing ring with sealing of the inlet pressure chamber (138).

17. A valve according to claim 16, wherein the sealing or o-ring seal is of plastic or elastomeric construction.

18. Valve according to claim 1 or 2, wherein the second blocking element (154) has a projection which projects in the longitudinal direction (124, 126) and is intended to abut against the valve seat (170).

19. The valve of claim 18, wherein the protrusion is tapered or bulbous.

20. The valve of claim 18, wherein the valve seat (170) is tapered or crowned.

21. The valve according to claim 1 or 2, characterized in that an opening pressure chamber (148) is assigned to the first blocking element (142), which opening pressure chamber can exert an opening pressure during the movement of the first blocking element (142) from the closed position into the open position.

22. Valve according to claim 1 or 2, characterized in that the first blocking element (142) can be moved from the open position into the closed position and/or in the closed position the value of the input pressure can be lowered to a value below the output pressure while maintaining the closed position only if the value of the output pressure is greater than a preset upper value of the output pressure.

23. The valve of claim 22, wherein in the closed position, the magnitude of the input pressure can be reduced to a predetermined lower input pressure limit while maintaining the closed position.

24. Hydraulic control device (2) for a clutch device, having at least one valve according to one of claims 1 to 23, wherein the at least one valve is connected behind or built into a second line section (8).

25. The hydraulic control device (2) according to claim 24, characterized in that the clutch device is a dual clutch device.

26. The hydraulic control device (2) according to claim 24, characterized in that the hydraulic control device (2) has a pressure supply device (4) for supplying the input pressure, a first line section (6) connected to the pressure supply device and a second line section (8) connected to the first line section (6) via a swivel joint (10).

27. The hydraulic control device (2) according to claim 26, characterized in that the first conduit section (6) is stationary.

28. The hydraulic control device (2) according to claim 26, characterized in that the second conduit section (8) is rotatable relative to the first conduit section (6).

29. The hydraulic control device (2) according to claim 24, characterized in that the at least one valve has a structure that rotates with the second conduit section (8).

30. The hydraulic control device (2) according to claim 24, characterized in that the valves comprise a first valve (20) and a second valve (22), wherein an input pressure chamber (138) of the first valve (20) can be supplied with a first input pressure (E)₁) And the input pressure chamber (138) of the second valve (22) can be acted upon by a second input pressure (E)₂) And a first output pressure (A) can be output in the output pressure chamber (140) of the first valve (20)₁) And a second output pressure (A) can be output in an output pressure chamber (140) of the second valve (22)₂）。

31. According to claimThe hydraulic control apparatus (2) of claim 30, wherein a first actuator (12) for a first clutch and a second actuator (14) for a second clutch are provided, the first actuator being operable by the first output pressure (a)₁) Is controlled, the second actuator is capable of passing the second output pressure (A)₂) And (5) controlling.

32. The hydraulic control device (2) according to claim 30, characterized in that the opening pressure chamber (148) of the first valve (20) can be supplied with a second input pressure (E)₂) And the opening pressure chamber (148) of the second valve (22) can be acted upon by a first input pressure (E)₁）。

33. The hydraulic control device (2) of claim 24, characterized in that the at least one valve is inserted into a longitudinal bore (24) in the hub (18).

34. The hydraulic control device (2) according to claim 33, characterized in that the at least one valve is inserted in a longitudinal hole (24) in a wall (26) of the tubular hub (18).

35. The hydraulic control device (2) according to claim 33, characterized in that the longitudinal bore (24) is closed or closable by means of a seal (28).

36. The hydraulic control apparatus (2) of claim 35, wherein the seal (28) is removable.