JP2000266082A - Friction clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the reliability and to reduce the abrasion by connecting a supporting element at a radially outer side of at least one supporting device, with an assembly attached to at least one supporting device, of the first and second assemblies. SOLUTION: In the axial direction, a ring piston 32 is supported by a housing 14 or a housing of a clutch 10 through a first bearing devcie 64. The bearing device 64 comprises a bearing ring 66 at a radially outer side, a bearing ring 68 at a radially inner side, and a plurality of bearing balls 70 existing therebetween, as a bearing element, the bearing ring 66 is engaged with the piston 32, and the bearing ring 68 is fixed to the housing 14 by means of a fixing ring 72 and the like. Corresponding thereto, a ring cylinder 34 is axially supported by a diaphragm spring 18 through a second bearing device 74 in a wall zone 44, and similarly comprises the bearing rings 76, 80. By applying this structure, the rotation substantially does not exist relative to an inertial system, the lubricant does not flow by the centrifugal force, and the abrasion can be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention is energized by a pressure-fluid operating device (Druckfluid-Betaetigungsanordnung) for performing an interlocking process (i.e., a clutch disengaging process) or a disengaging process (i.e., a disengaging process). The resulting energy accumulator, preferably a friction clutch with a diaphragm spring, in particular a motor vehicle friction clutch, wherein the pressure-fluid-operated operating device has a first support on a component which is essentially fixed in the axial direction A first assembly that can be axially supported via a device, and axially moved relative to the first assembly for biasing the energy storage device via a second support device A telescoping (nesting) unit comprising a second assembly that can be adapted to be actuated, wherein said first assembly and said second assembly form a fluid chamber, A working fluid may be flowed into the body chamber to generate an axial relative movement between the first assembly and the second assembly, wherein the first support device and the second At least one of the two support devices includes a radially outer support element and a radially inner support element, and a plurality of support devices between the radially outer support element and the radially inner support element. The present invention relates to a friction clutch having a support.

[0002]

2. Description of the Related Art A friction clutch constructed in this way is known, for example, from DE-A 4 208 906 (DE 42 08 906 A1). In the case of this known friction clutch, this occurs during the execution of the disengagement process, due to the telescopic unit being supported on the housing on the one hand and the telescopic unit being engaged on the diaphragm spring on the other hand. It is achieved that the axial forces are completely absorbed in the clutch and that external components, such as, for example, crankshaft bearing arrangements, are not affected. The assembly called the cylinder, i.e. the assembly supported on the axially fixed housing component, has its front end, i.e. the end region located close to the housing, radially inwardly of the bearing device. The ring engages the ring, the radially outer bearing ring being axially supported by the housing.
Correspondingly, an assembly called a cylinder engages the bearing ring radially inside the bearing arrangement. The radially outer bearing ring of the bearing device moves to engage the diaphragm spring to perform the decoupling process.

[0003]

Starting from this prior art, it is an object of the present invention to provide an assembly in which several assemblies are axially supported or axially engaged with the respective components. It is an object of the present invention to provide a friction clutch, in particular a motor vehicle friction clutch, in which increased reliability (operating reliability, Betriebssicherheit) and reduced wear can be achieved in the area.

[0004]

SUMMARY OF THE INVENTION According to the present invention, an object is to provide an energy storage device (energy accumulator, Kraftspeicher), which can be actuated by a pressure-fluid operating device for performing an interlocking or decoupling process. Is a friction clutch with a diaphragm spring,
In particular in the case of a motor vehicle friction clutch, the pressure-fluid operating device can be supported axially on a component which is essentially fixed in the axial direction via a first support device (bearing device). A first assembly and a second assembly that can be moved axially relative to the first assembly to act on the energy storage device via a second support device (bearing device) Telescopic unit with telescoping
wherein the first assembly and the second assembly form a fluid chamber, wherein the first assembly and the second assembly are in the fluid chamber. The working fluid may be introduced to generate an axial relative movement between the first and second support devices, wherein at least one of the first and second support devices is a radially outer support element ( Bearing element) and a radially inner support element (bearing element) and a plurality of supports (bearing body, Lagerkoerpe) between the radially outer support element and the radially inner support element.
r) is solved by a friction clutch.

In the friction clutch according to the present invention,
The radially outer support element of the at least one support device is coupled to an assembly of the first assembly and the second assembly that is associated with the at least one support device. Taken into account.

[0006] In the friction clutch according to the invention, at least one of the support devices is assigned a reverse effect on the operation of several support elements compared to the prior art. This has the following advantages. That is, for example, the at least one support device is a support device as described below, that is, through which a power storage device (the power storage device is generally configured as a diaphragm spring) is supported. When a support device, the radially inner support element of the support device rotates, while the radially outer support element on the basis of the rotational disconnection provided by the support device (rotational isolation, ie, not transmitting rotation). Has the advantage that it is held stationary in rotation. This means that essentially no rotation is present, for example with respect to the inertial system defined by the motor vehicle. This has the following important advantages: This has the advantage that the centrifugal force has essentially no effect on the lubricant provided in the region of the support device, or only a clearly reduced centrifugal force. This has the additional consequence that the tendency of the lubricant to collect in the region radially outside the support device is reduced. This also reduces the lubricant pressure in the radially outer region of the support device. It has the consequence that sealing problems can be avoided, especially in the radially outer region. In the radially inner region, a contact seal (contacting joint, Beruehrungsdichtung) on the radially inner support element can be created in a simple manner.
This is because there is essentially no tendency for the lubricant to flow out of the support area (bearing area) (eg, caused by centrifugal force). Another advantage is that, as the radially inner support element rotates, the sliding speed that occurs in the contact area between each support and said one or more support elements is reduced by a configuration known from the prior art (see FIG. (Configuration, arrangement). It also results in reduced wear (wear).

[0007] In order to be able to take advantage of the aforementioned advantages in a particularly efficient manner, the radially outer support element of the first support device is connected to the first assembly and that of the second support device. It is proposed that the radially outer support element is connected to the second assembly.

For example, the component fixed in the axial direction may be a clutch housing. Then again the full force connection in the clutch (Kraftrueckschluss, force co
nnection) is obtained.

In order to achieve a pressure fluid supply in a simple manner, the first assembly and the second assembly are of an inertial system in which the axially fixed components rotate. ) Are held in a rotationally fixed manner (without relative rotation). Furthermore, a valve device is provided which is essentially fixedly connected to the first or second assembly, by means of which the fluid can be selectively introduced into the fluid chamber. This valve device is, for example, a pressure governor (pressure balance,
Pressure regulator, Druckwaage), but may include any other valve arrangement that allows the working fluid to flow into or out of the fluid chamber with or without feedback.

The valve arrangement has a dual function in that the first and second assemblies are essentially held in a rotationally fixed manner by means of parts savings.
ion).

In a friction clutch known from DE-A-4208906, both assemblies of the telescopic unit are each configured in the form of a cylinder. That is, the outer assembly forming the cylinder, which is supported by the clutch housing, surrounds another tubular assembly that engages the diaphragm spring. The outer assembly carries a packing that seals (sealably) engages the outer peripheral surface of the inner assembly, and the inner assembly carries the inner peripheral surface of the outer assembly. It carries a packing (sealant) that engages to seal the leak. The result of this configuration is that, on the one hand, the fluid chamber, which is also essentially tube-shaped or ring-shaped, is located relatively close to the axis of rotation, so that at the set fluid operating pressure A correspondingly small decoupling force can be achieved on account of the relatively small effective working surface of the telescopic unit. On the other hand, this configuration is such that the fluid chamber and the support device (through which the outer assembly is supported by the housing) are axially staggered (staggered, gestaffelt, staggered). ) Lead to location. This leads to a relatively large axial structural length.

In order to eliminate these disadvantages, the present invention further provides a friction clutch, in particular a motor vehicle friction clutch, as follows. That is, the friction clutch is
It has an energy accumulator, preferably a diaphragm spring, which can be energized by a pressure fluid operated device for performing an interlocking process (clutch disengaging process) or a disengagement process (clutch disengaging process), wherein the pressure fluid type is operated. A first assembly in which an actuating device can be supported axially on a component which is essentially fixed axially via a first support device, and said energy storage via a second support device A second assembly that can be axially displaced with respect to said first assembly for biasing the container, wherein said first assembly comprises a telescopic unit. And the second assembly forms a fluid chamber in which the working fluid flows to generate an axial relative movement between the first assembly and the second assembly. The body can be allowed to flow.

In this aspect of the invention, the following is further taken into account: That is, each of the first assembly and the second assembly surrounds the radially inner wall region, and surrounds the radially inner wall region and, together with it, the substantially ring-shaped space. With a radially outer wall region. In that case, the radially inner wall region and the radially outer wall region of the respective assembly are connected to one another by respective connecting wall regions, the radially outer wall regions of the two assemblies being relative to each other. Being able to be moved axially so as to be almost fluid-free, and that the radially inner wall regions of the two assemblies can be moved axially so as to be almost fluid-free with respect to each other; It is.

In the case of the present invention, both assemblies are not configured in the shape of a pipe, but each have a ring portion which is substantially concentric with each other. These ring parts are connected to each other. From this, the advantage arises that greater form freedom can be obtained with an effective working volume of the fluid chamber. It has the consequence that a clearly greater decoupling force can be obtained for equal fluid operating pressures. Also, as described below, significantly greater form freedom can be obtained with respect to the relative positioning between the first support device and the fluid chamber.
In the case of a clutch having such a configuration, for example, the following may be taken into consideration. That is, the inner peripheral surface of the radially outer wall region of one of the first and second assemblies and the other of the first and second assemblies. The outer peripheral surfaces of the radially outer wall regions of the assemblies are at least regionally facing each other and sealed so as to be free of fluid with respect to each other; The inner peripheral surface of the inner wall region and the outer peripheral surface of the radially inner wall region of the other assembly are at least regionally facing each other and are sealed so as not to receive fluid with respect to each other. Should be taken into account.

Furthermore, the following may be taken into account in order to obtain a structural form which is short in the axial direction. That is, the coupling wall region of the one assembly has a radially outer wall region of the one assembly and an end of the radially outer wall region located near an axially fixed component. A radially inner wall region of the one assembly and an end region of the radially inner wall region remote from the axially fixed assembly. That they are united. At that time, preferably the following is taken into account. That is, the coupling wall area of the one assembly is at least locally approximated between its junction with the radially outer wall area and its junction with the radially inner wall area of the one assembly. Wherein the one assembly is the first assembly, and wherein the first support device is at least regionally connected to a radially inner wall region, a coupling wall region. A substantially radially extending region and an approximately axially extending region of the coupling wall region of the first assembly.

In another configuration, the following may be taken into account. That is, the inner peripheral surface of the radially outer wall region of one of the first and second assemblies and the other of the first and second assemblies. The outer peripheral surfaces of the radially outer wall regions of the volume are at least regionally facing each other and are sealed so as to be free of fluid with respect to each other; and The outer peripheral surface of the wall region and the inner peripheral surface of the radially inner wall region of the other assembly are located at least regionally facing each other and are sealed so as not to have fluid with respect to each other. is there.

In this case, preferably, the one assembly is the second assembly. In another independent aspect, it is proposed that the first support device and the fluid chamber overlap at least regionally in the axial direction, in order to obtain an axially short structure.

[0018]

BRIEF DESCRIPTION OF THE DRAWINGS The invention will now be described in more detail with reference to an advantageous embodiment with reference to the accompanying drawings, in which: FIG. FIG.
2 shows a partial longitudinal sectional view of an embodiment of the friction clutch according to the present invention, FIG. 2 shows a longitudinal sectional view of another embodiment of the friction clutch according to the present invention, and FIG. 3 shows the friction clutch of FIG. 1 shows a diagrammatic view in the axial direction of FIG.

In FIG. 1, a motor vehicle friction clutch (automobile friction clutch) according to the present invention is indicated by the reference numeral 10 as a whole. The friction clutch includes a housing 14,
The housing 14 is held in a rotationally fixed manner (that is, so as not to rotate relatively) by, for example, a tangential leaf spring (tangential leaf spring, Tangentialblattfedern) or the like.
Plate 1 that can be moved in the direction of
6 and a pressing plate subassembly (pressing plate assembly) 12. Further, a pressure plate subassembly 12 is supported on a support portion 20 of the housing in a radially outer region and radially inward of the support region 20 presses the pressing plate 16 toward the flywheel 22. An energy accumulator 18 in form is included. The pressing plate 12, its housing 14, is located in the radially outer region in a manner known per se,
2 (the flywheel may for example be constructed as a dual mass flywheel). Between the pressing plate 16 and the flywheel 22, a clutch disk (clutch plate), generally designated 24, together with its friction lining, is engaged with the clutch, as is known per se (i.e., 1), i.e., in a state where the pressing plate 16 is prestressed toward the left in FIG. 1.

The diaphragm spring 18 extends radially inward and has, for example, a plurality of elastic tongues (spring tongues, Federzun) in its radially inner region.
gen) 26. The resilient tongue has a pressure-fluid type, which will be described in more detail below, in order to carry out a disengagement process (clutch disengaging process), i.e. to release the pressing plate 16 from the biasing by the diaphragm spring 18. The operating device 28 is engaged.

The pressure fluid type operation device 28 has a unit (nested unit) 30 which can be expanded and contracted in the axial direction by supplying a pressure fluid (compressed fluid). The telescoping unit includes a first assembly 32 and a second assembly 34 that can be moved relative to the first assembly 32 in the direction of the axis of rotation A. First assembly 32
Is configured like a ring piston that fits into a ring cylinder formed by a second assembly 34. Ring piston 32, first assembly 3
2 has a radially outer wall region 52, a radially inner wall region 38, and a substantially ring-shaped connecting wall region 40 connecting these two wall regions 52,38.
This approximately pot-like (deep-pan) structure can be produced from a single piece, for example by a deep-drawing process (Tiefziehvorgang), however, just as can be seen in FIG. It is pointed out that 38 may be formed by a separate member connected to the coupling wall region 40 by welding or the like.

[0022] Correspondingly, the ring cylinder 34, the second assembly 34, has a radially outer wall region 42, a radially inner wall region 44 and a connecting wall region 46. Here again, an integrated structure is possible. However, for manufacturing reasons, as will be described further below, preferably the radially inner wall region 44 is made as a separate member. This member, on the other hand, can also be connected, for example, by welding or caulking (caulking,
Verstemmen) or the like. The ring piston 32 is formed in a ring shape and seals between the outer peripheral surface 36 of the radially outer wall region 52 of the ring piston 32 and the inner peripheral surface 54 of the radially outer wall region 42 of the ring cylinder 34. Or the inner peripheral surface 5 of the radially inner wall region 38 of the ring piston 32
6 carries respective sealing elements 48, 50 which provide a seal between the outer peripheral surface 58 of the radially inner wall region 44 of the ring cylinder 34. Thus, the fluid chamber 60 is formed in the telescopic unit 30.
A pressure fluid can be introduced into the fluid chamber for disengagement of the clutch (i.e., to disengage the clutch) by means of a valve device, generally designated 62.

In the axial direction, a ring piston 32 is supported by a housing 14 of the pressing plate subassembly 12 or a housing of the clutch 10 via a first bearing device (first support device) 64. The first bearing device 64 includes a radially outer bearing ring (support ring).
66 and a radially inner bearing ring (support ring) 68
A plurality of bearing balls (supporting balls) 70 are provided between the bearing rings 66 and 68 as bearings (supporting members). The radially outer bearing ring engages the ring piston 32 and can be, for example, fixedly connected thereto, or the connection can be generated simply by an axial pressure bias. It is also possible that
The radially inner bearing ring 68 is fixed to the housing 14 by a fixing ring 72 or the like.

Correspondingly, the ring cylinder 34 is axially supported by the diaphragm spring 18 by the inner wall region 44 via a second bearing device (second support device) 74. This second bearing device 74 also has a radially outer bearing ring (support ring) 76, which is likewise fixed to the flange-like projection of the inner wall region 44 by a fixing ring 78, and for example A radially inner bearing ring (support ring) 80 is fixedly connected to the entrainment ring 82 by welding. A plurality of bearing balls (supporting balls) 84 are arranged as bearing bodies (supporting bodies) between the radially outer bearing ring 76 and the radially inner bearing ring 80. The entrainment ring 82 has a plurality of entrainment protrusions 86. These entraining projections each bite between two circumferentially adjacent resilient tongues 26, whereby the radially inner bearing ring 80
Creates a rotational connection between the diaphragm spring 18 (ie, rotates together). A prestressing element is provided, for example, in the form of a disc spring 88 or the like. The diaphragm spring 18 is axially immovably held on the radially inner bearing ring 80 by the prestressing element.

The two bearing devices 64, 74 are each sealed by a sealing element which can be seen in the drawing. As a result, the bearing balls 70 to 84
Each move (rotate) in a preferably completely sealed and lubricant containing chamber. In the case of the friction clutch 10 according to the invention, as will be described further on, the radially outer bearing rings 66, 76 do not rotate about the axis of rotation A, however, the radially inner bearing rings 68 to 80 Rotating with the housing 14 or the diaphragm spring 18 provides several advantages during operation. On the one hand, excessive centrifugal action prevents the accumulation of lubricant in the bearing devices 64, 74 in the radially outer region, and thereby prevents lubricant shortage in the radially inner region. Just as well, on the basis of the lack of tendency to move radially outwards, the lubricant pressure in the radially outer region affecting the sealing element is reduced. As a result, the problem of packing (seal) can be further avoided. For example, a sealing element can be used which engages in radial contact with the radially inner bearing ring. This is because there is essentially no lubricant pressure and there is no risk of lubricant leakage. Further, the bearing balls 70 and 84 overlap (acts as overlapping).
Rolling and sliding movements (Waelz- und Gleitbewegun
The sliding speed occurring during g) is reduced, and the wear and wear of each bearing device 64, 74 is reduced.

For example, coupling wall region 40 and coupling wall region 46
It should be pointed out that the prestressing elastic means should work between the two. The prestressing elastic means prestresses the axially movable ring cylinder 34 in a direction away from the clutch housing 14 in this embodiment. Thereby, the pulling support of the ring cylinder 34 on the diaphragm spring 18 causes the ring piston 32 to move axially towards the clutch housing 14 and thus to the radially outer bearing ring 66 of the first bearing device 64.
Is achieved. Then, it is not necessary for both these components to be fixedly connected to each other.
As a result, a self-centering of the entire pressure-medium operating device 28 can now be achieved on the basis of the possible radial relative movement possibilities.

With respect to the structure of the valve device 62, it is pointed out that it can have any arbitrary structure of the valve device.
Thus, for example, the valve device 62 is opened according to the detected actuation of the clutch pedal, whereby a pressure fluid, for example compressed air or pressure oil (compressed oil), is introduced into or into the fluid chamber 60. It is possible to include a valve that can be electrically controlled (driven) to allow it to escape. Further, as shown in the figure, the valve device 62
However, it is possible to include a so-called pressure governor (pressure regulator, pressure equalizer, Druckwaage) having a structure known in the prior art and not shown here in detail. The following is essentially the principle of the functioning of the pressure governor. The pressure governor is in communication with a source of pressure fluid via a pressure fluid supply conduit 90, for example, a compressed air supply conduit 90. In addition, the pressure governor is in communication with a control engine or master cylinder, also activated by a clutch pedal, via a control fluid conduit 92. This control fluid is generally liquid based on slight compressibility. The pressure governor can release or shut off the pressure fluid flow path between the pressure fluid conduit 90 and the fluid chamber 60 so that the fluid chamber 60 can be kept sealed or environmentally friendly. A valve element is provided which can be opened. The valve element can be moved by the fluid pressure of the control fluid.

Starting, for example, from the engaged state (engaged state) of the clutch 10 shown in FIG. 1, when the clutch pedal is operated and thereby the master cylinder is activated, the pressure of the control fluid is increased. Is increased,
Thereby, the valve element is repositioned so that a pressure fluid, for example compressed air, can flow into the fluid chamber 60 via the pressure fluid conduit 90. Due to the flowing fluid and the pressure generated in the fluid chamber 60, the ring cylinder 34 is moved to the right in FIG. As a result, the resilient tongue 26 of the diaphragm spring 18 is pulled into engagement, and the force of the plate 16 is gradually released. Ring cylinder 34
(The ring cylinder has a valve device 62 fixed thereto,
In other words, during this movement of the pressure governor in the axial direction), the measuring cylinder chamber (female cylinder chamber) 9
4 is increased. A measuring piston 96 is hermetically guided in the measuring cylinder chamber. This measuring piston 96 is also fixedly connected to the ring cylinder 32. Measuring cylinder chamber 94 contains control fluid conduit 92
As a result, fluid flows from the control fluid conduit 92 into the measuring cylinder chamber 94 as the volume of the measuring cylinder chamber 94 increases. As a result, the fluid pressure in the control fluid conduit 92 decreases. Based on this pressure decrease in the control fluid conduit 92, the force bias on the valve element is also reduced. As a result, the valve element is displaced, whereby the pressure fluid conduit 90 and the fluid chamber 6
Block the fluid communication between 0 and keep the fluid chamber 60 sealed. Thereby, the control fluid conduit 9
An equilibrium state is achieved by the gradual flow of the control fluid from 2 into the measuring cylinder chamber 94. The equilibrium state ultimately depends on the magnitude of operation of the clutch pedal.
Starting from the decoupling state then present, when releasing the clutch pedal, the fluid pressure in the control fluid conduit 92 is subsequently reduced. As a result, the valve element of the pressure governor is further displaced and now opens fluid chamber 60 to the environment if fluid communication between pressure fluid conduit 90 and fluid chamber 60 is still obstructed. . As a result, pressure fluid, generally compressed air, can escape toward the environment or into the fluid reservoir. At this time, the ring cylinder 34 is pulled toward the housing 14 in the axial direction via the bearing device 74 based on the prestress force of the diaphragm spring 18. At that time, the measuring piston 96 also moves into the measuring cylinder chamber 94 again. Eventually then the state shown in FIG. 1 is reached again.

The functional principle of the pressure governor has been described earlier, but with integrated pneumatic (pneumatic)
It should be pointed out once again that operation by a slave cylinder (Nehmerzylinder) or the like may be considered.

To obtain a simple fluid communication between the pressure fluid conduit 90 and the fluid chamber 60, the clutch 1 according to the invention
In the case of 0, the entire telescoping unit 30 together with the valve device 62 held thereon, together with a fixed reference system (B
ezugsystem) held in a rotationally fixed manner (i.e., so as not to rotate relative to one another), and eventually the telescopic unit 30
Only the components cooperating with the clutch housing 14 and the diaphragm spring 18 and the bearing rings 68, 80 fixed thereto are brought into rotation.
This means that, for example, when the valve device 62 is directed radially outward, the transmission housing (G
etriebeglocke) can be provided by projecting through an opening 98. A first engaging device (gear cutting device) 102 is provided on the ring cylinder 34, and the engaging device is a second engaging device (gear cutting device).
104, but may be movable axially in this regard, and the second engaging device 1
04 may be fixed to a component that is also fixed, ie, does not rotate (rotate), for example, the transmission housing 100 or the like. The rotationally fixed positioning of the ring piston 32 is obtained in the arrangement shown, for example, by a measuring piston 96 which cuts into a measuring cylinder chamber 94.

The formation of the telescopic unit 30 with both assemblies 32, 34 as ring pistons or ring cylinders, respectively, results in a very reliable operation. In this operation, tilting (Verkante
n, pinching by tilting), etc. are almost completely avoided. This is because the guide areas are each formed by facing surface areas, which hold the two assemblies 32, 34 in position relative to one another.

When constructing the clutch 10 according to the present invention,
For example, it may be performed as follows. First, the diaphragm spring 18 is combined with an assembly that includes the bearing device 74 and the inner wall region 44 of the second assembly 34. For this purpose, the bearing device 74 can first be pushed into the diaphragm spring 18 together with the resilient means (spring) 88 already provided thereon. The entrainment ring 82 may then be attached and welded thereto or joined by a scissor ring (lock ring, Klemmring) or the like. Next or already before, the inner wall region 44 comprises the outer bearing ring 76 and the fixing ring 7.
8 or the like. In addition, as a precautionary measure, the bearing device 64 is inserted into the central opening of the housing 14 and then the radially inner bearing ring 68 is fixed to the housing 14 by means of a fixing ring 72 or otherwise. When this is done, the diaphragm spring 18 is moved axially through the first bearing device 64 with the inner wall region 44 of the second assembly 34 from the left in the illustration of FIG. The first assembly 32 may then be slid into the inner wall region 44 of the second assembly 34 with its radially inner wall region 38 and packing 48. Then, the remaining part of the second assembly 34, the outer wall area 42, is axially slidably mounted together with the integrated wall area 46 provided therein, and the inner wall area 44 Should be combined with However, the first assembly 32 and the remaining portion of the second assembly 34
Already before that they may be fitted together and then slid into the inner wall area 44 as a combined assembly. In this way, a simple assembly process is possible. Furthermore, embodiments according to the present invention allow the valve device 62 to be easily removed through the transmission housing 10. In that case, there is no need to dismantle the entire transmission.

Another embodiment of the friction clutch according to the present invention is shown in FIG. Components corresponding to those described above with respect to structure or function are indicated by the same reference numerals with the addition of the suffix “a”. Next, we will focus primarily on the structural differences that exist with respect to the embodiment shown in FIG.

The embodiment shown in FIG. 2 differs from the embodiment shown in FIG.
A distinction is made in terms of the structural form of 4a, and thus also in terms of its function. In contrast to the configuration of FIG. 1, the first assembly 32a has its outer wall region 52a sealed by its inner peripheral surface 108a by the sealing element 50a and the outer surface of the second assembly 34a. The wall region 42a is configured to face the outer peripheral surface 110a. Thereby, a staggered arrangement of wall regions (zigzag arrangement, Staf
felung) exists. The staggering begins with the inner wall region 44a of the second assembly 34a. Adjacent to the inner wall area 38a of the first assembly 32a.
It is now, however, followed by the outer wall area 42a of the second assembly 34a. The arrangement is the first assembly 32a
Is completed by an outer wall region 52a of the That is, in such an embodiment, the assembly 32
It is not possible to call one of the cylinders a and 34a functionally in the sense of the embodiment shown in FIG. Due to the radial staggering in several wall regions, each of the assemblies 32a, 34a has essentially the same configuration in principle or function and thus the same function.

Another structural difference is that the first assembly 32a
Of the first assembly 32a in the radially outer region with the radially outer wall region 52a of the first assembly 32a at its end region located near the housing 14a of the clutch 10a. It is in. On the other hand, the connection of the connecting wall area 40a to the inner wall area 38a is made by the following end area of the inner wall area, namely the housing 14a
This is done in the end region located farther from the end.
This results in the following configuration of the coupling wall region 40a. That is, in this configuration, the coupling wall region has an essentially axially extending portion 112a as well as one or more essentially radially extending portions 114a. In particular, the radially extending part 1 connecting to the inner wall area 38a
The first bearing device 64a is supported by 14a. As a result, this results in an essentially axially extending portion 112a,
It is almost completely surrounded by the radially extending portion 114a as well as the inner wall region 38a, thereby providing very good protection against dirt.
Despite the surrounding of this first bearing device 64a, the working fluid flowing through the fluid chamber 60a nevertheless provides sufficient cooling of the bearing. In addition, this configuration allows the fluid chamber 60
It can be seen that a completely overlaps the first bearing device 64a in the axial direction. As a result, the pressure fluid type operating device 28
The axial structural length in the region can be reduced. At this time, the cylindrical portion 116a of the housing 14a is connected to the radially inner bearing ring 68a of the first bearing device 64a.
Or connected to it for rotation. This results in the following configuration: That is, in this configuration, the telescopic unit 30a, ie, its first assembly 32a, is no longer
a in the end region directed towards the housing 14a
Rather than being supported by the housing 14a at the rear, in a region farther away from the housing 14a.

Another structural difference with respect to the embodiment shown in FIG. 1 is that the valve device 62a is axially fixed when performing the decoupling process, ie is fixedly connected to the assembly 32a. That is, it is fixed to the subassembly (assembly). This simplifies the connection of the fluid conduits and furthermore the transmission housing 10
The opening 98a at Oa can be made relatively short in the axial direction. The advantage is that dirt or foreign matter can be prevented from entering the internal space of the transmission housing 100a. For this purpose, as can be seen in FIG. 3, for example, the resilient closing element 12 in the opening 98a and surrounding the valve device 62a
0a may be provided. The closing element is
It allows only a small amount of circumferential and axial movement of the valve device 62a, however, it also provides an almost unobstructed closure of the transmission housing 100a.
As a result, no undesired pressing in the region of the opening 98a occurs in the event of a rocking movement (swaying movement, Taumelbewegungen) of the clutch housing 14a. Further, no bumping sound of the valve device 62a is generated at the peripheral edge of the opening 98a.

In the embodiment shown in FIG. 2, the inner bearing rings 68a to 80a, respectively, are connected to rotating components, namely the housing 14a and the diaphragm spring 18a. On the other hand, radially outer bearing rings 66a and 76a cooperate with first 32a or second assembly 34a. This again gives the above-mentioned advantages.

As can be seen, for example, in FIG. 2, the bearing arrangements do not have to engage directly with the associated assembly by their respective bearing rings,
It should be pointed out that an intermediate element such as, for example, a coupling ring 122a may be provided. At the intermediate element, here the radially outer bearing ring 76a of the second bearing device 74a is connected to the associated assembly.

In the embodiment shown in FIG. 2, a prestress elastic means (prestress spring) 124a is further recognized.
The prestressing elastic means is a pressure fluid type operating device 2
1a, whereby the housing 14 in particular via the first bearing device 64a
a) to ensure that the first assembly 32a is pressed into contact with a. Here, a fluid chamber 6 having a radially outer ring-shaped area
A guide for this prestressed elastic means 124a is provided at the same time by the specific form or shaping of Oa.

In FIG. 2, at least one compensating elastic means (compensating spring) 126a acting between the first assembly 32a and the second assembly 34a is provided at the pressure fluid type operating device 28a. You can see that it is done. The compensating elasticity means compensates for the tilting moment possibly transmitted to the second assembly 34a by the measuring piston 96a. The measuring piston 96a is mounted on the assembly 34.
a eccentrically engages with the measuring cylinder chamber 9 in principle.
There is a risk that the pressure of the control fluid generated at 4a will cause the second assembly 34a to be tilted or prestressed in the tilting direction with respect to the first assembly 32a. This is hindered by the compensating elastic means 126a.

Both of the above-mentioned embodiments, in each of which the ring-shaped space is surrounded by the respective wall regions of the two assemblies and the corresponding ring-shaped fluid chambers are created by combining the two assemblies Then, there are the following advantages. That is, the effectively (substantially) utilized surface area of the fluid chamber can be larger, ie, the working radius of the fluid chamber can be increased in a simple manner. As a result, an increased decoupling force can be provided for equal pressure fluid pressures.

According to the present invention, the following friction clutch is provided. That is, in the case of this friction clutch, a complete force connection is provided inside the clutch itself during operation of the clutch. That is, the decoupling force does not need to be received by the external bearing. Such clutches can be deployed on many vehicle types without too much deformation measures. Furthermore, although the clutches that are respectively pulled (pulled to release the interlocking) are shown in the preceding description, it is needless to say that the clutch can be used in a simple manner (pressed to release the interlocking by pressing). . In the case of a pushed clutch, the axially movable assembly is then moved towards the pressing plate.

It should be pointed out that the term "friction clutch", as used herein and in particular in the claims, sometimes refers to the following subassemblies: That is, in the sub-assembly, a configuration that is essential to the present invention is realized. That is, a subassembly called a "friction clutch" need not necessarily include, for example, a flywheel or clutch disc. This is because both the clutch disc and the flywheel have a parallel meaning with respect to the main aspects of the invention. Those skilled in the art will appreciate that the friction clutch defined in particular in the claims can be obtained in general by a combination of a unit, which in principle can be called a pressure plate subassembly, and a pressure-fluid operating device forming a decoupling mechanism. recognize.

[Brief description of the drawings]

FIG. 1 is a partial longitudinal sectional view of an embodiment of a friction clutch according to the present invention.

FIG. 2 is a longitudinal sectional view of another embodiment of the friction clutch according to the present invention.

FIG. 3 is a schematic view of the friction clutch of FIG. 2 as viewed in the axial direction.

[Explanation of symbols]

14; 14a Clutch housing 18; 18a Energy storage device (diaphragm spring) 28; 28a Pressure fluid type operating device 30; 30a Telescopic unit 32; 32a First assembly 34; 34a Second assembly 36 Outer peripheral surface 38 38a radially inner wall region 40; 40a coupling wall region 42; 42a radially outer wall region 44; 44a radially inner wall region 46; 46a coupling wall region 52; 52a radially outer wall region 54 inner periphery Surface 56; 56a Inner peripheral surface 58; 58a Outer peripheral surface 60; 60a Fluid chamber 62; 62a Valve device (pressure governor) 64; 64a First bearing device 66; 66a Radially outer bearing element 68; 68a Radially inner Bearing element 70; 70a bearing ball 74; 74a second bearing device 76; 76a half Bearing elements outward 80; 80a radially inward of the bearing element 84; 84a bearing balls 108a inner circumferential surface 110a outer circumferential surface 112a axial extension to a region extending region 114a radially

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[Procedure amendment]

[Submission Date] May 10, 2000 (2000.5.1)
0)

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] Claims

[Correction method] Change

[Correction contents]

[Claims]

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Joachim Lintner Germany 97456 Hambach am Stockofen 20 (72) Inventor Thomas Otto Germany 97497 Gög Schheim am Szezen 104 (72) Inventor Frank Hirschmann Germany Day 97664 Niederwern Wijernstrasse 8

Claims (14)

[Claims] 1. An accumulator (18; 18a), preferably a diaphragm spring (18; 18a), which can be acted upon by a pressure-fluid operating device (28; 28a) for performing an interlocking or decoupling process. A friction clutch having a pressure fluid type actuating device (28; 28a) on a component (14; 14a) which is essentially fixed in the axial direction. 64; 64a), a first assembly (32; 32a) which can be supported in the axial direction, and said energy accumulator (18; 18) via a second support device (74; 74a).
a) to act on said first assembly (32; 3).
Telescopic unit (3) comprising a second assembly (34; 34a) which can be moved axially with respect to 2a).
0; 30a), wherein the first and second assemblies (32, 34; 32a, 34a) have a fluid chamber (6
0; 60a), and a working fluid flows into the fluid chamber to generate an axial relative movement between the first and second assemblies (32, 34; 32a, 34a). First and second support devices (64, 74;
64a, 74a) is provided with a radially outer support element (66, 76; 66).
a, 76a) and a radially inner support element (68, 80; 68a, 80a), and a plurality of supports (70) between the radially outer support element and the radially inner support element. , 84; 70a, 8
4a), wherein the at least one support device (64, 74; 64a,
74a) said radially outer support elements (66,
76; 66a, 76a) are the first and second assemblies (3
2, 34; 32a, 34a), the assembly (32, 34; 32) attached to the at least one support device.
a, 34a). 2. The radially outer support element (66; 66a) of the first support device (64; 64a) is coupled to the first assembly (32; 32a); and 2. The device according to claim 1, wherein the radially outer support element of a second support device is connected to the second assembly. 3. The friction clutch as described. 3. The clutch housing (14; 14a), wherein said axially fixed component (14; 14a) is provided.
3. The method according to claim 1, further comprising the step of:
3. The friction clutch according to 1. 4. The first and second assemblies (32,
34; 32a, 34a) are held in a rotationally fixed manner with respect to the inertial system as follows, i.e., with respect to the inertial system in which the axially fixed component (14; 14a) rotates in the inertial system. The friction clutch according to any one of claims 1 to 3, characterized in that: 5. The first or second assembly (3).
2, 34; 32a, 34a) and a valve device (62; 62a) which is essentially fixedly connected to the fluid chamber (60; 60).
2. The method according to claim 1, wherein the liquid can be introduced into a).
5. The friction clutch according to claim 4. 6. The friction clutch according to claim 5, wherein the valve device includes a pressure governor. 7. The first and second assemblies (32,
34; 32a, 34a) is the valve device (62; 62a).
The friction clutch according to claim 4, wherein the friction clutch is held in a substantially rotationally fixed manner. 8. An accumulator (18; 18a), preferably a diaphragm spring (18; 18a), which can be actuated by a pressure-fluid actuating device (28; 28a) for performing an interlocking or decoupling process. A pressure clutch, such as a motor vehicle friction clutch, wherein the pressure fluid actuating device (28; 28a) is axially first attached to a component (14; 14a) which is essentially fixed in the axial direction. A first assembly (32; 32a) that can be supported via a supporting device (64; 64a) of the power storage device (18; 18) via a second supporting device (74; 74a).
a) to act on said first assembly (32; 3).
Telescopic unit (3) comprising a second assembly (34; 34a) which can be moved axially with respect to 2a).
0; 30a), wherein the first and second assemblies (32, 34; 32a, 34a) have a fluid chamber (6
0; 60a), and a working fluid flows into the fluid chamber to generate an axial relative movement between the first and second assemblies (32, 34; 32a, 34a). A friction clutch that may be adapted to include a first and a second assembly (32, 34; 32a, 34a).
Each of which surrounds and is essentially associated with the radially inner wall region (38, 44; 38a, 44a) and the radially inner wall region (38, 44; 38a, 44a). A radially outer wall region (52, 42; 52a, 42a) surrounding the ring-shaped space, and the respective assemblies (32, 34; 32a, 34).
a) said radially inner wall regions (38, 44; 38);
a, 44a) and said radially outer wall regions (52, 4a).
2; 52a, 42a) are respectively connected wall regions (40,
46; 40a, 46a), the radially outer wall regions (52, 42; 52a, 42) of the two assemblies (32, 34; 32a, 34a).
a) can be moved axially so as to be essentially fluid-free with respect to each other; and the radially inner wall regions (of the two assemblies (32, 34; 32a, 34a)) 38, 44; 38a, 44
Friction clutches, characterized in that a) can be moved axially so as to be essentially fluid-free with respect to one another, optionally associated with one or more of the arrangements of claims 1 to 7. 9. The first and second assemblies (32a, 34).
a) of the radially outer wall region (52a) of one of the assemblies (32a) and the other of the first and second assemblies (32a, 34a). The radially outer wall region (42) of one of the assemblies (34a)
a) are at least regionally facing each other and are sealed so as to be free of fluid with respect to each other; and the radius of the one assembly (32a) The inner peripheral surface (56a) of the radially inner wall region (38a) and the outer peripheral surface (58) of the radially inner wall region (44a) of the other assembly (34a).
9. A friction clutch according to claim 8, characterized in that a) are positioned at least regionally opposite one another and are sealed off from each other. 10. The coupling wall region (40a) of the one assembly (32a) is fixed in the axial direction to the radially outer wall region (52a) of the one assembly (32a). At the end region of the radially outer wall region (52a) which is located closer to the component (14a), and at the radially inner side of the one assembly (32a). A wall region (38a) and an end region of the radially inner wall region (38a) remote from the axially fixed component (14a). The friction clutch according to claim 9. 11. The connecting wall area (40a) of said one assembly (32a) is provided with said radially outer and said radially inner wall area (5) of said one assembly (32a).
2a, 38a) extending at least approximately in the axial direction between its joints, said one assembly (32a) being said first assembly (32a);
And an area (1) in which the first support device (64a) extends at least locally in the radially inner wall area (38a), essentially the radial direction of the coupling wall area (40a).
14a) and an approximately axially extending region (1) of the coupling wall region (40a) of the first assembly (32a).
A friction clutch according to claim 10, characterized in that it is surrounded by 12a). 12. The first and second assemblies (32, 34).
An inner peripheral surface (54) of the radially outer wall region (42) of one of the assemblies (34) and the other of the first and second assemblies (32, 34). An outer peripheral surface (36) of said radially outer wall region (52) of the body (32) is positioned at least regionally facing each other and sealed so as to be free of fluid with respect to each other; The outer peripheral surface (58) of the radially inner wall region (44) of the one assembly (34) and the inner periphery of the radially inner wall region (38) of the other assembly (32). The friction clutch according to claim 8, characterized in that the surfaces (56) are at least regionally facing one another and are sealed off without fluid with respect to one another. 13. The assembly according to claim 12, wherein said one assembly (34) is said second assembly (34).
3. The friction clutch according to 1. 14. A friction clutch, for example a friction clutch having a power storage device (18a), preferably a diaphragm spring (18a), which can be acted upon by a pressure-fluid actuating device (28a) for performing an interlocking or decoupling process. In the form of a motor vehicle friction clutch, said pressure fluid operating device (28a) is axially supported by a component (14a) which is essentially fixed axially via a first support device (64a). The first assembly (32a) obtained and axially with respect to said first assembly (32a) for acting on said energy storage device (18a) via a second support device (74a). A telescopic unit (30a) comprising a second assembly (34a) that can be moved;
The first and second assemblies (32a, 34a) form a fluid chamber (60a) in which the first and second assemblies (32a, 34a) are located. A friction clutch into which a working fluid can flow to generate an axial relative movement between the first support device (64a) and the fluid chamber (60).
a) overlaps at least regionally in the axial direction and is optionally tied to one or more of the arrangements of claims 1 to 13.