JPH10196679A - Operation device for frictional clutch operation, especially for pneumatic operation - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent great force, especially a tilting force, from working on an interlocking release bearing device from a control valve side by expressing a differential related to an actual quantity and a guiding quantity in terms of positions of both side valve elements in a valve device. SOLUTION: A control valve 42 constitutes a mechanical position regulating device with its valve element, a pneumatic power cylinder device 14, and a connection element 74 serving as a supply device element for an actual value signal. According to a matching switch between three control conditions, the position regulating device regulates an axial directional position of an interlocking release bearing device 32 to a target position indicated by means of a guiding signal from a guiding signal supply device unit 60. Therefore, a momentary position of the interlocking release bearing device 32 is expressed as an actual quantity in terms of the position of the second valve element, while a target position of the interlocking release bearing device 32 is expressed as a guiding quantity in terms of the position of the first valve element.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a friction clutch arranged between a transmission of a casing bell and an internal combustion engine in a power train of a motor vehicle, particularly a useful motor vehicle (commercial vehicle, Nutz-Kraftfahrzeug). An interlocking release bearing device that is moved substantially coaxially with respect to a friction clutch for operating a friction clutch, and a guide amount and a control amount that represent a target position by a control valve that communicates with a pressure medium source. The invention relates to an operating device comprising a positioning servo device having a pressure medium / power cylinder device acting on the decoupled bearing device, the positioning servo device being operable depending on the actual amount representing the axial position of the decoupled bearing device.

[0002]

2. Description of the Related Art An operating device of this kind is known, for example, from DE 33 21 578. The known operating device has a negative pressure servo power assist (negative pressure servo force amplifier) as a positioning servo device. Servo power assist assembled in the type of negative pressure power brake (negative pressure braking force amplifier) is integrated with the pneumatic power cylinder (pneumatic power cylinder) and the control valve, and outside the casing bell Are located in The two working chambers of the pneumatic power cylinder are isolated from each other by a piston guided movably in the axial direction and an elastic diaphragm. One working chamber configured as a negative pressure chamber is connected to a suction manifold system (suction pipe system) of the internal combustion engine. Another working chamber, which is used as a control chamber, can be brought into communication with the vacuum chamber by way of a control valve or with the atmosphere via a pressure compensation opening. The operation of the negative pressure servo power assist is performed by a control rod hitting the valve body of the control valve. The control rod can be moved axially by a cam driven by an electric motor. The control valve is switched such that the axial movement of the control rod causes the piston to power-amplify and follow the movement of the control rod. The movement of the piston acts on a slave cylinder (Nehmerzylinder) which is arranged outside the casing bell via a hydraulic master cylinder (Geberzylinder) and is in communication with the master cylinder.
The slave cylinder acts on an interlock release fork attached to the interlock release bearing device. Emergency operation of the clutch (Notbetaetigung) when the internal combustion engine is stopped and therefore the vacuum is insufficient is possible because the control rod can act directly on the piston via the valve body of the control valve It is.

[0003] The control valve has a valve body that cooperates with an elastic valve seat. A communication channel (communication passage) is provided in the valve seat. As long as the valve is not pressed against the resilient valve seat to close the communication channel by the valve, the communication between the control chamber and the surrounding air is established by the communication channel. Another communication channel communicates the control chamber with the negative pressure chamber.

[0004] In addition, operating devices of the type mentioned at the outset are known which have a pneumatic power cylinder as pressure medium power cylinder device. The operating device is mounted externally on the casing bell as an integrated unit comprising a pneumatic power cylinder, a hydraulic slave cylinder, and a control valve. The piston of the pneumatic power cylinder is
It is mounted on a rod element which forms the piston of the hydraulic slave cylinder and is connected to the tappet. The tappet reaches the interior of the casing bell and engages a decoupling fork attached to the decoupling bearing device. The hydraulic slave cylinder is connected to a master cylinder operable with a clutch pedal and a control introduction part of a control valve. The control valve, depending on the hydraulic pressure being applied to the control introduction, causes the compressed air to be supplied to the pneumatic power cylinder so that the set hydraulic pressure determined by the compression spring device is generated at the control introduction. It controls the supply and the discharge of air from the pneumatic power cylinder. In this case, the hydraulic slave cylinder serves as a measuring cylinder (measuring cylinder,
Messzylinder). In the operation of the master cylinder, in addition to the operating force of the pneumatic power cylinder based on the supply of compressed air to the pneumatic power cylinder, via a hydraulic slave cylinder used as a measurement cylinder, The force is exerted directly on the rod element and thus on the decoupling bearing device.

[0005] It is to be noted that operating devices of the type mentioned at the outset, in which the pressure medium / power cylinder device is arranged in the casing bell, are marketed. A possible variant is characterized in that the pressure medium and power cylinder device is configured to exert an essentially coaxial force on the clutch shaft on the decoupling bearing device. For this,
For example, it is worth considering that the pressure medium / power cylinder device comprises a pressure medium / ring cylinder essentially concentric with the clutch axis.

[0006] Such a device utilizes in principle a control valve of the type described above which has a hydraulic slave cylinder used as a measuring cylinder, which exerts a force on the decoupling bearing device in the operation of the control valve. Could be done. However, in this case, in the case of a pressure medium / power cylinder arrangement configured to exert an essentially coaxial force on the clutch axis to the decoupling bearing device, the measuring cylinder is also essentially coaxial with the clutch axis. Unless it is configured to exert a force on the decoupling bearing device, for example, unless it is configured as a measuring ring cylinder essentially concentric with the clutch axis, the measuring cylinder exerts a tilting moment on the decoupling bearing device. That would be inconvenient. In such measuring ring cylinders, hydraulic measuring cylinders are not tight (leakage)
In some cases, the replacement of the measuring cylinder would have the disadvantage of requiring the removal of the casing bell from the internal combustion engine. On the other hand, if, for example, a measuring cylinder arranged beside the pressure medium / power cylinder device is used, the tilting moment exerted on the decoupling bearing device in order to absorb or compensate for this tilting moment Causes correspondingly high mechanical costs.

[0007]

An object of the present invention, on the other hand, is to provide a pressure medium disposed inside a casing bell.
An operating device of the type mentioned above with a power cylinder device, (pressure medium by the supplied pressure medium,
An operating device in which significant forces, especially tilting forces, from the control valve (and, if necessary, measuring devices attached to the control valve, etc.) are not applied to the decoupling bearing device, except for the force via the power cylinder device To provide.

Another object of the present invention is to provide a control device of the type mentioned at the beginning, whether the pressure medium / power cylinder device is arranged inside or outside the casing bell. It is an object of the present invention to provide an operating device which allows a simplified maintenance of the valve and the components attached thereto.

[0009]

To solve at least one of these problems, the present invention provides the following:
That is, between the first control state in which the control valve communicates the pressure medium / power cylinder device with the pressure medium source and the second control state in which the pressure medium / power cylinder device communicates with the pressure compensation opening. A valve device which can be switched between the two control states depending on the difference amount associated with the actual amount and the guide amount, wherein the valve device is Comprises two valve elements movable relative to each other and relative to the valve casing, and wherein the guiding amount is of the two valve elements relative to the valve casing. The actual quantity is represented by the position of the second one of the two valve elements relative to the valve housing. Ri, and the difference amount is proposed that are represented by the relative position of the two valve elements relative to one another.

[0010]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a control valve having two valve elements, the positions of which each represent a separate quantity which determines the control state of the control valve;
"Guide amount side" of the positioning servo device ("Fuehrungsg
In the event of a change in the guiding amount of the roessen-Seite "), a significantly fluctuating force is not exerted on the decoupling bearing device, except for the force exerted by the supplied pressure medium via the pressure medium / power cylinder device. One enables the disconnection (de-correlation, Entkopplung) between the "actual quantity side" of the positioning servo device ("Ist-Groessen-Seite") and the other with the "guide quantity side" of the positioning servo device. At this time, no significant tilting moment is applied to the interlock release bearing device from the “guide amount side” of the positioning servo device. This makes it possible to eliminate the mechanical costs for absorbing and compensating the tilting force, so that the operating device according to the invention can be manufactured at low cost.

Since the actual quantity and the guidance quantity are each represented by a unique position of the valve element, the uncomplicated connection of the control valve to the guidance quantity supply unit on the one hand and to the actual quantity supply unit on the other hand is reduced. It is possible. Thereby, the control valve is easy to maintain,
For example, it can be formed so that it can be replaced without great expense.

The valve device may be adjustable to a third control state depending on the difference. In the third control state, the pressure-medium power cylinder arrangement is advantageously closed essentially free of pressure medium. That is, at the same time, there is no communication between the pressure medium source and the pressure compensation opening. then,
A fixed position (state) of the valve device is associated with (associated with) the third control state. However, the third control state alternately occupies the position where the valve device is arranged in the first control state and the position where the valve device is arranged in the second control state. It may be characterized by not being closed so as not to have pressure medium.

A first signal connection for the control valve to receive a guidance signal providing a guidance amount, in particular from a clutch pedal device, and a transmitter element device (an actual value signal providing the actual amount) attached to the decoupling bearing device ( It is proposed to have a second signal connection for receiving from the feeder element device. The guidance signal and the actual value signal each then preferably act directly on exactly one of the two valve elements independently of the respective other signal, i.e. the guidance signal is the first On the valve element, the actual value signal acts on the second valve element. The fact that the signals act directly on exactly one valve element in each case does not exclude that the signals act on the respective valve element via intermediate components. In other words, the concept of "direct action" is distinguished from "indirect" action, in particular from the "indirect" action of the guide signal to the second valve element via the positioning servo, i.e. the actual quantity That the position of the second valve element, which is adjusted by the guiding quantity in response to a given condition and which represents the actual quantity accordingly, also changes during the control state using the pressure medium / power cylinder device. It is only used to distinguish it from the "indirect" effect of the guide signal to the second valve element via the positioning servo device, as achieved by a corresponding switching of the valve.

The actual value signals are, in particular, pressure, volume, force,
It may be a hydraulic, pneumatic, pneumatic, mechanical or electrical signal represented by a travel (distance), an angle, a current strength or a voltage. At that time, the second signal connection, if necessary,
Converter means are provided for converting the actual value signal into an actual quantity.

The positioning servo device has a mechanical position adjusting device having a mechanically connected or connectable transmitter element (feeder element, Geberelement) for directly or indirectly detecting the position of the decoupling bearing device. It is suggested that In this connection, it is advantageous for the transmitter element to act on the second valve element and in particular to be (or are) kinematically coupled to it. The second valve element is preferably essentially fixedly connected to the decoupling bearing device or to the decoupling bearing device-side part of the pressure medium and power cylinder device via a connection element which is possibly integrated therewith. (Connected so as not to move relative to each other), or may be fixedly connected. However, the second valve element is preferably essentially fixedly connected thereto and possibly integrated therewith, and is provided with a decoupling bearing device or a decoupling bearing device-side part of the pressure medium power cylinder device. It is also possible to be connected or connected to this via a connecting element that is prestressed or prestressed towards the

As the guide signal, in particular, pressure, volume, force,
Consider hydraulic, pneumatic (pneumatic, pneumatic), electrical, or optical signals represented by stroke, angle, current, voltage, or light intensity. In this case, the first signal connection is, if appropriate, provided with a converter means for converting the guidance signal into a guidance quantity. It is preferable to use a pneumatic or hydraulic signal as the guide signal, and a hydraulic guide signal is most preferable. In this connection, it is proposed that the transducer means for the conversion of the pneumatic or hydraulic guidance signal comprises a particularly elastically prestressed piston. The piston is preferably connected or connectable with the first valve element, and is particularly integrated therewith.

The valve device may include, in addition to the first valve element and the second valve element, an auxiliary valve element movable relative to the valve casing. The auxiliary valve element cooperates with the first valve element and / or the second valve element to provide at least one of the control states.

[0018] The auxiliary valve element preferably has an engagement portion arranged corresponding to the first valve element.
In the engagement portion, a first valve element is provided for the entrainment of the auxiliary valve element or / and for the interruption (temporary interruption) of at least one pressure medium communication in the control valve. In particular, it engages to interrupt (temporarily shut off) the pressure medium communication between the pressure medium / power cylinder device and the pressure compensation opening.

Preferably, the auxiliary valve element further has an engagement portion disposed corresponding to the second valve element. In the engagement portion, a second valve element is provided.
For the entrainment of the auxiliary valve element or / and for the interruption (temporary interruption) of at least one pressure medium connection in the control valve, in particular between the pressure medium source and the pressure medium power cylinder device For the interruption of the pressure medium communication (temporary interruption) or / and for the closure of the pressure medium communication between the pressure medium source and the pressure compensation opening, which is in principle possible in principle. Engage.

An auxiliary valve element to create a respective pressure medium communication by contributing in creating or (temporarily) interrupting at least one, preferably a plurality of pressure medium communication in the control valve; or The conditions which have to be fulfilled in order to shut off can be set particularly strictly and, if necessary, independently of the other pressure medium connections.

It is proposed to provide a prestressing means, in particular a prestressing means acting between the second valve element and the auxiliary valve element. In particular, in order to close the pressure medium communication in the basic state of the operating device in which the clutch is not actuated, the prestressing means provides the auxiliary valve element with the second valve element to the correspondingly arranged engaging part of the auxiliary valve element. Prestressing in the direction for engagement or / and in the direction for engagement of the first valve element with the correspondingly arranged engagement portion of the auxiliary valve element. The prestress of these prestressing means must be chosen large enough to ensure a bare state (sealing) and at the same time to minimize the tilting forces that may be generated by the prestress. is there. The first valve element and the second valve element and possibly the valve housing to limit the range of movement of both valve elements relative to each other, and possibly to the valve housing In order to limit the range of movement of at least one of the valve elements, each can have at least one stop part or engagement part. With the correspondingly disposed stop portions of the first and second valve casings in contact with one another, one pressure medium connection in the control valve, in particular a connection between the pressure medium source and the pressure medium / power cylinder device, Preferably, pressure medium communication between them is created.

It is further proposed that a prestressing means is provided which acts between the first valve element and the second valve element, in particular in order to keep the pressure compensation opening in the basic state open. Is done. The prestress of these prestressing means must be chosen large enough to barely overcome the frictional forces generated and at the same time to minimize the tilting forces which may be caused by this prestress. The stress (tension) of the prestressing means acting between the first valve element and the second valve element is such that the correspondingly disposed stopper portions of the first and second valve elements contact each other. It is preferable that the maximum value is obtained in the state in which the user is in the state.

According to an advantageous configuration of the operating device according to the invention, one of the elements (ie the first valve element and the second valve element), in particular the second valve element, forms a control edge. It has at least one part. The part comprises at least three openings for the pressure medium in the other valve element and in the valve housing, and in particular one opening for the pressure medium in the other valve element and two openings for the pressure medium in the valve housing. At least one relative position of the two valve elements with respect to each other during movement of the one valve element relative to the other valve element in one direction. In at least one of the pressure medium openings, in particular at least one control edge passes past the pressure medium opening in the other valve element, whereby the control valve First pressure medium communication, especially the pressure medium communication between the pressure medium source and the pressure medium / power cylinder device There is blocked, or produced, and, another pressure medium communication within the control valve, in particular a pressure-medium communication is created or interrupted, between the pressure compensating opening and the pressure medium power cylinder arrangement. In this configuration, preferably no auxiliary valve element is provided which cooperates with the first valve element and / or the second valve element and is movable relative to the valve housing.

It is possible that one of the valve elements (first valve element and second valve element), in particular the first valve element, has at least one, especially pin-like, engaging portion, The engagement part engages a correspondingly arranged slit-shaped cavity of the other valve element. At that time, the space is at both ends,
It is defined by a stop for limiting the range of movement of both valve elements relative to each other.

It is particularly advantageous that the control valve (independently of other structural features) is provided with a pressure compensation opening in the basic state of the operating device without clutch operation in the pressure medium / power supply. It is proposed to occupy a control state in communication with the cylinder device. Pneumatic
In the case of a pressure medium / power cylinder device configured as a power cylinder device, if the cylinder device is vented (exhausted, ventilated) to the atmosphere via the pressure compensation opening, the ambient pressure in the basic state of the operating device Controls the inside of the cylinder device. As a result, unintended pressure fluctuations in the cylinder device due to external influences (for example, temperature) are eliminated.

The first valve element, the second valve element and, if provided, the auxiliary valve element are mounted movably along the valve axis in the cavity of the valve housing. Is possible. The actual quantity and the guidance quantity are then represented by the axial position of the respective valve element. At least one of said elements (first valve element, second valve element and possibly auxiliary valve element) is configured as a ring element which is at least regionally coaxial with the valve axis, and It is possible to surround at least one further of the valve elements at least partially radially outward.

The cavity of the valve casing is preferably a ring cavity. The ring-shaped cavity has a radially spaced, coaxially extending ring-cylindrical wall and extends coaxially with a valve shaft, preferably integral therewith, which is fixed with respect to the valve casing. Extending around the existing tube element. In this case, the tube element has a pressure medium through-opening in the region of its free end, in particular open in the axial direction, as part of at least one pressure medium communication in the control valve, in particular with a pressure medium power cylinder device. As part of the pressure medium communication between the pressure medium source and / or the pressure medium / power cylinder device and the pressure compensation opening. In this connection, it is proposed that the first valve element has a ring-shaped part surrounding the tube element at least in a region radially outside. At this time, at least one ring-shaped packing element (seal element)
Preferably acts to block leakage between the ring-shaped part and the tube element.

Furthermore, at least one ring-shaped packing element between the ring-cylindrical wall radially outside of the ring-shaped cavity and the first valve element, in particular the ring-shaped part, blocks leaks. It is proposed to work as follows.

It is particularly advantageous for the first valve element to have a pipe section which borders the ring-shaped section in the axial direction. The tube section surrounds the tube element at least in a region radially outside. In this case, it is preferred that at least one ring-shaped packing element acts so as to close the gap between the pipe section and the pipe element.

An auxiliary valve element configured as a ring element can surround the first valve element, in particular the pipe section, at least in a region radially outward. It is particularly advantageous that the first valve element has a seal which extends essentially radially adjacent to the pipe section and axially covers the pressure medium through-opening at the free end of the pipe element. It is suggested that: By means of the seal, the first valve element is brought into engagement with a correspondingly arranged ring-shaped and radially inwardly projecting engagement part of the auxiliary valve element for entrainment or / and
Engage to block at least one pressure medium communication. The engagement portion of the auxiliary valve element may define a pressure medium through-opening in the radial direction. The pressure medium through-flow opening is a part of one pressure medium communication in the control valve and is arranged in particular corresponding to the pressure compensation opening or is identical thereto.

In connection with the configuration of the first valve element having the seal, the first valve element may have at least one, in particular in the radial direction, an end region of the tube section adjacent to the seal. The open pressure medium through-flow opening is part of at least one pressure medium communication in the control valve, in particular the pressure medium communication between the pressure medium / power cylinder device and the pressure medium source or / and the pressure medium / power cylinder. It is particularly advantageous to have it as part of the pressure medium communication between the device and the pressure compensation opening.

The second valve element formed as a ring element can be a first valve element or (and)
In some cases, the auxiliary valve element can be surrounded at least partially radially outside. Between the second valve element and the auxiliary valve element, at least one ring-shaped packing element may act to close the leak.

[0033] Furthermore, at least one ring-shaped packing element may act between the ring-cylindrical wall portion radially outside the ring-shaped space and the second valve element so as to close the leak.

A ring-cylindrical ring defining the cavity radially outwardly between the tube section and the auxiliary valve element or / and radially between the second valve element and the valve casing. It is proposed that a respective pressure medium channel (pressure medium channel, pressure medium groove), in particular a pressure medium ring channel, is formed between the wall and the wall. The pressure medium channel is part of one pressure medium communication in the control valve, in particular the pressure medium communication between the pressure medium source and the pressure medium / power cylinder device. In this connection, between the two pressure medium channels, a pressure medium which can be shut off by engagement of the second valve element with an engagement portion of the auxiliary valve element which is arranged corresponding to the second valve element Advantageously, communication is provided.
The pressure medium communication preferably defines at least one radially open pressure medium flow-through opening in the second valve element or (and / or) a pipe section, an auxiliary valve element or a second valve element. Equipped with a ring chamber.

With respect to the connection of the pressure medium source or / and the guide signal transmitter to the control valve, a valve connection connected to the pressure medium source or / and a guide signal supply. It is proposed that each of the valve connections has a hole in the valve housing that opens into the cavity and is directed in particular in a radial direction. The hole of the valve connection, which is connected to the guidance signal supply, preferably opens into the cavity in the region of the cavity bottom, which closes the cavity on one side in the axial direction. The ring-shaped part of the first valve element, which is used as a piston of the converter means, is located facing the cavity bottom. The bore of the valve connection, which is connected to the pressure medium source, preferably opens into the cavity in the cavity end region bordering the axially open cavity opening.

With regard to the connection of the pressure medium power cylinder device to the control valve, it is particularly advantageous that the pressure medium
A valve connection in communication with the power cylinder device connects a first bore opening into the cavity, in particular extending through the pipe element, and preferably to the first bore. It is proposed to provide a second hole which is located and extends at the bottom of the cavity.

In an advantageous variant of the operating device according to the invention,
It is possible that the valve element, in particular the first valve element and the second valve element, are mounted rotatably about the valve axis in a cavity of the valve housing. In this case, the actual quantity and the guidance quantity are represented by the rotational position of the respective valve element.

One of the elements (the first valve element and the second valve element), particularly the second valve element, has a ring-shaped portion coaxial with the valve axis. The ring-shaped part surrounds the other one of the two valve elements at least in a region radially outward. In this context, a ring-shaped portion of the one valve element, which is radially outwardly surrounded by the inner peripheral surface of the valve casing defining the cavity, extends circumferentially and is circumferentially relative to one another. Having at least two breakthroughs offset in direction and separated from each other by respective portions of said ring-shaped portion and opening radially inward and radially outward;
The valve casing is provided with at least two holes, preferably radially oriented, opening into the cavity, the openings of the holes being circumferentially offset from one another and the one At least partially covering another breakthrough of each one of said breakthroughs in at least one rotational position of said valve element, and said at least one communication channel in said other valve element has a through hole, in particular Is provided,
In particular, both openings of the through-hole are at least partially covered by another break-through of each one of the break-throughs, so that the through-hole has at least one of the two valve elements relative to each other. It is particularly advantageous for two of the breakthroughs to be open at two relative rotational positions.

In addition to this, it is furthermore particularly advantageous to provide exactly three holes each, exactly three breakthroughs each, and exactly one communication channel, in particular a radially extending through hole. It is proposed that In this case, in at least one rotational position region of both valve elements relative to each other and relative to the valve housing, two of these holes, two of these breakthroughs, And the communication channel creates pressure medium communication between the pressure medium source and the pressure medium / power cylinder device,
And in at least one further rotational position area of both valve elements, relative to each other and to the valve housing, two of these holes, two of these breakthroughs And this communication channel creates a pressure medium communication between the pressure medium and power cylinder device and the pressure compensation opening.

The part of the ring-shaped part separating the breakthrough from one another is preferably in at least one relative rotational position of both valve elements with respect to one another and / or of one valve element. At least one channel opening in at least one rotational position relative to the valve housing, in particular the opening of a through hole in the other valve element, and / or of the opening of said hole in the valve housing. So that at least one is closed by a respective part of the ring-shaped part, which in particular forms a control edge,
Dimensioned (sized).

By means of the last-mentioned measures, the pressure medium / power cylinder device and the pressure medium source can be moved in at least one rotational position of the valve element both relative to each other and relative to the valve housing. The situation in which neither pressure medium communication nor pressure medium communication between the pressure medium / power cylinder device and the pressure compensation opening is created can be achieved in a simple manner. Thereby, without the additional auxiliary valve element movable relative to the valve housing, three control valve states, i.e., "pressure medium source and pressure" can be achieved using the first valve element and the second valve element. "Pressure medium communication state between the medium and the power cylinder device", "pressure medium communication state between the pressure medium and the power cylinder device and the pressure compensation opening", and "essential pressure of the pressure medium and the power cylinder device" A connection state that does not pass the medium (does not receive the pressure medium) ”can be realized.

The openings of the three holes in the valve casing are preferably spaced from one another at equal circumferential angles, preferably covering equally sized circumferential angle regions. . Correspondingly, for the three breakthroughs in the ring-shaped part of the one valve element, they each cover an equally sized circumferential angle area and are spaced from one another by an equal circumferential angle. Advantageously, they are arranged. Preferably, the openings of the three holes and correspondingly the three breakthroughs are not located essentially offset from one another in the axial direction.

The three holes are provided corresponding to the pressure compensating opening, the holes provided corresponding to the pressure medium source, and provided corresponding to the pressure medium / power cylinder device. It is preferable that the holes formed are located consecutively one after the other in the determined rotation direction. At that time, in the basic state of the operating device, the opening of the through hole of the first valve element is located substantially opposite to the hole arranged corresponding to the pressure compensation opening, and the second valve element The part forming the control edge of the ring-shaped part of the ring is offset in the direction of rotation with respect to the hole arranged corresponding to the pressure-compensation opening, but is close to but adjacent to it. doing. In this case, for the operation of the clutch, the first valve element can be twisted (relatively rotated) in the rotation direction with respect to the rotation position in the basic state. It can be twisted to a rotational position which is located substantially opposite the hole arranged corresponding to the source.

The cavity for receiving the valve element is formed in the valve housing as a through-hole extending preferably transversely (crosswise) to the direction of movement of the decoupling bearing device. A first valve element is accessible at one end of the through-hole (hand-held), especially protruding, and a second valve element is accessible at another end of the through-hole And especially protruding. In this connection, it is particularly advantageous that the end portion of the second valve element projecting from the through-hole in the valve housing carries the fixedly connected curved body as a connection element. . The bent body is engaged with the decoupling bearing device or a portion of the pressure medium / power cylinder device on the decoupling bearing device side, and in particular, the elastic body means engaged with the bending body and the valve casing, preferably the end means. Leg springs (Schenkelf
prestressed towards it by means of an elastic body comprising an eder) or in a form-constrained manner (for example by means of a slot (elongate) in which the mating part of the curved body engages) I have. As a result, the curved body is forcibly entrained. The linear movement of the uncoupling bearing device or of the uncoupling bearing device side of the pressure medium and power cylinder device can then be converted by the bending body into a rotary motion of the second valve element.

If converter means are provided for the conversion of pneumatic or hydraulic guidance signals,
The elastic prestress of the transducer means (spring
The prestressed piston may be part of a separate cylinder and piston arrangement for the valve element. In so doing, the piston is preferably movable in a direction extending essentially transversely (crosswise) to the valve axis, and the linear movement of the piston engages the first valve element. It can be converted into a rotational movement of the first valve element by a coupling device, in particular a toggle lever device.

In order to achieve a high reliability (operating stability) of the control valve, the first valve element of the valve casing
And the surface of the second valve element in contact with each other is a sealing surface (seal surface) or / and a sliding surface (Dicht-
oder / und Gleitflaechen) or (and / or) the packing element can act to close the leak between them.

The above-described configuration of the modified control valve having the valve element rotatably mounted around the valve axis in the valve casing cavity moves the valve casing cavity along the valve axis. It can easily be diverted to a control valve with a possibly mounted valve element.

In general, the direction of disengagement of the pressure medium / power cylinder device and the direction of disengagement of the friction clutch can have any orientation with respect to each other. This is not only the case when the pressure medium / power cylinder device is arranged outside the casing bell and is mounted, for example, on the transmission housing. However, especially when the pressure medium / power cylinder device is arranged in the casing bell, the direction of disengagement of the pressure medium / power cylinder device and the direction of disengagement of the friction clutch are essentially parallel to each other. Is often convenient. At this time, it is preferable that the clutch axis and the power cylinder apparatus axis substantially coincide with each other.

The axis of the valve and the axis of the power cylinder device are:
In principle, they can be arbitrarily oriented with respect to each other and need not have a common point. However, the valve axis and the power cylinder device axis are essentially parallel to each other,
Alternatively, it is advantageous that they are essentially orthogonal to each other as projected onto a plane essentially parallel to both axes.

Both with the valve element movable along the valve axis and with the valve element rotatable around the valve axis, the advantageous configuration of the control valve, in particular the valve arrangement, and the above-described device The control valve, which can be manufactured individually or jointly, has a compact structure, has high functional reliability, and contributes to manufacturing at low cost. The control valve may be located entirely within the casing bell, or may be at least partially located within the casing bell, and the control valve of the casing bell connected to the internal combustion engine and the transmission. In some cases, it is preferred that the hand be accessible (reachable) from the outside, and in particular be removable. The operating device can then be easily serviced and, if necessary, repaired, without having to remove the casing bell, which is generally constituted by a part of the transmission housing, from the internal combustion engine. The control valve may be configured integrally with the pressure medium / power cylinder device,
However, it is advantageous for the control valve to be particularly removably mounted as a separate structural unit on the pressure medium and power cylinder device.

In particular, in view of the fact that the maintenance is very easy, it is particularly advantageous that the control valve structure unit provided with the control valve has a higher power than the power cylinder structure unit provided with the pressure medium / power cylinder device. It is proposed that it be offset radially with respect to the cylinder axis and be removably mounted on the radially outer part of the power cylinder-structure unit. In this connection, the control valve structural unit may be provided with fixing means or / and connecting means possibly acting between the two structural units, preferably at least one radius which essentially corresponds to said radial direction It is particularly advantageous that the radially removable from the power cylinder structural unit after the release of the directionally accessible (reachable) fastening means or / and the coupling means is essentially possible. The resulting ease of servicing works both with control valves located inside the casing bell and with control valves located outside the casing bell.

As the pressure medium, a pneumatic or hydraulic pressure medium can be considered. It is particularly advantageous for the pressure medium to be a pneumatic pressure medium, in which case the pressure medium source is preferably an overpressure source which supplies a pressure above ambient pressure.

[0053]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a block diagram showing a first embodiment of the present invention. FIG. 1 shows a casing bell (G) between an internal combustion engine and a transmission (transmission device, gear device) in a drive train (power transmission system) of a motor vehicle.
The operating device 10 according to the invention for a friction clutch, in this example a pressed clutch, arranged in an ehaeuseglocke 12 is shown schematically. The operating device 10
Pressure cylinder (pressing means) power cylinder device (Druckmitt) configured as a structural unit (package unit)
el-Kraftzylinderanordnung) 14, in this example a pneumatic power cylinder device (power cylinder device acting by gas, Pneumatik-Kraftzylinderanordnu
ng). The pressure medium / power cylinder device is also hereinafter referred to as an operating cylinder structural unit (operating cylinder / package unit). The actuating cylinder construction unit 14 comprises a pressure medium ring cylinder, in this example a ring cylinder-shaped cavity 18 in a stationary body member 20 and a pneumatic ring cylinder 16 formed by a pneumatic ring piston element 22. ing. The pneumatic ring piston element 22 is pre-stressed (to the left in FIG. 1) by a resilient means (spring means) 24 toward a clutch (not shown), and the pneumatic ring cylinder 16
A packing ring 26 for sealing the ring cylinder chamber is carried.

The pneumatic ring cylinder 16 and the pneumatic ring piston element 22
It is arranged coaxially with the clutch axis A. Body member 20
Has an axial hole through which a clutch shaft (transmission input shaft) 28 extends coaxially with the clutch axis A.

The ring-shaped portion 30 of the pneumatic ring piston element 22 at the clutch-side end of the ring piston element forms the decoupling ring (Ausrueckring) 30 of the decoupling bearing device (Ausruecklageranordnung) 32. I do. The interlock release bearing device further includes an interlock release ring 34 that can be twisted (relatively rotated) with respect to the interlock release ring 30 and rotates together with the clutch, and both the interlock release rings 30.
, And a spherical bearing 36 that allows relative rotation between them. The decoupling bearing device is used to release the clutch in order to interrupt the flow of force between the transmission and the internal combustion engine. It acts on the clutch via a spring tongue.

The operation cylinder structure unit 14 carries a control valve structure unit (control valve package unit) 40 which is releasably fixed (can be released) to the operation cylinder structure unit. The control valve structural unit comprises a control valve 4 shown only schematically in FIG.
2 is provided. The control valve structural unit 40 projects beyond the outer surface of the casing bell 12 through a correspondingly provided opening 44 in the casing bell 12, and the casing bell is connected to the internal combustion engine and the transmission. The case is arranged so that it is removable.

The control valve 42 is connected via a gas working conduit (gas conduit) 46 inside the control valve structural unit 40.
A pneumatic source (pneumatic source, pneumatic source) 51 via a pneumatic connection 48 at a portion of the control valve structural unit protruding beyond the outer surface of the casing bell 12 and via a further pneumatic conduit 50 Has been communicated with. The control valve 42 is further connected to the control valve structural unit 40 via a conduit (wiring) 52 inside the control valve structural unit 40.
Via a connection 54 at a portion protruding beyond the outer surface of the casing bell 12 and to another conduit 5
6 through the guidance signal supply unit (Fuehrungssignal
gebereinheit) 60. As the guide signal supply unit 60, in this case, a clutch pedal device 60 having a clutch pedal 62 is considered. The clutch pedal device is provided with a guide signal (an operation signal,
Control signal) in the form of hydraulic signal conduit (wiring)
It is designed (configured) to communicate to control valve 42 via 56, connection 54, and conduit (wiring) 52. Accordingly, the conduits (wirings) 52 and 56 are considered hydraulic conduits which are in communication via a connection 54 configured as a hydraulic connection.

The control valve 42 further communicates with the ring cylinder chamber of the pneumatic ring cylinder 16 via a pneumatic conduit 64 inside the control valve structural unit 40 and a pneumatic conduit 66 inside the operating cylinder structural unit 14. Have been allowed. Furthermore, the control valve 42 is in communication with a pressure compensation opening 70 in the clutch-side surface of the control valve structure unit via a pneumatic conduit 68 inside the control valve structure unit 40.

The instantaneous axial position of the decoupling bearing device 32 is, as shown diagrammatically by a dashed connection 76 inside the control valve construction unit 40, mechanically connected. Element (connecting rod element)
The control valve 42 is supplied via 72 and 74 in the form of a mechanical actual value signal representing the stroke (distance, Weg). For this purpose, a rod-shaped connecting element 74 projecting from the control valve structure unit 40 is movably connected to one valve element of a valve device with three valve elements. The three valve elements of the valve device are movable in the control valve structure unit 40 parallel to the clutch axis A. The first of the three valve elements is arranged in connection with the guide signal supply unit 60. The second (described above) valve element is arranged in connection with the decoupling bearing device and is movably connected with it via coupling elements 72 and 74 for axial movement. A third valve element, hereinafter referred to as an auxiliary valve element, is used in conjunction with the first and second valve elements to achieve various control states of the control valve 42. For the more exact structure of the control valve 42, see the embodiment shown in FIGS. The control valve 42a of this embodiment essentially corresponds to the control valve 42 of FIG. 1 in terms of function and basic structure. However, as the control valve 42, simply, only two movable
In particular, control valves with relatively rotatable valve elements may be considered. In this regard, see the embodiment shown in FIGS. The control valve 42b of this embodiment can be used in the case of the embodiment of FIG. 1 with only minor changes in the connection of one valve element to the decoupling bearing device.

The control valve 42 (or 42a or 42a)
b) depends on the guide signal output from the guide signal supply unit 60 for setting the target axial position of the decoupling bearing device 32 and the actual value signal indicating the instantaneous axial position of the decoupling bearing device 32. Then, switching between the three control states is performed. In the first control state, pneumatic communication (pneumatic communication) between the pneumatic ring cylinder 16 and the pneumatic source 51 is created via the control valve 42. As a result, pneumatic
The ring cylinder is supplied with a pneumatic medium (pneumatic medium), in this case compressed air, from a pneumatic source 51 and the pneumatic ring piston element 22 is correspondingly pushed out of the cavity in the direction of the clutch. In the second control state of the control valve 42, pneumatic communication between the pneumatic ring cylinder 16 and the pressure compensation opening 70 is created via the control valve 42. As a result, the protruding pneumatic ring piston element 22 is retracted into the cavity 18 again by the pressing force (compression force) of the clutch main elastic body (clutch main spring), for example, a diaphragm spring or the like. At that time, the pneumatic ring cylinder 16
The compressed air in the ring cylinder chamber flows out of the pressure compensation opening 70. In the third control state, the ring cylinder chamber of the pneumatic ring cylinder 16 is essentially free of gas (airtight, pneumatikdic
ht) It is closed. As a result, the pneumatic ring piston element 22 retains its instantaneous axial position.

The control valve 42 has a valve element, a pneumatic power cylinder device 14 and a connection element 72 which is a supply element for the actual value signal.
Together with the connecting element 74 form a mechanical position adjustment device. The position adjusting device adjusts the axial position of the decoupling bearing device 32 to the target position indicated by the guide signal from the guide signal supply unit 60 by corresponding switching between the three control states. For this purpose, the interlock release bearing device 42
Is represented by the position of the second valve element as an actual quantity, and the target position of the decoupling bearing device is represented by the position of the first valve element as a guiding quantity. The actual quantity and the guiding quantity depend on the position of the first and second valve elements relative to each other (ie by the position of the first and second valve elements relative to each other).
A difference amount (difference amount) that is represented and takes a value of zero when the actual axial position of the decoupling bearing device 32 matches the target position is associated.

In the following, two alternative embodiments of the operating device according to the invention or of the individual components of the operating device according to the invention will be described. In describing each embodiment, the same reference signs are used for one or more previously described embodiments for components that perform the same or similar functions. In that case, only the differences from one or more embodiments already described are mentioned. Otherwise, reference is made explicitly to the preceding description of one or more other embodiments. For the sake of distinction between the embodiments, reference numerals for both embodiments described below are given in FIGS.
4 is shown with a for the embodiment of FIG. 4 and b for the embodiments of FIGS.

FIG. 2 shows the operating cylinder structure unit 14a of the operating device according to the present invention. The operating cylinder construction unit likewise comprises a pneumatic ring cylinder 16a with a pneumatic ring piston element 22a. The cylinder chamber of the pneumatic ring cylinder 16a is sealed off by at least one packing ring 27a which takes effect between the pneumatic ring piston element 22a and the body member 20a of the operating cylinder structural unit 14a. The control valve structure unit 40a is detachably connected to the operation cylinder structure unit 14a via a flange. The control valve structure unit 40a has a control valve 42a provided with a valve casing 90a. The valve housing has three valve elements, as in the embodiment of FIG. 1, namely a first valve element 92a, a second valve element 94a, and a third or auxiliary valve element 96a. The valve casing 90a is movably mounted in a ring-shaped space 98a along a valve axis B parallel to the valve shaft 90. The control valve 42a has a pneumatic connection 48a. A pneumatic source 51a is connected to the pneumatic connection via a pneumatic conduit 50a.
Furthermore, the control valve has a hydraulic connection 54a. A clutch pedal device 60a is connected to the hydraulic connection via a hydraulic conduit 56a.

The hydraulic connection portion 54a is provided with a ring-shaped space 98a.
A hole 100a opening into the ring-shaped cavity 98a in the region of the cavity bottom 102a which defines (limits) the side far from the clutch. The pneumatic connection 48a has a hole 104a that opens into the ring-shaped cavity 98a in the region of the clutch-side end that opens towards the clutch.

The valve casing 90a is defined (limited) radially outward and radially inward by a plurality of radially spaced, coaxially extending ring-cylindrical walls of the valve casing 90a. Ring-shaped space 98a
Extends around a tube element 106a integral with the valve casing 90a, coaxial with the valve axis B and extending from the cavity bottom 102a in the direction of the clutch.
The tube element 106a does not extend as far toward the clutch as the remaining valve casing 90a. As a result, in the ring-shaped cavity 98a, a strictly ring-cylindrical cavity, that is, a cavity defined radially inward and radially outward, the cylinder is moved toward the clutch. Void portions that are confined radially outward but not radially inward are connected. The space portion is interpreted as a part of a space 98a called a ring-shaped space for convenience.

The axial hole 1 through the pipe element 106a
08a extends. The axial hole is open in the direction towards the clutch, and thus to the ring-shaped cavity 98a. The hole 108a has a hole 11 at the bottom of the space.
0a is connected, and the operating cylinder structural unit 1
Operating cylinder structural unit 1 that opens into the cylinder inner chamber of pneumatic ring cylinder 16a of 4a
The hole 112a in 4a connects. The plurality of holes described above may create pneumatic communication between the ring cavity 98a and the cylinder chamber of the pneumatic ring cylinder 16a.

The strictly cylindrical portion of the ring-shaped cavity 98a and the first valve element 92a form a hydraulic slave cylinder (Nehmerzylinder). For this purpose, the end of the first valve element 92a remote from the clutch is configured as a ring-cylinder-shaped hydraulic piston portion 114a. Hydraulic piston part 114
a is guided by two packing rings 116a and 118a in a strictly ring-cylindrical part of the ring-shaped cavity 98a so as to be movable (closed).

During operation of the clutch pedal device 60a, the first valve element 92a causes the hydraulic medium, especially the hydraulic medium, which flows into the cylinder chamber of the hydraulic slave cylinder and acts on the hydraulic piston 114a. Starting from the axial position corresponding to FIG. 3a, based on the pressure oil, it is moved towards the clutch. In this case, the axial position of the first valve element that is occurring at that time is shown in FIG.
4 shows the target position of the decoupling bearing device, which is not shown in FIG.

The first valve element 92a has a tube portion 120a connected to the hydraulic piston portion 114a in a direction toward the clutch. The tube part is a tube element 1
06a on the radial outside, and the tube element 106
The sealing ring (122a) in the ring-shaped groove (a) guides the pipe element 106a in a sealed manner (closely) near the clutch-side end of the pipe element. The first valve element 92a shown in FIG.
Position farthest from clutch (hydraulic piston 11
4a strikes or is directly adjacent to the cavity bottom 102a), the tube section 120a projects slightly beyond the tube element 106a towards the clutch. The tube section 120a then terminates at an end section 124a that extends radially and covers the inner chamber of the tube section 120a and thus the tube element 106a in the axial direction. The end portion is hereinafter referred to as a sealing portion (closing portion) 124a on the basis of the function described in more detail. FIG. 3a of tube section 120a
The portion protruding beyond the tube element 106a at the position is provided with four holes 126a extending in the radial direction. The hole is formed between the inside of the tube portion 120a and the tube portion 1
A communication between the area of the radially outer ring-shaped cavity 98a on the radially outer side of the pneumatic ring cylinder 16a and the tube section 120a is created.
(In this case, the second valve element 94a and the auxiliary valve element 96a have not yet been taken into account).

The second valve element 64a, which is also formed in a ring shape, is connected to the first valve element 9 having a ring shape.
2a surrounds the tube section 120a radially outward. The ring-shaped end portion 128a remote from the clutch is used as a stopper portion. At that end, the first valve element 92a may be bumped by the hydraulic piston portion 114a on the side closer to the clutch as a result of clutch pedal operation (see FIGS. 4a and 4b). Thereby, the limit of the axial movement range of the first valve element 92a towards the clutch, which varies with the axial position of the second valve element 94a, is reached. The end portion 128a carries a packing ring 130a in a ring-shaped recess. By the packing ring, the end portion 128a is movably guided by being hermetically sealed (closed by gas leakage) to a ring-shaped wall radially outside the ring-shaped space 98a. Between the end portion 128a of the second valve element 94a and the hydraulic piston portion 114a of the first valve element, a coil compression spring (Schraubendruckfeder) extending around the tube portion 120a of the first valve element 92a. 132a is provided. The coil compression spring is located at the position of the valve element corresponding to FIG.
The pressure load is applied when the hydraulic piston 114a and the hydraulic piston 114a do not hit each other, and when the hydraulic piston 114a hits the end portion 128a, the pressure is applied higher. I have. Thus, the compression spring 132a has a hydraulic piston 114a and an end portion 12 that are far less than the spacing of FIG. 3a and the spacing of FIGS.
8a has the effect of increasing the axial spacing.

The end portion 128 of the second valve element 94a
The ring-shaped or tubular-shaped portion 134a of the second valve element 94a is connected to a toward the clutch. This part is hereinafter referred to as the guide portion 134a, based on its ability to contribute to the compressed air guide inside the control valve, which will become apparent hereinafter. Guide part 134a
In the position of the second valve element 94a, which corresponds to FIG.
8a) in the position).
The valve casing 90 is formed from a ring-shaped cavity 98a which is not essential.
It protrudes toward the clutch beyond a.

The ring-shaped space 98 in the valve casing 90a
A ring-shaped recess for the packing ring 136a is provided in the ring-shaped wall portion defining a toward the outside in the radial direction. The ring-shaped recess, and thus the packing ring 136a, is offset towards the clutch with respect to the hole 104a used for the supply of the pneumatic medium. The packing ring 136a has an effect of guiding the guide portion airtightly in the ring-shaped space 98a. Guide part 13
Because there is some considerable radial spacing between the radially outer periphery of 4a and the ring wall of the valve casing 90a which limits the ring-shaped cavity 98a radially outwardly, the radial direction described above Outer radial peripheral surface 13
A ring chamber 140a is formed between 4a and the above-mentioned ring wall of the valve casing 90a. The ring room,
Packing ring 13 in the direction toward the clutch in the axial direction
6a (see FIG. 3b) and in the axial direction
2a in the direction towards packing ring 130a (FIG. 3b).
). The hole 104a opens into this ring chamber 140a which is variable in its axial extent based on the mobility of the second valve element 94a.

In the guide area 134a of the second valve element, in the transition region to the end 128a, but still on the clutch side of the packing ring 130a, the ring chamber 1 described above is provided.
A plurality of through holes 138a opening to 40a are provided. The through-hole is formed between the ring chamber 140a and the guide 1
A communication is created between the area radially inward of 34a and the annular cavity 98a of the end portion 128a on the axial clutch side. 3 and 4 show two such through holes 1.
38a can be seen. As long as the auxiliary valve element 96a is not taken into account, these through holes 13
Via 8a there is communication between the gas source 51a and the cylinder chamber of the pneumatic ring cylinder 16a. That is, the gas working conduit 50a and the gas working connection 4
8a, a hole 104a, a ring chamber 140a formed between the second valve element 94a and the valve casing 90a in the ring-shaped cavity 98a, a through hole 138a, a hole 126a in the tube portion 120a of the first valve element, The communication is made through a hole 108a in the pipe element 106a, a hole 110a in the cavity bottom 102a of the valve casing 90a, and a hole 112a in the operating cylinder structure unit 14a. Since the ring-shaped cavity 98a is open in the direction toward the clutch, the auxiliary valve element 96
If a was not present, there should also be a constant and constant communication between the cylinder chamber of the pneumatic ring cylinder 16a and the surrounding environment, and accordingly a communication between the gas source 51a and the surrounding environment. The result will be a constant flow of compressed air. Auxiliary valve element 96a, described in detail below, prevents such unwanted pneumatic communication between pneumatic source 51a and the surrounding environment. It also cooperates with the first valve element 92a and the second valve element 94a to realize switching between the three control states of the control valve already described in connection with the embodiment of FIG. As a result, the cylinder chamber of the pneumatic ring cylinder 16a is communicated with the gas source 51a (first control state).
Or communicated with the surrounding environment (second control state)
Or closed so as not to get gas (third control state).

The auxiliary valve element 96a, also configured as a ring element, is arranged radially between the guide part 134a of the second valve element and the pipe part 120a of the first valve element. In the axial direction, the auxiliary valve element extends beyond the seal 124a of the first valve element 92a towards the clutch and at its clutch-side end a ring-shaped projecting radially inward. It has an engaging portion 142a. The engagement portion is disposed corresponding to the first valve element, and in the case of a clutch operation, the first engagement of the first valve element as a result of the axial movement of the first valve element toward the clutch. The valve element 92a is engaged by its seal 124a, thereby entraining the auxiliary valve element 96a. At this time, the regions where the seal portion 124a and the engagement portion 142a abut each other at this time are in a sealed engagement (Dichteingriff) state that does not emit gas.

The auxiliary valve element 96a is provided at the end opposite to the engaging portion 142a corresponding to the first valve element, that is, at the end remote from the clutch, and this time the second valve It has another engagement portion 144a disposed corresponding to the element 94a. The engagement portion 144a is
Similarly, it is formed in a ring shape. The auxiliary valve element 96a is secured (eg, screwed or pinched) to its clutch-side end at a ring-shaped collar (Ringbund) adjacent to the engagement portion 144a and at the second valve element 94a. Ring portion 146a
A compression coil spring 148a surrounding the auxiliary valve 96a is interposed between the auxiliary coil 96a and the compression coil spring 148a. By the compression coil spring, the auxiliary valve element 96a is connected to the clutch side of the engagement portion 144a of the auxiliary valve element 96a corresponding to the second valve element and the end portion 128a of the second valve element 94a. It is prestressed in the direction in which the sides meet and engage. The seal portion 124a of the first valve element 92a has an engagement portion 142 disposed corresponding to the first valve element of the auxiliary valve element.
a, unless the auxiliary valve element is moved towards the clutch relative to the second valve element 94a against the force of the compression spring 148a.
Due to the action of the compression spring 148a, an engagement between the engagement part 144a of the auxiliary valve element and the end part 128a of the second valve element is created. that time,
The areas where the engagement portion 144a and the end portion 128a abut each other are in a gas-tight sealing engagement.

The ring portion 146a of the second valve element 94a has a packing ring 150a in a ring-shaped groove.
Is carried. By the packing ring, the auxiliary valve element 96a is movably guided so as not to get gas into the second valve element 94a. The engagement between the ring part 146a and the second valve element 94a is also airtight, so that the sealing part 124a of the first valve element 92a has a correspondingly arranged engagement of the auxiliary valve element 96a. When not engaged with the portion 142a, the ring chamber 15 defined by the tube portion 120a of the first valve element 92a and the auxiliary valve element 96a
2a is closed so as not to release gas to the surrounding environment. If the engagement portion 142a of the auxiliary valve element 96a corresponding to the first valve element and the seal portion 124a of the first valve element are not engaged with each other, the engagement portion 142a The defined ring-shaped opening 154a creates communication between the ring chamber 152a and the surrounding environment. The ring-shaped opening 154a is connected to the pressure compensating opening 7 of the control valve 42a.
0a is formed.

The ring chamber 152a between the auxiliary valve element 96a and the pipe section 120a of the first valve element 92a
Are constantly provided with holes 126a and holes 108a, 110a,
And 112a via the cylinder chamber of the pneumatic ring cylinder 16a. The ring chamber 152a has a hole 138a and a second valve element 94a.
Whether it is in communication with the pneumatic source 51a via the ring chamber 140a and the pneumatic connection 104a, 48a, 50a between the second valve element 94a and the valve casing 90a. Auxiliary valve element 9
It depends on the position of 6a. Auxiliary valve element 96a
Of the second valve element 94a correspond to the end portion 128 of the second valve element 94a.
(the seal portion 124a of the first valve element 92a is engaged with the engagement portion 142a of the auxiliary valve element 96a disposed correspondingly and the auxiliary valve element 96a is not engaged with the compression spring 148a. Only when you are dragging towards the clutch against the force)
The ring chamber 152a, and thus the cylinder chamber of the pneumatic ring cylinder 16a, is in pneumatic communication with the pneumatic source 51a (FIGS. 4a and 4b). Conversely, if the engagement portion 144a and the end portion 128a of the second valve element 94a are in the engaged state, the gas source 5
The gas communication between 1a and the cylinder chamber of the pneumatic ring cylinder 16a is interrupted, and the cylinder chamber of the pneumatic ring cylinder 16a is closed so as not to release gas (at the same time as the first). This is the case when the sealing part 124a of the valve element 92a is engaged with the correspondingly arranged engaging part 142a of the auxiliary valve element 96a: FIG. 3b) or
The ring chamber 152a, and thus the cylinder chamber of the pneumatic ring cylinder 16a, has a pressure compensation opening 70a.
(The seal portion 124a of the first valve element 92a is connected to the auxiliary valve element 96a
This is the case when it is not engaged with the correspondingly arranged engaging part 142a: see FIG. 3a).

With regard to the manner of operation of the control valve 42a, it is important that the second valve element 94a represents the axial position of the decoupling bearing device (not shown here) by its axial position. To this end, the second valve element 94a is connected without play by a fork-like (bifurcated) connecting part 160a integral with the second valve element 94a, on the clutch side of the pneumatic ring piston element 22a. Flange-like end part 16
2a. As a result, the second valve element 94a and the pneumatic ring piston element 22a are axially fixed (i.e., relatively stationary) and movably connected. Conversely, the axial position of the first valve element 92a is
It represents the axial target position of the interlock release bearing device. The difference between the actual position of the interlock release bearing device and the target position of the interlock release bearing device is represented by the relative positions of the first valve element 92a and the second valve element 94a with respect to each other. The quantity is associated. If the actual position of the disengagement bearing device coincides with the target position when disengaging the clutch (i.e., when disengaging the clutch), the first valve element 92a and the second valve element 9
4a occupy designated relative positions with respect to each other. That is, at the same time, the engagement portion 142a of the auxiliary valve element 96a and the seal portion 1 of the first valve element 92a
24a and the engaging part 1 of the auxiliary valve element 96a
The engagement between 44a and the end portion 128a of the second valve element 94a occupies a relative position in which it has been created. As a result, the pneumatic ring cylinder 16
The cylinder chamber of a is closed so as not to get gas (see FIG. 3b).

The manner of functioning of the control valve 42a becomes most apparent when the continuity of the control state during the operation of the clutch is observed. In the basic state where the clutch pedal device 60a is not operated,
The control valve assumes the state shown in FIG. 3a. In this basic state, the pneumatic ring cylinder 16a
Is in communication with the surrounding environment through the pressure compensation opening 70a. As a result, the ambient pressure (Umgebungsdruck) governs the cylinder chamber. Thus, external effects (eg, temperature) that would otherwise have caused unintended pressure fluctuations in the cylinder chamber are not a problem. Sealed piston (seal piston, Dichtkolbe
n) The engagement portion 144a of the auxiliary valve element 96a, which may also be referred to as n), comprises a disengagement stroke unit.
End portion 12 of the second valve element 94a, which may also be referred to as
8a, the compressed air of the gas acting source 51a is suppressed.

When the driver operates the pedal 62a, the first valve element 92a, also referred to as the pedal travel unit (Pedalwegeinheit), is moved toward the clutch (to the left in the figure). In so doing, the first valve element 92a entrains the auxiliary valve element 96a with respect to the second valve element 94a and thus disengages the engagement portion 144a of the auxiliary valve element against the force of the compression spring 148a. End portion 12 of the valve element 94a
First, before removing (disengaging) and moving towards the clutch 8a (FIG. 4a), a pneumatic communication between the pneumatic source 51a and the cylinder chamber of the pneumatic ring cylinder 16a is created. First, an engagement between the engagement portion 142a of the auxiliary valve element and the seal 124a of the first valve element 92a is created, i.e., of the pneumatic ring cylinder 16a via the pressure compensation opening 70a. The exhaust (ventilation) of the cylinder chamber is closed (FIG. 3b). In the state of FIG. 4a, compressed air may flow from the gas source 51a to the cylinder chamber of the pneumatic ring cylinder 16a. As a result, the pneumatic ring piston element 22a
Moves toward the clutch against the force of the diaphragm spring. In doing so, the pneumatic ring piston element 22a entrains the second valve element 94a by way of the coupling part 160a towards the clutch. As a result, the second valve element 94a also follows the stroke set by the first valve element 92a (FIG. 4b). Then, if the pedal 62a is not subsequently operated, the second valve element 94a will eventually reach the following axial position. That is, in the axial position, the seal portion 124a of the first valve element 92a is also connected to the correspondingly disposed engagement portion 142 of the auxiliary valve element 96a.
a, and the end portion 128a of the second valve element also has a correspondingly disposed engagement portion 144 of the auxiliary valve element 96a.
a so that the cylinder chamber of the pneumatic ring cylinder 16a is closed off from gas. The force balance between the diaphragm spring force on the pneumatic ring piston element and the force exerted on the pneumatic ring piston element by the compressed air in the cylinder chamber of the pneumatic ring cylinder 16a then governs. As a result, the pneumatic ring piston element 22
a, so that the decoupling bearing device is held in the reached axial position (see FIG. 3b).

When the clutch pedal 62a is partially or completely released (released), the compression spring 132a acting between the first valve element 92a and the second valve element 94a causes the first valve Element 92
a to the cavity bottom 102 with respect to the second valve element 94a.
It can be shifted toward a. As a result, the first valve element 9
The engagement between the seal portion 124a of 2a and the correspondingly disposed engagement portion 142a of the auxiliary valve element 96a is released. (If the clutch pedal 62a is only partially released, 3) Until this engagement is re-established, or until the basic state of FIG. 3a is again achieved (if clutch pedal 62a is completely released), the cylinder chamber of pneumatic ring cylinder 16a is Air is exhausted through the pressure compensation opening 70a. This is because in this situation the diaphragm spring of the clutch moves the pneumatic ring piston element 22a and thus the second valve element 94a away from the clutch towards the transmission (Getriebe) based on the exhaust of the cylinder chamber. This is because they can be moved.

A plurality of valve elements of the control valve are used to represent the actual axial position of the decoupling bearing device or the pneumatic ring piston element by the axial movement position of the second valve element and the first valve element. In contrast to the embodiment shown in FIGS. 1 to 4, which can be moved along the valve axis to represent the axial target position of the decoupling bearing device or the pneumatic ring piston element by means of the axial movement position of 5 to 9, the second valve element 9
4b, depending on the rotation state (rotation position) of the bearing device or the pneumatic ring piston element 22b
The first valve element 92b for representing the actual position in the axial direction of the first valve element 92 and for representing the target position of the decoupling bearing device or the pneumatic ring piston element 22b depending on the rotational state (rotational position) of the first valve element 92b. And the second valve element 94b
Are relatively rotatable (twisted) around the valve axis B '.

The valve casing 90b has a circular cylinder (cylindrical or cylindrical) through hole 180b. The through-hole extends coaxially with the valve axis B 'across the valve casing 90b, is open on both sides, and has both valve elements, namely the first valve element 9
2b and the second valve element 94b. A third or auxiliary valve element is not provided in this embodiment. As a result, the control state of the control valve is realized only by the first valve element 92b and the second valve element 94b.

The through hole 180b has three radial holes (radial holes) 182b, 184b, and 186b located on a common plane orthogonal to the valve axis B '. At this time, the radial holes 182b and 184b
, Between the radial hole 184b and the radial hole 186b, and between the radial hole 186b and the radial hole 182b, there are equal circumferential angular intervals with respect to the valve axis B '. And, the three radial holes, respectively,
Covers equally sized circumferential angle areas. In the view shown in FIG. 8, the three radial holes are clockwise 182b, 184b, and 186b along the perimeter of through hole 180b.
Are located consecutively in succession.

The radial hole 182b creates communication between the interior of the through hole 180b and the surrounding environment and is used as a pressure compensation opening 70b for the control valve. Radial hole 184
b is part of the pneumatic connection 48b, thereby creating pneumatic communication (gas communication) between the inner chamber of the through-hole 180b and the pneumatic source 51b via the pneumatic conduit 50b. The radial hole 186b has a hole 188b in the main body member 20b of the operation cylinder structure unit 14b.
Connect. Through this, a communication between the inner chamber of the through-hole 180b and the cylinder chamber of the pneumatic ring cylinder 16b is created (see FIG. 8). (The first valve element 92b has not yet been taken into account in these considerations.) Intersecting holes 190b and 19
2b is closed (sealed) with respect to the outside of the main body member 20b by a pressed sealing ball (closing ball) 194b.

The first valve element 92b has a through hole 18
0b has a main portion 198b in the form of a circular cylinder coaxial with the valve axis B '. The main part also has a circular cylinder-shaped through-hole 180b coaxial with the valve axis B '.
The pin portion (journal portion, Zapfenab) of the first valve element 92b protrudes to one side (left side in FIG. 7) from the
schnitt) 200b connects. The main portion 198b has a through hole 202b directed radially (radially) with respect to the valve axis B '. The through hole 202b is located on the same plane perpendicular to the valve axis B 'as the radial holes 182b, 184b, and 186b.

The first valve element 9 in the through hole 180b
The main portion 198b of the second portion 2b is formed by
The circumference of the second valve element 94b which fills (fills) the remaining ring chamber between the inner peripheral surface of the second valve element 94b and the inner peripheral surface of the second valve element 94b by a circular cylindrical ring-shaped portion 204b coaxial with the valve axis B '. being surrounded. The ring-shaped portion 204b has a second valve element disposed in the through-hole 180b in a direction toward the end of the through-hole 180b opposite to the pin portion 200b and having a radius substantially corresponding thereto. 94b
The circular wall parts are connected. The wall portion also has a circular cylinder-shaped pin portion (journal portion) protruding from the through hole 180b and coaxial with the valve axis B '.
208b connects. That is, the pin portion 200b of the first valve element protrudes on one side of the through hole 180b, and the pin portion 208b of the second valve element protrudes on the other side of the through hole 180b.

The ring-shaped part 204 of the second valve element
b has three through-holes 210b, 212b and 214b, which can be called slits or break-throughs (openings, Durchbrueche) in the shape of a slot (a slot). The through-holes respectively extend in the circumferential direction with respect to the valve axis B ′, and have radial holes 182b, 184.
b, and 186b and the through hole 202b, and are located on a plane orthogonal to the valve axis B '. Three through-holes 210b, 212 hereinafter referred to as breakthroughs
b and 214b respectively cover equal circumferential angles and are between breakthrough 210b and breakthrough 212b, between breakthrough 212b and breakthrough 214b, and between breakthrough 214b and breakthrough 210b. Are the same size. The circumferential angle covered by the breakthrough is approximately 95 °, while the spacing circumferential angle between these breakthroughs is approximately 25 °. Radial holes 182b,
184b, 186b, through-hole 202b, and breakthroughs 210b, 212b, 214b each extend in the axial direction into the same axial region of the control valve, as best seen in FIG.

On the outer peripheral surface of the ring-shaped portion 204b of the second valve element 94b, breakthroughs 210b,
Packing rings 216b on both sides of 212b, 214b
The main part 198b of the first valve element 92b is provided with a packing ring 218b that is positioned so as to be shifted toward the pin part 200b with respect to the through hole 202b. These packing rings 216b and 218b
Are radial holes 182b, 184b, and 186b, through holes 202b, and breakthroughs 210b, 212.
b, and 214b, the axial region between the packing rings 216b of the through hole 180b
Used to seal off gas from both open ends of 80b. Further, the second valve element 94b, which can be recognized in FIG.
b by means of its main part 198b
A snap ring (Spring ring) is provided to be fixed inside the ring-shaped portion 204b of 4b.

The two valve elements 92b and 94b are
It can be twisted (relatively rotatable) with respect to each other only to a limited extent. This is because two pins 220b are provided on the axial end face of the main portion 198b of the first valve element 92b on the side opposite to the pin portion 200b in a radial direction with respect to the valve axis B '. Because it is. The pin 2
20b is a wall portion 206b of the second valve element 94b.
(See FIGS. 7 and 9). Based on the dimensioning of the cavity 222b, the relative twistability (relative rotation possibility) of both valve elements is approximately 75 °
Enabled over an angle range of ８０80 °.

Both valve elements 92b and 94b are
With breakthroughs 210b, 212b, and 214b, through holes 202b, pins 220b, and voids 222
b, the through-hole 202b is in communication with the breakthrough 214b on one side and the breakthrough 210b on the other side, or on the other side, in any possible relative rotational position of both valve elements It is configured to be in communication with 212b or to be gas tightly closed by a portion 224b forming a seal and control between both breakthroughs 210b and 212b. . At this time, the breakthrough 210b is constantly in communication with the pressure compensation opening 70b, the breakthrough 212b is constantly in communication with the gas source 51b through the hole 184b, and the breakthrough 214b is in communication with the hole 186b. And is constantly in communication with the cylinder chamber of the pneumatic ring cylinder 16b.

The second valve element 94b has exactly one of the second valve element 94b in the axial position (with respect to the clutch axis) of the pneumatic ring piston element 22b and thus of the decoupling bearing device. Pneumatic ring piston element 22b so that the two rotational states (rotational positions) are associated
It is motion-coupled with (linked). For this purpose, the curved body 226b is fixed to the pin portion 208b of the second valve element 94b in a rotationally fixed manner (that is, so as not to rotate relatively). The curved body has a pin portion 2
A coil spring (see FIGS. 5 and 7) that surrounds and engages the curved body 226b and the valve casing 90b to prestress the flanged end portion 162b of the pneumatic ring piston element 22b. Have been. At this time, the curved body 226b
Engages the end portion 162b on the side remote from the clutch.

A lever 230b is rotatably fixed to the pin portion 200b. The lever, together with the piston rod 232b of the cylinder-piston device 234b, forms a two-part toggle lever (bell crank lever). Cylinder / piston device 23
As 4b, consider a hydraulic slave cylinder which is in communication with the clutch pedal device 60b via a connection 54b and a hydraulic conduit 56b. Piston rod 232b
The piston 236b attached to the slave cylinder 23 is hydraulically driven by a coil compression spring 238b.
4b is prestressed in a direction to reduce the cylinder chamber.

The hydraulic slave cylinder 234b is
It is configured as a structural unit (package unit) together with the valve casing 90b. A toggle lever arrangement comprising a lever 230b and a piston rod 232b provides a displacement movement of the piston 236b for the first valve element 92b.
It is used to convert to rotational motion. Piston 23
6b, the first valve element 92
Exactly one rotation state (rotation position) of b is made to correspond.

[0095] The clutch pedal 62b of the clutch pedal device 60b is not pressed and the pneumatic ring piston element 22b is not disengaged.
Accordingly, in the basic state (basic position) of the control valve, which occupies the axial position furthest from the clutch, the through hole 202 in the main portion 198b of the first valve element 92b.
b, the opening opposite to the breakthrough 214b is
The seal unit and the control unit 224b are disposed so as to substantially face the pressure compensation opening 70b.
8 with some holes 184b clockwise with respect to FIG.
Is shifted toward. The other opening of the through hole 202b faces the breakthrough 214b, and thus the ring-shaped portion 2 of the second valve element 94b.
04b, breakthrough 214b breakthrough 2
It is not closed by a portion 240b that separates from 12b. Thereby, in the above-mentioned basic state, between the cylinder chamber of the pneumatic ring cylinder 16b and the pressure compensation opening 70b, ie, the holes 192b, 190
b, 186b, breakthrough 214b, through hole 202
b and permanent exhaust communication (ventilation communication) via breakthrough 210b. At this time, the gas action source 51b
Is suppressed by the seal / control unit 224b and the portion 240b of the ring-shaped portion 204b of the second valve element 94b.

When the clutch pedal 62b is operated by the driver, the exhaust opening 70 of the through hole 202b is used.
a first valve element 92b having an opening substantially facing b (also referred to as a pedal travel unit)
Are twisted toward the hole 184b forming the compressed air inlet. At this time, by passing through the seal / control unit 224b forming a control edge between the breakthrough 210b and the breakthrough 212b, first, the seal / control unit 224b closes the through hole 202b. The exhaust is thereby closed, and then the cylinder chamber of the pneumatic ring cylinder 16b and the gas source 51
b, ie, hole 184b, breakthrough 21
2b, through-hole 202b, and holes 186b, 188b, 1
Ventilation communication is created via 90b and 192b. When the compressed air flows into the cylinder chamber, the pneumatic ring piston element 22b moves toward the clutch against the force of the diaphragm spring. In so doing, the second valve element (which can be referred to as a decoupling stroke unit) responds to the rotation angle set by the first valve element. During the supply of compressed air to the cylinder chamber of the pneumatic ring cylinder 16b, the supplied compressed air flows out of the pressure compensating opening 70b, and the sealing / control unit 224b and the second valve element 94b
Of the ring portion 204b of the first and second portions of the ring portion 204b separating the breakthrough 214b from the breakthrough 210b.

If the clutch pedal is held in the reached operating position, the seal / control unit 224b will again return to the main part of the first valve element 92b upon achieving the rotation angle set by the first valve element. The through hole 202b at 198b is closed. As a result, the compressed air supply is cut off, and the pneumatic ring cylinder 16b
Exhaust communication between the cylinder chamber and the pressure compensation opening 70b is also not created. At this time, the force applied to the pneumatic ring piston element 22b by the diaphragm spring and the compressed air in the cylinder chamber of the pneumatic ring cylinder 16b cause the pneumatic ring piston element 2
The equilibrium of the forces between the forces exerted on 2b governs.

When the clutch pedal 62b is released again, the first valve element 92b is released from the spring (spring).
It is twisted in the opposite direction based on the elastic force (spring force) exerted on the piston 236b by the 238b. as a result,
Again, exhaust communication between the pressure compensating opening 70b and the cylinder chamber of the pneumatic ring cylinder 16b is created, and the second valve element 94b
Under the appropriate twist (relative rotation) of
The ring piston element 22b is displaced (pushed) away from the clutch toward the transmission by the force of the diaphragm spring.

As will be clear from the above description, in the case of the embodiment described with reference to FIGS. 5 to 9, the target of the pneumatic ring piston element 22b and thus of the decoupling bearing device is described. The position and the instantaneous actual position of the pneumatic ring piston element 22b, and thus of the decoupling bearing device, depend on the first valve element 92b or the second valve element 9
This is represented by the rotation state (rotational position) of 4b. In other words, the first valve element represents the amount of guidance by its rotational position, and the second valve element represents the actual amount by its rotational position. Based on the actual quantity, the control valve switches between the control states generally described in connection with FIG. In this case, the difference quantity represented by the relative rotational position of the two valve elements with respect to one another can be associated with the guidance quantity and the actual quantity.

In order to realize a control state by closing or opening the pressure medium communication in the control valve, a plurality of twistable (relatively rotatable) valves representing a guide amount, an actual amount, and a difference amount depending on a rotational position. It should be kept in mind that having an element would also be able to work with a particularly similarly twistable auxiliary valve element that cooperates with the first and second valve elements. Would. Conversely, in the case of a control valve having a plurality of valve elements which can be moved along the valve axis to represent the guiding quantity, the actual quantity and the difference quantity, it may also be actuated by only two valve elements. That is, one of the two valve elements is configured with a control edge that switches between two selectable pressure medium connections or closes a pressure medium path common to both pressure medium connections. As a result, there is no need to provide an additional auxiliary valve element that can be moved along the valve axis.

The principle of operation of a control valve having a plurality of valve elements which are rotatably arranged and which represent the above-mentioned quantity by a rotational position, comprises a plurality of movably arranged and which represent the above-mentioned quantity by a displacement position. The diversion possibility to a control valve with a valve element (or vice versa) is described in the embodiment of FIGS.
It becomes particularly clear when compared with the embodiment of FIG. In the embodiments of FIGS. 10 and 11, the same reference numerals are used extensively as in the embodiments of FIGS. Here, for the sake of distinction, the reference numerals for the embodiments of FIGS. 10 and 11 are characterized by the letter "c". With respect to the embodiment of FIGS. 10 and 11, the above description of the embodiment of FIGS. Only the differences between the two embodiments are described.

The control valve 42c has two valve elements, that is, a first valve element 92c and a second valve element 94c, disposed in the valve casing 90c, just like the control valve 42b. In contrast to the embodiments of FIGS. 5 to 9, these valve elements are movable along the valve axis B "and, depending on the position of movement or axial position, the guiding amount, the actual amount and the difference amount. In this regard, reference can be made to the embodiments of FIGS.

The control valve of FIGS. 5 to 9 is very similar to the control valve of FIGS. 10 and 11 in that the control valve of FIGS. It can be seen that this essentially corresponds to the "exploded view"("Abwicklung") of the control valve of FIGS. Therefore, the valve element 92
Corresponding rotation positions of valve elements 92b and 94b may be associated with respective axial positions of c and 94c.

The valve element 90c has a circular cylindrical space 180c coaxial with the valve axis B ". In this space, the second valve element 94c is movably accommodated along the valve axis B". Have been. The second valve element 94c similarly has a circular cylindrical space 300c coaxial with the valve axis B ". In the space, the first valve element 92c having the control unit 302c is provided with the valve axis B. ″. The first valve element 92c has a portion 200c projecting from the valve casing 90c and receiving (measuring, recording) a guide quantity. Second valve element 9
4c has a portion 208c projecting from the valve casing 90c on the opposite side to receive the actual quantity.

The valve casing 90c has three holes 182c, 186c, and 184c that are offset from each other in the axial direction (the direction of the valve axis B ″).
These holes are in this order from section 200c to section 208
It is located one after the other in the direction to c. The axial distance between the hole 182c and the hole 186c is
84c. These holes are
It is oriented radially (radially) with respect to the valve axis B "and opens into a cavity 180c in the valve casing 90c. The holes 182c, 184c, 186c are also offset relative to one another in the circumferential direction. However, this is less important with respect to the function of the control valve and is only useful for constructing the control valve into a structure which is short in the axial direction.

The second valve element 94c has three breakthroughs 210c, 214c, and 2 that are offset from each other in the axial direction (the direction of the valve axis B ″).
12c. In doing so, these breakthroughs
They are located one after the other in the order mentioned in the direction from the part 200c to the part 208c. Each of the above-mentioned breakthroughs is formed by a vertically elongated cavity extending in the axial direction and a hole located further inward in the radial direction and provided at the axial center of the cavity. As a result, the second valve element 94c is formed by the elongated space and the hole.
Can be created between the outside room and the empty space 300c provided therein. At each axial position of the second valve element 94c, a breakthrough 210c
82c, breakthrough 214c opens into hole 186c, and breakthrough 212c opens into hole 184c.
This is because the respective longitudinal cavity of the relevant breakthrough covers the relevant hole in the valve housing radially inward. Thereby, if the first valve element 92c is not taken into account, the holes 182c, 1
There is communication between 86c and 184c and the cavity 300c inside the second valve element 94c, and thus communication between the holes.

Control section 302 of first valve element 92c
c is used to open and close the communication between the holes 182c, 186c and 184c depending on the axial relative position of both valve elements. To this end, the controller 302c has two seals 306c and 308c, each forming a control edge. These seals indicate that they have respective breakthroughs 210
c or 212c as long as they cover the radially inner holes of the second valve element 94c.
Close to 00c.

The control portion 302c of the first valve element 92c has a ring-shaped space opened radially outward forming a ring channel (ring-shaped groove) 202c between the two seal portions 306c and 308c. . The ring channel 202c opens at least in all axial positions of the two valve elements with respect to one another to the breakthrough 214c and thus to the bore 186c leading to the pressure medium and power cylinder device.

Depending on the axial position of both valve elements with respect to each other, the ring channel 202c
Only towards breakthrough 214c, and thus hole 18
6c, or additionally to the breakthrough 212c, and thus also to the hole 184c leading to the pressure medium supply, or to the breakthrough 210c.
c, and thus also into a hole 182c used as a pressure compensation opening 70c.

In the basic state shown in FIG. 11a of the control valve, with the clutch disengaged, there is exhaust communication between hole 186c and hole 182c via ring channel 202c. When the first valve element 94c is moved to the left in the view of FIG. 11 in response to an increasing amount of guidance, for example based on clutch pedal operation, the control valve via the breakthroughs 212c, 214c and the ring channel 202c Until the pressure medium communication between the holes 186c and 184c in the casing 90c is created and the pressure medium is supplied to the power cylinder device,
Before the seal portion 308c, which closed the radially inner hole of the breakthrough 212c in the basic state, moves past the radially inner hole, firstly, the breakthrough 2
The radially inner hole 10c is closed by the seal portion 306c. FIG. 11b shows the control valve in maximum clutch operation. In this situation, such pressure medium communication between holes 184c and 186c has been created.

In the case of a non-maximum clutch operation, when the actual quantity is equal to the guiding quantity, both valve elements occupy the following axial position with respect to one another: That is, this is a relative position where the seal portion 306c closes the hole inside the breakthrough 210c in the radial direction, and the seal portion 308c closes the hole inside the breakthrough 212c in the radial direction. As a result, there is no pressure medium communication between the pressure medium / power cylinder device on one side and the pressure compensation opening 70c and the hole 184c leading to the pressure medium supply (i.e., the pressure medium / power cylinder). There is no communication between the power cylinder device and the pressure compensation opening 70c, nor between the pressure medium / power cylinder device and the hole 184c).

Apart from the mentioned holes and breakthroughs in the valve casing 90c and in the second valve element 94c, the valve casing and both valve elements 92c and 94c are essentially rotationally symmetric with respect to the valve axis B ''. (Rotationally symmetric), except that
Rotational position fixing means, not shown in the drawing, are provided. The rotation position fixing means disables relative rotation between the second valve element 94c and the valve casing 90c.
As a result, it is always ensured that breakthrough 210c opens into hole 182c, breakthrough 214c opens into hole 186c, and breakthrough 212c opens into hole 184c. In order to keep the control valve short in the axial direction, holes 182c, 186c and 184c are provided and breakthroughs 210c, 214c and 21 correspondingly.
2c are also offset relative to one another in the circumferential direction (with respect to the valve axis B "), in addition to their mutual offset in the axial direction, as already mentioned. In principle, the holes 182c
186c and correspondingly breakthrough 210c
The "stretch"("") 214c in the axial direction such that the longitudinally extending longitudinal cavity of the breakthrough no longer covers (overlaps) in projection onto the valve axis B ".
auseinanderziehen "). As a result, a plurality of ring channels in the form of a ring channel 202c may be provided on the outer periphery of the second valve element 94c instead of the elongated cavity. As is the case with the second valve element 94c (in the embodiment shown in FIGS. 10 and 11), the second valve element 94c moves to an arbitrary rotational position (rotation state) relative to the valve casing 90c. May occupy.

In summary, the invention relates to an operating device for a friction clutch arranged in a casing bell between an internal combustion engine and a transmission in a power train of a motor vehicle. The operating device is an interlock release bearing device, and a positioning servo device (Pos Pos) having a pressure medium / power cylinder device for the interlock release bearing device.
itionierservoanordnung). The positioning servo device has a control valve in communication with a pressure medium source. The control valve is a valve device that can be switched between at least two control states depending on an actual amount representing an axial position of the decoupled bearing device and a guide amount representing a target position of the decoupled bearing device. Have. In the first control state, the pressure medium
It is in pressure medium communication between the power cylinder device and the pressure medium source. In the second control state, there is a pressure medium communication state between the pressure medium / power cylinder device and the pressure compensation opening. The valve device comprises two valve elements that can move relative to each other and relative to the valve casing. In this case, relative to the valve casing, the guiding amount depends on the position of the first valve element of the two valve elements, and the actual amount is determined by the position of the first of the two valve elements. Represented by the position of the second valve element. The difference quantity associated with the actual quantity and the guidance quantity is represented by the position of the two valve elements relative to each other.

[Brief description of the drawings]

FIG. 1 shows a diagrammatic and partially sectional view of an operating device according to the invention having a pressure medium / ring cylinder, in particular a pressure medium / power cylinder device in the form of a pneumatic ring cylinder. is there.

2 shows a part of a pressure-medium power cylinder device with a control valve connected via a flange of another operating device according to the invention, which corresponds to the operating device shown in FIG. 1 with only slight modifications. FIG. 2 is a perspective view schematically shown in a sectional view.

3 is a sectional view of a pressure medium / ring cylinder of a pressure medium / power cylinder device having the control valve shown in FIG. 2, particularly a part of a pneumatic ring cylinder and a control valve. In (a), the control valve and the pressure medium power cylinder device are shown in a basic state of the operating device without clutch operation. (B) shows one of a series of different positions and states of the control valve and the pressure medium / power cylinder device during operation of the operating device for disengagement of the clutch.

4 is a cross-sectional view of a pressure medium / ring cylinder of the pressure medium / power cylinder device having the control valve shown in FIG. 2, particularly a part of a pneumatic ring cylinder and a control valve. (A), (b) is a continuation of FIG. 3 (b) of the sequence of different positions and states of the control valve and the pressure medium / power cylinder device during operation of the operating device for disengagement of the clutch. The figure is shown.

FIG. 5 shows a pressure medium with a control valve joined via a flange according to another embodiment of the operating device according to the invention.
It is a perspective view of a power cylinder device.

6 is a perspective view of a part of the control valve and the pressure medium / power cylinder device shown in FIG. 5 as viewed from another direction, and is partially shown in a sectional view.

7 shows the pressure medium and ring cylinder of the pressure medium and power cylinder device shown in FIG.
It is sectional drawing by I-VII.

8 is a sectional view of a part of the pressure medium / power cylinder device and the control valve shown in FIG. 5, taken along line VIII-VIII in FIG. 7;

9 is a sectional view of the control valve shown in FIG. 5, taken along line IX-IX in FIG. 7;

FIG. 10 is a perspective view, partially in section, of another embodiment of the control valve according to the invention, which corresponds to the control valve of the embodiment shown in FIGS. It is.

FIG. 11 (a) is a cross-sectional view of a portion of the control valve shown in FIG. 10 corresponding to the cross-sectional view shown there, in a basic state position without a clutch operation. (B)
FIG. 4 is a sectional view at an operation position for clutch operation.

[Explanation of symbols]

 10, 10b Operating device 12 Casing bell 14, 14a, 14b Operating cylinder structure unit 16 Pneumatic ring cylinder 32 Interlock release bearing device 40 Control valve structure unit 42, 42a, 42b, 42c Control valve 48a Pneumatic connection 51, 51a, 51b Gas action source 54 Connection 54a Hydraulic connection 60, 60a Clutch pedal device 64 Gas action conduit 70, 70a, 70b, 70c Pressure compensation opening 72 Connection element 74 Connection element 76 Connection 90a, 90b, 90c Valve Casing 92a, 92b, 92c First valve element 94a, 94b, 94c Second valve element 96a Auxiliary valve element 98a Ring-shaped cavity 100a Hole 102a Vacancy bottom 104a Hole 106a Tube element 108a Axial Hole 110a Hole 114a Hydraulic piston part 116a Ring-shaped packing 118a Packing element 120a Pipe part 122a Packing element 124a Seal part 126a Hole 128a End part of second valve element 132a Coil compression spring 138a Through hole 140a Ring chamber 142a Engagement part 144a Engagement part 148a Compression coil spring 150a Packing ring 152a Ring chamber 154a Ring opening 160a Connection part 162a, 162b Flange-like end part 180b Through hole 180c Vacancy 182b, 182c Radial hole 184b, 184c Radial hole 186b 186c Radial hole 202b Through hole 202c Ring channel 204b Ring-shaped portion of second valve element 206b Second Valve element wall portion 208b Pin portion 210b, 210c Breakthrough (through space) 212b, 212c Breakthrough (through space) 214b, 214c Breakthrough (through space) 216b Packing element 218b Packing element 220b Pin 222b space 224b Seal / control unit 226b Curved body 230b Lever 232b Piston rod 234b Cylinder / piston device 236b Piston 238b Coil compression spring 306c Seal portion 308c Seal portion A Clutch axis, power cylinder apparatus axis B, B ', B "Valve axis

Continued on the front page (72) Inventor Jörg Wiert Germany Day 97422 Schweinfurt Groilstraße 6 (72) Inventor Thomas Otto Germany Day 97469 Van Gogh Sheim am Zetzen 104

Claims (68)

[Claims] 1. An operating device (10) for a friction clutch arranged on a casing bell (12) between an internal combustion engine and a transmission in a power train of a motor vehicle, in particular a useful motor vehicle, A decoupling bearing device (32) that is moved essentially coaxially with the friction clutch for operation of the friction clutch, and a pressure medium and power cylinder device (14) acting on the decoupling bearing device (32). Yes, pressure medium source (5
The guide amount indicating the target position and the interlocking release bearing device (3) are controlled by the control valve (42) connected to the control valve (1).
The pressure medium / power cylinder device (1) which can be operated depending on the actual quantity representing the axial position of (2).
4) A control device (10) comprising a positioning servo device having a pressure medium, essentially concentric with respect to the clutch axis.
Said pressure medium and power cylinder device (14) comprising a ring cylinder (16) is arranged in said casing bell (12), preferably with a force essentially coaxial to the clutch axis (A). The control valve (42) connects the pressure medium / power cylinder device (14) to the pressure medium source (51). A valve device adjustable between one control state and a second control state communicating said pressure medium and power cylinder device (14) to a pressure compensation opening (70). A device is switchable between the two control states depending on a difference amount associated with the actual amount and the guidance amount, the valve devices being relative to each other and to a valve casing. phase Manner movable two valve elements (92
a, 94a, 96a; 92b, 94b),
Also, the actual amount depends on the position of the first valve element (92a; 92b) of the two valve elements, and the actual amount is the second valve element (94a; 94b) of the two valve elements. Of the valve casing (40; 90a; 90b), and the difference is represented by the two valve elements (92a, 94a; 92b, 94b).
Said operating devices are represented relative to each other by the position of 2. An operating device (10) for a friction clutch arranged in a casing bell (12) between an internal combustion engine and a transmission in a power train of a motor vehicle, in particular of a useful motor vehicle. A decoupling bearing device (32) which is moved essentially coaxially with the friction clutch for the operation of the friction clutch, and a pressure medium and power cylinder device (14) acting on the decoupling bearing device (32). , Pressure medium source (5
The guide amount indicating the target position and the interlocking release bearing device (3) are controlled by the control valve (42) connected to the control valve (1).
The pressure medium / power cylinder device (1) which can be operated depending on the actual quantity representing the axial position of (2).
An operating device (10) including a positioning servo device having 4), wherein the control valve (42) connects the pressure medium / power cylinder device (14) to a pressure medium source (51). A valve device adjustable between a first control state in which the pressure medium and the power cylinder device (14) communicates with the pressure compensation opening (70). The valve device is switchable between the two control states depending on a difference amount associated with the actual amount and the guide amount. Two valve elements (92
a, 94a, 96a; 92b, 94b), and
The guide amount is determined by the position of the first valve element (92a; 92b) of the two valve elements.
The actual quantity is expressed relative to the valve casing (40; 90a; 90b) by the position of the second valve element (94a; 94b) of the two valve elements; The operating device as described above, wherein the quantity is expressed relative to each other by the position of the two valve elements (92a, 94a; 92b, 94b). 3. The valve device is adjustable to a third control state as a function of the difference amount, wherein the pressure medium / power cylinder device has essentially no pressure medium in the third control state. The operating device according to claim 1, wherein the operating device is closed. 4. The control valve (42), in particular a first signal connection (54) for receiving a guidance signal giving the guidance amount from a clutch pedal device (60), and the disengagement bearing device (32). ) And a second signal connection (76) for receiving an actual value signal giving said actual amount from a transmitter element device (72) associated with said second element. The operating device according to item 1. 5. The guide signal, wherein the guide signal and the actual value signal each act directly on exactly one of the two valve elements independently of the other signal, respectively. One valve element (9
Operating device according to claim 4, characterized in that it acts directly on 2a; 92b) and the actual value signal acts directly on the second valve element (94a; 94b). 6. The method according to claim 6, wherein the actual value signal is a pressure, a volume,
A hydraulic, pneumatic, mechanical or electrical signal, represented by force, stroke, angle, current intensity or voltage, and, if necessary, the second signal connection ( The operating device according to claim 4 or 5, wherein a converter means for changing the actual value signal into the actual amount is added to (76). 7. A mechanical position adjustment, wherein said positioning servo device has a mechanically connected or connectable transmitter element (72) for directly or indirectly detecting the position of said decoupling bearing device (32). Means (42, 64, 16, 72, 7
The operating device according to claim 1, wherein the operating device includes 4). 8. The transmitter element (7)
2; 160a; 226b) acting on said second valve element (94a; 94b), in particular being or movably coupled thereto.
The operating device according to claim 7. 9. The second valve element (94a)
If necessary, the decoupling bearing device or the decoupling bearing device-side part (162a) of the pressure medium and power cylinder device (14a) is preferably connected via a coupling element (160a) integrated therewith. 9. The operating device according to claim 8, wherein the operating device is fixedly connected or can be fixedly connected. 10. The second valve element (94b).
Are preferably fixedly connected to this, and if necessary, are integrated therewith so that the decoupling bearing device or the decoupling bearing device side part (162b) of the pressure medium power cylinder device (14b) Operation according to claim 8, characterized in that it is connected to, or can be connected to, a pre-stressed or pre-stressable connecting element (226b) towards apparatus. 11. The guide signal may comprise, in particular, pressure, volume,
A hydraulic, pneumatic, electrical or optical signal represented by force, stroke, angle, current, voltage, or light intensity, and, if necessary, the first signal connection ( 5. The method according to claim 1, wherein said control means includes means for converting said guide signal into said guide quantity. Operating device. 12. The transducer means for the conversion of pneumatically or hydraulically guided signals is preferably a resilient prestressed piston (114a; 236b).
12. The piston according to claim 11, characterized in that the piston is preferably connected to or can be connected to, in particular integrated with, the first valve element (92a; 92b). Operating device. 13. The valve device according to claim 12, wherein the valve device is provided in the valve casing.
0a) with an auxiliary valve element (96a) movable relative to said first valve element (92a) to provide at least one of said control states. Alternatively (and) cooperating with a second valve element (94a),
An operating device according to any one of the preceding claims. 14. The auxiliary valve element (96a) has an engagement portion (142a) disposed corresponding to the first valve element (92a), and the auxiliary valve element (96a) For the purpose of entrainment or / and to interrupt at least one pressure medium communication in the control valve (42a), in particular the pressure medium / power cylinder device (14a) and the pressure compensation opening (70a) In order to shut off the pressure medium communication between
Operating device according to claim 13, characterized in that the first valve element (92a) engages 2a). 15. The auxiliary valve element (96a)
An engagement portion (144a) arranged corresponding to the second valve element (94a) for entrainment of the auxiliary valve element (96a) or (and) 42a) to interrupt at least one pressure medium communication, in particular to interrupt pressure medium communication between the pressure medium source (51a) and the pressure medium and power cylinder device (14a), or (And) the pressure medium source (51a) and the pressure compensation opening (70);
a) in order to close the pressure medium communication possible in principle, if necessary, in principle.
15. The operating device according to claim 13, wherein the second valve element (94a) is engaged with the operating member. 16. Prestressing means, in particular said second valve element (94a) and said auxiliary valve element (96).
a) prestressing means (148)
a), said second valve element (9)
4a) in the direction of engagement with the correspondingly arranged engaging part (144a) of the auxiliary valve element or / and the first valve element (92a) is in the corresponding arrangement of the auxiliary valve element (96a). The prestressing means prestresses the auxiliary valve element (96a) in the direction of engagement with the engaged engagement portion (142a). Operating device. 17. The first valve element (92a) and the second valve element (94a) and, if necessary, the valve casing (90a) extend the range of movement of both valve elements relative to each other. At least one of the valve elements (92a), if necessary, in order to limit the range of movement of the valve element (92a) relative to the valve casing (90a). Operating device according to any one of the preceding claims, characterized in that it has one stop or engaging part (102a, 114a, 128a). 18. When the correspondingly disposed stopper portions (114a, 128a) of said first valve element (92a) and said second valve element (94a) are in contact with each other, Pressure medium communication in the control valve (42a) is created, in particular pressure medium communication between the pressure medium source (51a) and the pressure medium and power cylinder device (14a). The operating device according to claim 17,. 19. A method as claimed in claim 1, characterized in that a prestressing means (132a) for effecting between the first valve element (92a) and the second valve element (94a) is provided. The operating device according to any one of the above items. 20. The stress of the prestressing means (132a) which takes effect between said first valve element (92a) and said second valve element (94a) is reduced by said first valve element (92a). 20. The method according to claim 19, wherein the at least one stop part (114a, 128a) of the second valve element (94a) is in contact with one another. Operating device. 21. A valve element (9) of one of said elements: a first valve element (92b; 92c) and a second valve element (94b; 94c).
4b; 92c), especially the second valve element (94b)
Has at least one part (22) forming a control edge.
4b; 306c, 308c), said parts being at least three pressure medium openings (70b, 184b, 202b) in said further valve element (92b; 94c) and in said valve casing (90b; 90c).
210c, 212c, 214c) and especially the pressure medium opening (20) in said further valve element (92b).
2b) and the two pressure medium openings (70b, 184b) in the valve casing, the one valve element moves in one direction relative to the other valve element. At least one control edge (224b; 306c, 308c) is provided in at least one relative position of the two valve elements (92b, 94b; 92c, 94c) with respect to one another. In particular, by moving past the pressure medium opening (202b) in the further valve element (92b), the first pressure medium communication in the control valve, in particular the pressure medium source (51b ) And said pressure medium / power cylinder device (14b) to interrupt or create pressure medium communication; Control valve (42b; 42c) further pressure medium communication in, in particular the pressure compensating opening (70b; 70
c) and the pressure medium / power cylinder device (14b)
Operating device according to any of the preceding claims, characterized in that it creates or shuts off pressure medium communication between the operating device and the pressure device. 22. The valve element, that is, one of the first valve element (92b) and the second valve element (94b), in particular, the first valve element (92b) has at least one In particular, it has a pin-shaped engagement part (220b), which engages in a correspondingly arranged slit-shaped cavity (222b) of said further valve element (94b), said two valve elements A device according to any one of the preceding claims, characterized in that the cavity (222b) is limited at both ends by stoppers in order to limit the range of movement of the (92b, 94b) with respect to each other. Operating device. 23. The pressure control opening (70) is connected to the pressure medium / power cylinder device (1) when the control valve (42) is in the basic state of the operating device without clutch operation.
An operating device according to any of the preceding claims, characterized in that it occupies a control state in communication with (4). 24. The first valve element (92a) and the second valve element (94a) and, if necessary, an auxiliary valve element (96a) are connected to the valve casing (9).
0a) movably mounted along the valve axis (B) in the cavity (98a), the actual quantity and the guide quantity being represented by the axial position of the respective valve element (92a; 94a). An operating device according to any one of the preceding claims, characterized in that: 25. Of said elements, a first valve element (92a) and a second valve element (9)
4a) and, if necessary, the auxiliary valve element (96a).
6a) is configured at least in part as a ring element which is coaxial with the valve axis and at least one further of these valve elements (9)
25. Operating device according to claim 24, characterized in that it surrounds 2a; 92a, 94a) at least regionally radially outside. 26. The cavity of claim 28, wherein the cavity is a ring cavity having a ring-cylindrical wall extending coaxially at radially spaced intervals, and Extending around a tube element (106a) extending coaxially with the valve axis (B), which is fixed with respect to the valve casing (90a) and preferably integral therewith, the tube element being in the region of its free end In particular, an axially open pressure medium through-opening (108a) is connected to the control valve (42).
a) as part of at least one pressure medium communication in
In particular, pressure medium communication between the pressure medium / power cylinder device (14a) and the pressure medium source (51a) or / and the pressure medium / power cylinder device (14)
25. The pressure-measuring device according to claim 24, comprising a part of the pressure-medium communication between a) and the pressure-compensating opening.
Or the operating device according to claim 25. 27. The first valve element (92a) has a ring-shaped part (114a), said ring-shaped part surrounding the pipe element (106a) at least in a radially outward manner, preferably At least one ring-shaped packing element (118a) is connected to said ring-shaped part (114a) and said tube element (1).
27. The operating device according to claim 26, wherein an effect is generated so as to close a leak between the operating device and the operating device. 28. A ring-cylindrical wall radially outside of said ring-shaped cavity (98a) and said first valve element (92a), in particular said ring-shaped part (114a).
28. The operating device according to claim 26, wherein the at least one ring-shaped packing element (116a) has an effect to seal the leak between itself and the other. 29. A tube section (120) in which said first valve element (92a) is axially bounded by said ring-shaped section.
a) wherein the tube section comprises the tube element (106).
a) at least in a region radially outwardly, so that preferably at least one ring-shaped packing element (122a) closes the leak between said tube section (120a) and said tube element (106a). 28. The operating device according to claim 28, wherein the operating device is effective. 30. The auxiliary valve element (96a) configured as a ring element surrounds the first valve element (92a), in particular the tube section (120a), at least in a region radially outside. A method according to any one of the preceding claims and claim 2 characterized by the claims.
5. The operating device according to 4. 31. The first valve element (92a)
A seal () extending essentially radially adjoining said tube section (120 a) and axially covering said pressure medium through opening (108 a) at the free end of said tube element (106 a) 124a), by means of which the first valve element (92a) protrudes inwardly in the correspondingly arranged ring-shaped and radially inwardly of the auxiliary valve element (96a) by means of the seal. Joint part (1
31. Operating device according to claim 29, characterized in that it engages at 42a) for entrainment and / or for breaking off the at least one pressure medium communication. 32. The engagement portion (142a) of the auxiliary valve element (96a) has a pressure medium through-opening (15).
4a) is limited in the radial direction, said pressure medium through-opening being part of the pressure medium communication in said control valve (42a), in particular corresponding to said pressure compensation opening (70a) 32. The operating device according to claim 31, wherein the operating device is or is the same as the operating device. 33. The first valve element (92a)
Is the seal portion (124) of the pipe portion (120a).
In the end region adjacent to a), at least one, especially radially open, pressure medium through-opening (126a) is part of at least one pressure medium communication in the control valve,
In particular, pressure medium communication between the pressure medium / power cylinder device (14a) and the pressure medium source (51a) or / and the pressure medium / power cylinder device (14)
32. The method as claimed in claim 31, comprising a part of the pressure medium communication between a) and the pressure compensation opening (70a).
Or the operating device according to claim 32. 34. The second valve element (94a) configured as a ring element connects the first valve element (92a) and / or, if necessary, the auxiliary valve element (96a) at least locally. 26. The operating device according to any one of the preceding claims, characterized in that it surrounds the operating device radially outwardly. 35. At least one ring-shaped packing element (150a) between said second valve element (94a) and said auxiliary valve element (96a).
Characterized in that it is effective to block leaks,
An operating device according to claim 34. 36. At least one ring-shaped packing element (150a) between said radially outer ring-cylindrical wall of said ring-shaped cavity (98a) and said second valve element (94a). The operating device according to any one of the preceding claims and characterized in that the operating device has an effect to close the leak. 37. Radially between said tube portion (120a) and said auxiliary valve element (96a) or (and) radially said second valve element (94a).
And the space (98a) of the valve casing (90a).
And, in particular, a pressure medium channel, in particular a pressure medium ring channel (140a, 152a), is formed between the control valve and the control valve. Characterized in that it is part of the pressure medium communication in (42a), in particular part of the pressure medium communication between the pressure medium source (51a) and the pressure medium / power cylinder device (14a). An operating device according to any one of the preceding claims and according to claim 24. 38. The two pressure medium channels (14)
0, 152a), the second valve element (94
a) is provided with a pressure medium communication which can be interrupted by engaging a correspondingly arranged engagement part (144a) of said auxiliary valve element (96a), said pressure medium communication comprising: Preferably said second valve element (9
4a) the at least one radially open pressure medium through-opening (138a) or / and the pipe section (120a), the auxiliary valve element (96a) or the second valve element (94a) 4. A ring chamber as defined above.
8. The operating device according to 7. 39. A valve connection (48a) connected to said pressure medium source (51a) or (and / or) a valve connection (54a) connected to a guide signal supply device (60a).
, Each comprising a particularly radially directed hole (104a; 100a) opening into said cavity (98a) in the valve casing (90a). The operating device according to claim 24. 40. A hole (100a) of a valve connection (54a) connected to the guide signal supply device (60a),
An opening in the cavity in the region of a cavity bottom (102a) which closes the cavity (98a) on the axial side, wherein the cavity bottom is used as a piston of the transducer means. Ring-shaped part (1) of the valve element (92a)
14a) are facing each other, and / or the cavity opening (104a) of the valve connection (48a) connected to the pressure medium source (51a) is open in the axial direction. The space (9) at the space end region bordering the
40. Operating device according to claim 39, characterized in that it is open to 8a). 41. A valve connection connected to the pressure medium / power cylinder device (14a) is provided in the space (9).
8a), in particular a first hole (108a) extending through said tube element (106a), and preferably connecting to said first hole (108a) and extending at said cavity bottom (102a). An operating device according to any one of the preceding claims and characterized in that it comprises a second hole (110a) present therein. 42. The first valve element (92b) and the second valve element (94b) are relative to a cavity (180b) of the valve casing (90b) around a valve axis (B ′). The actual quantity and the guide quantity are rotatably mounted and the respective valve elements (92
The operating device according to any one of claims 1 to 23, wherein the operating device is represented by a rotation position of b; 94b). 43. One of said elements, ie one of the first valve element (92b) and the second valve element (94b), in particular the second valve element (94b), (B ') having a coaxial ring-shaped portion (204b), which at least regionally surrounds another of the two valve elements (92b) radially outside. The operating device according to claim 42, characterized by: 44. The one valve element (94) surrounded radially outward by an inner peripheral surface of the valve casing (90b) defining the cavity (180b).
The ring-shaped portions (204b) of b) are circumferentially widened and offset from one another in the circumferential direction, so that respective portions (224b; 240) of said ring-shaped portions (204b)
b; 242b) having at least two break-throughs (210b, 212b, 214b) open radially inward and radially outward, separated from one another by the cavity (180b) in the valve casing (90b). ) Are provided, at least two holes (182b, 184b, 186b) which are directed in particular in the radial direction, the openings of these holes being circumferentially offset with respect to one another and At least partially covering another breakthrough of each one of the breakthroughs in at least one rotational position of one valve element (94b), and at least one communication with said another valve element (92b) Channels, especially through holes (202
b), wherein said communication channel is provided in at least one relative rotational position of said two valve elements (92b, 94b) with respect to each other, in particular said through-hole (202).
b) both openings are open to two of the breakthroughs by being at least partially covered by another breakthrough of each one of the breakthroughs. The operating device according to claim 43, wherein: 45. Each of exactly three holes (182b,
184b, 186b), each having exactly three breakthroughs (210b, 212b, 214b) and exactly one communication channel, in particular a radially extending through-hole (202b), provided relative to each other. And two of these holes (18) in at least one rotational position area of the two valve elements (92b, 94b) relative to the valve casing (90b).
4b, 186b), two of these breakthroughs (212b, 214b), and the pressure medium source (51b) and the pressure medium / power cylinder device (1) via the communication channel (202b).
4b) is created and relative to each other and to the valve casing (90)
b) relative to the two valve elements (92
b, 94b), two of these holes (182b, 186b), two of these breakthroughs (210b, 214b) and the communication channel in at least one other rotational position area (2
Operation according to claim 44, characterized in that a pressure medium communication is created between the pressure medium and power cylinder device (14b) and the pressure compensation opening (70b) via the pressure medium / power cylinder device (14b). apparatus. 46. Portions (224b, 240b, 242) of said ring-shaped portion (204b) separating said breakthroughs (210b, 212b, 214b) from each other.
b) is dimensioned as follows: at least in one relative rotational position of the two valve elements (92b, 94b) with respect to each other and / or with respect to the valve casing (90b). At least one rotational position of said one valve element (94b) relative to at least one channel opening of said communication channel, in particular said another valve element (92b)
At least one of the opening of the through-hole (202b) or (and / or) the opening of the hole in the valve casing (90b).
b) of each of the parts forming a particularly controlled edge (22)
The operating device according to claim 44 or 45, characterized in that it is dimensioned to be closed by 4b). 47. The pressure medium and power cylinder device (at least one rotation position of the two valve elements (92b, 94b) relative to each other and relative to the valve casing (90b)). Pressure medium communication between the pressure medium power cylinder device (14b) and the pressure compensation opening (70b) is created as well as pressure medium communication between the pressure medium source (51b) and the pressure medium source (51b). 5. The apparatus according to claim 4, wherein the state is not present.
7. The operating device according to 6. 48. The three holes (182b, 184b,
186b) preferably have axially essentially non-displaced openings spaced from one another at the same circumferential angle and preferably each have a circumferential angle area of equal size The operating device according to any one of claims 45 to 47, wherein the operating device is covered. 49. The three breakthroughs (210), which are preferably not essentially offset from one another in the axial direction.
46, b, 212b, 214b), each covering a circumferential angle region of equal size and being spaced from one another at the same circumferential angle.
49. The operating device according to any one of 48. 50. A hole (182b) provided corresponding to the pressure compensation opening (70b) of the three holes,
A hole (1) provided corresponding to the pressure medium source (51b)
84b), and the holes (186b) arranged corresponding to the pressure medium / power cylinder device (14b) are located one after the other in the defined rotation direction. In the basic state, one opening of the through hole (202b) in the first valve element (92b) is positioned substantially facing the hole (182b) provided corresponding to the pressure compensation opening (70b). And a portion (224b) of the second valve element (94b) forming a control edge of the ring-shaped portion (204b).
Are shifted in the rotation direction with respect to the hole (182b) disposed corresponding to the pressure compensation opening (70b),
However, adjacent to this, the first valve element (92
b) can be rotated in the rotational direction compared to the rotational position in the basic state, in particular at most approximately
The opening of the through hole (202b) can be rotated to a rotational position located substantially opposite a hole (184b) arranged corresponding to the pressure medium source (51b). Item 50. The operating device according to Item 48 or 49. 51. The cavity is formed in the valve casing (90b) as a through hole (180b) extending preferably transversely to the direction of movement of the decoupling bearing device, one of the through holes. At the end of the first valve element (92b) is accessible, in particular projecting, and at the other end of the through-hole the second valve element (94b) is accessible, in particular The operating device according to any one of claims 42 to 50, wherein the operating device protrudes. 52. A connecting element for connecting a curved body (226b) to which an end portion (208b) of the second valve element (94b) projecting from the through hole (180b) in the valve casing (90b) is fixedly connected. And the curved body engages with the uncoupled bearing device side portion (162b) of the uncoupled bearing device or the pressure medium / power cylinder device (14b), and in particular, the curved body (226b) and the Prestressed towards it by elastic means (228b) which engages the valve casing (90b), preferably by elastic means comprising leg springs (228b) arranged around said end portion (208b). And the interlock of the interlock release bearing device or the pressure medium / power cylinder device (14b) 52. The method as claimed in claim 51, characterized in that the linear movement of the release bearing device side part (162b) can be converted by the bending body (226b) into a rotational movement of the second valve element (94b). The operating device according to claim 10. 53. The resilient pre-stressed piston (236b) of said transducer means has a cylinder cylinder separate from said valve element (92b, 94b).
Part of a piston arrangement (234b), said piston (236b) preferably being essentially said valve shaft center (B ')
And the linear movement of the piston (236b) engages the first valve element (92b), in particular a toggle lever device (230b, 232b). 54. The operating device according to claim 51 or claim 52 and claim 12, characterized in that it can be converted into a rotary movement of the first valve element (92b) by means of a). 54. The mutually contacting surface portions of the valve casing (90b), of the first valve element (92b) and of the second valve element (94b) as sealing surfaces or / and sliding surfaces. Is formed as
Or (and) packing elements (216b, 2
The operating device according to any one of claims 42 to 53, characterized in that 18b) produces an effect so as to close the leak between them. 55. In addition to the first valve element (92c) and the second valve element (94c), another valve element is provided in the cavity (180c) of the valve casing (90c). 26. The operating device according to claim 24, wherein the operating device is not mounted so as to be movable along (B "). 56. One of said elements, namely one of the first valve element (92c) and the second valve element (94c), in particular the second valve element (94c), (B ″) has a coaxial ring-shaped part (204c), which at least regionally surrounds another of the two valve elements (92c) at least in a region. The operating device according to claim 55, wherein: 57. The one valve element (94c)
A ring-shaped portion (204c), which is surrounded on the outside by the inner surface of the valve casing (90c), which defines the cavity (180c), extends in the axial direction and is offset from one another in the axial direction. And the ring-shaped portion (2
At least two breakthroughs (210b, 212b, 214) that are separated from each other by respective parts of the respective parts of FIG.
b), in the valve casing (90c), the space (180c).
At least two holes (182c, 184c,
186c) are provided, the openings of these holes are offset relative to each other in the axial direction and at least one axial position of said one valve element (94c) At least partially over one another breakthrough, and said another valve element (92c) is provided with at least one communication channel (202c), said channel comprising both of said two Valve elements (92c, 94
57. The operating device according to claim 56, characterized in that it opens to two of said breakthroughs in at least one relative axial position of c). 58. Each of exactly three holes (182c,
184c, 186c), each having exactly three breakthroughs (210c, 212c, 214c), and exactly one communication channel (202c) extending along the outer surface of one particularly said another valve element (92c). Two of these holes in at least one axial position area of the two valve elements (92c, 94c) relative to each other and relative to the valve casing (90c). Holes (184c, 186)
c), two of these breakthroughs (212c, 214c) and the communication channel (202c) create a pressure medium communication between the pressure medium source and the pressure medium / power cylinder device. These holes are provided in at least one further axial position area of the two valve elements (92c, 94c) relative to each other and relative to the valve casing (90c). Two of the holes (182
c, 186c), two of these breakthroughs (210c, 214c) and the communication channel (202c) between the pressure medium / power cylinder device and the pressure compensation opening (70c). 58. The operating device according to claim 57, wherein a pressure medium communication is created. 59. The pressure medium and power cylinder device in at least one axial position of the two valve elements (92c, 94c) relative to each other and relative to the valve casing (90c). And no pressure medium communication between the pressure medium source and the pressure medium source, and no pressure medium communication between the pressure medium / power cylinder device and the pressure compensation opening (70c). The operating device according to claim 57 or 58, which performs the operation. 60. The control valve (42) is arranged in the casing bell (12), but is reached from the outside in the case of a casing bell (12) connected to the internal combustion engine and the transmission. Operating device according to any one of the preceding claims, characterized in that it is possible, in particular removable. 61. The direction of disengagement of the pressure medium / power cylinder device (14) and the direction of disengagement of the friction clutch are essentially parallel to each other, preferably the clutch axis (A) and the power cylinder apparatus axis. An operating device according to any one of the preceding claims, characterized in that (A) essentially corresponds. 62. Operation according to claim 1, characterized in that the valve axis (B; B ') and the power cylinder apparatus axis (A) do not have a common point. apparatus. 63. The operating device according to claim 62, wherein the valve axis (B) and the power cylinder apparatus axis (A) are essentially parallel to each other. 64. The valve axis (B ′) and the power cylinder axis (A) are essentially perpendicular to one another in a projection onto a plane essentially parallel to both axes. The operating device according to claim 62, which performs the operation. 65. The control valve (42) comprising:
Operating device according to any one of the preceding claims, characterized in that it is particularly removably mounted on a power cylinder device (14). 66. A control valve structure unit (40) including the control valve (42) is provided with respect to a power cylinder structure unit (14) including the pressure medium / power cylinder device (14). 66. Operation according to claim 65, characterized in that it is radially offset with respect to A) and is removably mounted on a radially outer part of the power cylinder structural unit (14). apparatus. 67. The control valve structural unit (40)
After the release of the fixing or / and coupling means which, if necessary, takes effect between the two structural units, preferably being accessible from at least one radial direction corresponding essentially to the radial direction. The operating device according to claim 66, characterized in that it is essentially removable in the radial direction from the power cylinder structural unit (14). 68. The operating device according to claim 1, wherein the pressure medium is a pressure medium caused by a gas action.