DE10063781C2 - Coupling system with a clutch device operated by master cylinder - Google Patents

Description

The present invention relates to a clutch system comprising a Coupling device in particular for the arrangement in a drive strand (in particular of a motor vehicle) between a drive unit and a transmission, and comprising an actuating device for actuation the coupling device by hydraulic means, the Coupling device an input side assigned to the drive unit, at least one output side assigned to the transmission and at least one integrated in the coupling device, with at least one in operation one co-rotating from the input side and the output side, with the Actuator via a rotary connection in hydraulic connection has standing or bringable hydraulic slave cylinder, the one Coupling arrangement comprising at least one on the input side and at least one friction surface on the output side for actuating the same assigned.

Such coupling systems or coupling devices and actuating devices are known for example from DE 35 26 630 A1, US 2,712,373 and EP 0 758 434 B1. Coupling systems or coupling devices of this type are also disclosed in the applicant's patent applications; in particular, the German patent applications DE 100 04 179 A1, DE 100 04 186 A1, DE 100 04 189 A1, DE 100 04 190 A1, DE 100 04 195 A1 ( all AT 01.02.2000); DE 100 34 730 A1 (AT 17.07.2000 ), the disclosure of which is included in the disclosure content of the present application.

Conventional couplings, in which the contact pressure for coupling over a hydraulic medium, in particular by means of a friction lining or Pad packages (possibly plate packs) assigned to the pressure piston becomes (NORMALLY OPEN clutch) or the Pressing force of a pressure spring arrangement for disengaging hydraulic pressure is overcome (NORMALLY OPEN- Coupling), have at least one pump for generating the hydraulic Energy on. In particular in the case of a coupling device as at the beginning addressed, in which the slave cylinder in the clutch device is integrated and rotates during operation, it appears under creation conventional scales, if not mandatory, that generate hydraulic energy by means of at least one pump, since at a certain amount of leakage is to be expected in conventional slewing rings can cause no problems if hydraulic energy or Hydraulic medium can always be supplied, as is the case with a Pump that works continuously or can be operated continuously, the case is.

But it has now become more important that one is always with running pump (with a pressure medium filling or running idle), the So it cannot be switched on and off, mechanically connected and disconnected if necessary is drivable, but consumes considerable energy and in one Energy consumption balance with a quite high power loss that affects the efficiency of the vehicle. This applies to both dry-running clutches, such as double or powershift clutches shown in DE 35 26 630 A1, as well as for wet-running Clutches, such as wet-running double or power shift clutches of the in the aforementioned applications shown by the applicant, the two each have a plate pack assigned to a transmission input shaft.

Against this background, the invention fails in a completely different way the obvious way of switching on and off (switching on and off if necessary  Uncoupling) the pumping approach before actuating device has at least one hydraulic master cylinder which with the hydraulic slave cylinder is in hydraulic connection or can be brought and via which the associated clutch arrangement can be actuated is.

The inventors have recognized that it is possible to provide hydraulic master cylinders with a sufficient actuation volume (for example 8 cm ³ ), and that the expected problems due to a leakage in the area of the rotary connection can also be dealt with. The effort to avoid or control of these problems may be offset by the advantage that energy losses due to a continuously running pump or the technical effort for switching a pump on and off, possibly coupling and uncoupling, are avoided become.

The coupling device can be a multiple coupling device, for example, a double clutch device with a first one Transmission input shaft of the transmission associated with the first clutch arrangement voltage and a second transmission input shaft of the transmission assigned second clutch arrangement. It is specially designed for one Multiple clutch device thought in which one is in operation rotating hydraulic slave cylinder, that of the first clutch Arrangement is assigned to their operation, and one in operation rotating hydraulic slave cylinder, the second Coupling arrangement for their actuation is integrated. For Such a multiple coupling device is based on the new approach the invention proposed that the actuating device a first has hydraulic master cylinder with the first hydraulic Slave cylinder is in hydraulic connection or can be brought and over the the first clutch arrangement is actuatable, and that the actuation direction has a second hydraulic master cylinder which with the  second hydraulic slave cylinder is in hydraulic connection or can be brought and via which the second clutch arrangement can be actuated.

The coupling device or at least one of the first and the The second clutch arrangement can be of the NORMALLY OPEN type and against the effect of an assigned energy storage arrangement (possibly Release spring) can be engaged by means of the assigned slave cylinder. Furthermore, it is possible for the coupling device or at least one from the first and the second clutch arrangement from the NORMAL WISE-CLOSED type is and against the effect of an assigned Force storage arrangement (if necessary, engagement spring) by means of the assigned Slave cylinder can be disengaged.

The clutch arrangement can be designed as a multi-plate clutch arrangement det be. In a corresponding manner, the first and the second Clutch arrangement each designed as a multi-plate clutch arrangement his. The multi-plate clutch arrangement or multi-plate clutch arrangement Solutions can be provided for wet operation and over a slewing ring on an operating medium pump Operating medium supply, in particular hydraulic medium supply, be connected.

Regarding the actuating device, it is proposed that this at least one electromotive actuator for actuating the transmitter cylinder or at least one master cylinder of the first and second Has master cylinder.

The electromotive actuator can with a gear mechanism non-linear transmission characteristic coupled to the master cylinder his. This proposal is based on the knowledge that at least most coupling designs do not have the same energy distributed over the stroke, but that, for example, in the  In the case of a power-operated closing (NORMALLY OPEN) clutch arrangement of the majority of the position energy only on the last part of the Stroke is required if the friction surfaces, possibly plate packs, pressed together or pressed on block. Accordingly, for proposes a clutch arrangement of the NORMALLY OPEN type the gear mechanism at the end of an engagement path provides more indirect translation than at the beginning of the engagement path. Conversely, for a clutch arrangement from the NORMAL CLOSED type may be advantageous if the gear mechanism on At the beginning of a decoupling path a more indirect translation than at the end of the Disengaging path provides. The non-linear transmission characteristic can can be achieved by a nonlinear kinematics (mechanics) over which the Actuator and the master cylinder are coupled together. For example the gear mechanism can be at least one of an eccentric drive arrangement, a toggle lever arrangement and an over-center spring arrangement include.

To avoid or master the already mentioned, on Leakage related problems, especially leakage in the area a slewing ring is proposed as particularly preferred that the coupling system has a hydraulic medium supply device which a sensor arrangement for monitoring at least one system status of the clutch system and is designed to respond to at least one predetermined system state to compensate for a Leakage-related loss of hydraulic medium from the master cylinder, the slave cylinder and a hydraulic connection connecting them comprehensive hydraulic system hydraulic medium in the hydraulic system or in a subsystem thereof, at least comprising the slave cylinder supply.

It is proposed as particularly expedient that the hydraulic medium Feeding device is designed for an operating pressure of the hydraulic system,  which, in the case of a coupling device, is OPEN type at the end of an engagement path and in the case of a clutch NORMALLY CLOSED type direction at the beginning of one Decoupling travel occurs, essentially to be maintained.

The sensor arrangement can, for example, be designed for one Detect hydraulic pressure in the hydraulic system, so that by a appropriate control a drop in hydraulic pressure below one Minimum value is prevented or the hydraulic pressure is at least back up the minimum value is increased, in each case by appropriate Subsequent delivery of hydraulic medium.

Another particularly useful option is that the sensor arrangement is designed to indicate a state of slip or slip Detect coupling device. The hydraulic pressure and therefore one Hydraulic medium loss through leakage is only according to this proposal indirectly detected via the resulting slip.

The hydraulic medium supply device can be a hydraulic medium pump have, which is designed, at least for a short time, hydraulic medium fed under pressure into the hydraulic system or subsystem. It will especially thought of not having a separate pump for the purpose of To provide subsequent delivery of hydraulic medium, but one anyway to use the existing pump for this. In particular, it is thought that the hydraulic medium pump of an operating medium supply, in particular cooling medium supply, the coupling device or / and is associated with the transmission and is intended and designed for it, Operating medium to at least one component of the coupling device or the transmission, for example to cool this component, if necessary a plate pack. Since the hydraulic medium pump only for a short time (intermit must) supply hydraulic medium for maintaining the pressure, it is usually sufficient if the hydraulic medium pump is less  is more powerful than one conventional for providing the actuation hydraulic pressure pump used.

A boundary condition for the hydraulic medium pump will usually be that these have a certain amount for the subsequent delivery of hydraulic medium Must provide minimum pressure that may be greater than that pressure otherwise required for the supply of operating medium. It comes in In this context, however, it is definitely worth considering that the Hydraulikme dium pump for short-term subsequent delivery operating states on overload running. Since it is not a continuous operation, the lifespan of the Pump not or through such intermittent overload operating conditions not significantly shortened.

According to a different approach, it is proposed that the taker cylinder subsystem of the hydraulic system and a Subsystem of the hydraulic system having master cylinder by means of a Shut-off valve arrangement can be shut off against each other and that the Master cylinder in interaction with the shut-off valve arrangement as Pump cylinder is operable to supply hydraulic medium to the Hydraulic system and / or the subsystem having the master cylinder. It is especially thought that for the supply of hydraulic medium in the Hydraulic system and / or the subsystem having the master cylinder a master piston of the master cylinder from a partially or completely in a cylinder position retracted stroke position by one pump stroke first is extendable and then retractable, and when the Master piston hydraulic medium from a hydraulic medium supply in the Cylinder space is traceable, preferably with the intermediation of one Valve arrangement, such as a check valve arrangement. For the business of the master cylinder as a piston pump, so to speak, the master cylinder for example with a valve arrangement, which at Extend the master piston hydraulic medium from the hydraulic medium into the cylinder space and when the master piston is retracted  a part of the cylinder space containing hydraulic medium under pressure seals. A seal associated with the master cylinder can be advantageous arrangement form the valve assembly.

The invention is explained below with reference to the figures examples of management explained in more detail,

Fig. 1 shows a schematic representation of an embodiment example of a clutch system according to the invention with a hydraulically operated double clutch;

Fig. 2 shows in the sub-figures 2a and 2b an example of a coupling mechanism with non-linear transmission characteristics for coupling an actuator and a Geberzylin;

Fig. 3 shows in the partial figures 3a and 3b another example of a coupling mechanism with a non-linear transmission characteristic for coupling an actuator and a master cylinder;

Fig. 4 shows a double clutch with two associated hydraulic master cylinders, which are connected via a rotary connection to a respective hydraulic slave cylinder of the double clutch;

Fig. 5 shows in the partial figures 5a and 5b a hydraulic master cylinder corresponding to the master cylinders of Fig. 4 in an enlarged sectional view ( Fig. 5a) and in a sectional overall view ( Fig. 5b) with associated actuating plunger, and in part 5c a variant of the master cylinder;

Could Fig. 6 shows in a partially sectioned view of an arranged in a drive train of a motor vehicle between a transmission and a drive unit double clutch with two multi-disk clutch assemblies which are part of a coupling system according to the invention be approximately as a dual clutch of the arrangement shown in Fig. 4.

Fig. 1 shows an example of a coupling system 200 according to the invention having a twin clutch 202 having a radially inner clutch assembly 204 and a radially outer clutch assembly 206. The two clutch arrangements are each represented only by schematically indicated disk packs 208 and 210 in FIG. 1 and serve, in a manner known per se, to provide a motor output shaft 212 or the like with an associated transmission input shaft 214 or 216 or the like for torque transmission connect. The radially inner clutch arrangement 204 is, for example, assigned to the transmission gears 1 , 3 and 5 and the radially outer clutch arrangement 206 is assigned to the transmission gears 2 , 4 and 6 , for example. The transmission input shafts 214 and 216 are designed as coaxially nested hollow shafts. Cooling oil can be fed from an oil sump 222 to the disk packs 208 and 210 via an oil channel 218 formed therein by means of a cooling oil pump 220 .

In the double clutch 202 , two hydraulic slave cylinders are integrated, each having an actuating piston assigned to one of the two disk packs and used to clamp the respective disk pack against the action of a return spring arrangement acting on the piston (clutch arrangement of the NORMALLY OPEN type) or the disk pack to relieve the clamping action of a clutch spring assembly for disengaging (clutch assembly of the NORMALLY CLOSED type).

The hydraulic slave cylinder of the radially outer clutch arrangement 206 is assigned a hydraulic master cylinder 230 or GZ1, which is connected to the hydraulic slave cylinder via a shut-off valve 232 or V ₁ , an oil line 234 , a rotary connection (not shown) and an oil channel formed in the nested transmission input shafts. In a corresponding manner, the hydraulic slave cylinder of the radially inner clutch arrangement 204 is assigned a hydraulic master cylinder 236 or GZ2, which via a shut-off valve 238 or V ₂ , an oil line 240 , a rotary connection (not shown) and an oil channel formed between the nested transmission input shafts on the hydraulic slave cylinder radially inner clutch assembly is closed. The oil lines 234 and 238 have due to a certain intrinsic flexibility pressure and volume storing properties, that is, they store part of the pressure generated when the respective master cylinder is actuated and the volume displaced from the master cylinder. The oil lines can be formed, for example, from a flexible rubber line (approximately similar to a conventional clutch pressure line or brake hose line), as indicated by schematically illustrated hose sections 242 and 244 .

The two clutch arrangements are actuated hydraulically via master cylinders 230 and 236 . Should there be any leaks in the rotary leadthroughs to the clutch arrangements, the pressure in the actuation system and thus, for example, the clamping force clamping the disk pack would decrease. This incipient leakage can be absorbed or "buffered" in the initial stages by the pressure storage properties of the elastic oil lines, since the oil lines release part of their "swallowing volume" when the pressure drops.

If an excessive pressure drop is registered by appropriate sensors, for example by pressure sensors detecting the oil pressure in the oil lines or indirectly by a clutch slip detection arrangement (for example comprising an input-side speed sensor assigned to shaft 212 and a first output-side speed sensor assigned to transmission input shaft 214 and one of transmission input shaft 216 associated second output-side rotational speed sensor), so, according to the arrangement of Fig. 1 remedy can be achieved in that the associated with the currently straight-operated master cylinder cut-off valve 232 and 238 closed and the piston 250 and 252 of the master cylinder motor, in particular an electric motor, is returned in order to compensate for the leakage-compensating Hydraulikme medium via a corresponding valve of the master cylinder in the piston chamber 254 or 256 from a hydraulic medium supply, for example from one on the oil sump 222 closed follow-up pipe. The master cylinder 230 and 236 thus serve as hydraulic medium-drawing reciprocating pumps. If a sufficient amount of hydraulic medium has flowed into the relevant piston chamber, the relevant master piston 250 or 252 moves forward again, the associated valve 232 or 238 is opened again. It is set by operating the master cylinder accordingly, the desired or required actuating pressure again. The valve of the master cylinder in question can be formed by a simple check valve. An advantageous possibility is that the valve is formed by a one-sided sealing arrangement of the master piston, similar to a bicycle air pump.

The arrangement according to FIG. 1 also illustrates a further possibility of how the actuating pressure can be maintained in spite of a leak at the rotary connections, for example. For the subsequent delivery of hydraulic medium, an existing oil pump can be used, such as a cooling oil pump for the gearbox and / or for the double clutch. Referring to FIG. 1, the oil pump 220 via two shut-off valves 260 (or V ₃₎ and 262 (or V ₄₎ connected to the lines leading to the rotary joints oil lines 216 and 240, respectively. As already mentioned, this pump normally conveys cooling oil from the oil sump 222 to the plate packs. Provided that this pump can at least briefly deliver an oil pressure which is in the order of magnitude of the clutch actuation pressures, a leakage loss can be compensated for by opening the valve 260 or the valve 262 and the actuation pressure can accordingly be maintained. Instead of two shut-off valves 260 and 262 , a single multi-way valve can also be provided.

It was briefly mentioned that the master cylinders 230 and 236 can be actuated by an electric motor. In principle, any other type of actuation, possibly also manual actuation, is also conceivable. It is assumed here that an electromotive actuation of the master cylinder is provided, wherein the respective master cylinder and the associated electric actuating motor, including a transmission mechanism or gear mechanism, can be integrated into an actuator unit.

The transmission or transmission mechanics can be linear or non-linear Have transmission characteristics. A non-linear transfer characteristic, one can also use the servomotor and the hydrauli nonlinear kinematics coupling the master cylinder can speak be advantageous if the assigned clutch arrangement is a has such a characteristic that the available operating energy is not required evenly or evenly distributed over the stroke, but, for example, a larger part of the energy at the end or at The beginning of the stroke is required. This is, for example, with power Closing multi-plate clutch assemblies (clutch assembly of the NORMALLY OPEN type) where most of the Control energy is only required on the last part of the stroke, if that the respective plate pack is pressed onto a block.  

A schematic example of a corresponding actuator with a servo motor M, a master cylinder GZ and a gear mechanism GM coupling them is shown in FIG. 2. The gear mechanism GM is designed as a toggle lever, which converts the actuating movement of the motor M at the beginning of the engagement path, when small system pressures are required, comparatively directly into a stroke movement of the piston K of the master cylinder ( FIG. 2a) and at the end of the engagement path, if high System pressures are required, the actuating movement of the motor, as a comparison, indirectly converts it into a stroke movement of the piston K ( FIG. 2b).

Another possibility for realizing such a non-linear actuation characteristic is shown in FIG. 3. Here, the Getriebemecha mechanism GM is formed by an eccentric arrangement, which comprises a turntable S rotatably arranged about a center of rotation Z and two coupling levers H ₁ and H ₂ articulated on the disk. Again, at the beginning of the engagement path when small system pressures are required, the translation is more direct than at the end of the engagement path when high system pressures are required.

FIG. 4 shows an embodiment specifying the arrangement according to FIG. 1 with a double clutch 202, preferably essentially according to the embodiment according to FIG. 6 and two master cylinders 230 and 236 according to the embodiment according to FIG. 5. The master cylinders are via the valves 232 and 238 and not recognizable in detail rotary connections 270 , 272 connected to the respectively assigned hydraulic slave cylinder 274 or 276 , which each act on the disk pack 208 or 210 by means of a piston 278 or 280, in the sense of the clutch arrangement 204 or 206 in question to engage a clutch. For further details, reference is made to FIGS. 5 and 6 and the associated description below.

FIG. 5 shows, in the partial figures 5a and 5b, a hydraulic master cylinder in a sectional representation, which has a housing 300 which, together with a piston 302 received axially displaceably therein, delimits a piston chamber 304 . The piston chamber 304 is connected via a passage 306 to a connection 308 to which an oil line leading to the associated hydraulic slave cylinder is connected. The connection 308 can be carried out with a retaining bracket 309 , which fixes the associated oil line or a counter-connection thereof.

The piston 302 axially guided in a guide sleeve 310 is designed as a hollow cylinder part closed on one side. In a piston end, which is opposed to a pressure surface 312 exposed to the pressure medium in the piston chamber 304 , a ball seat part 314 , which can also be referred to as a piston joint head, is inserted, which receives a coupling ball 316 of an actuating plunger 318 , which is coupled to an associated actuator, in particular servomotor, for example as a piston-side lever of the toggle lever according to FIG. 2 or as a coupling lever H2 according to FIG. 3. A joint head 319 can advantageously be used to link the tappet 318 to the actuator or an intermediate gear arrangement.

The housing 300 forms a follow-up line 320 which can be connected to a hydraulic medium supply. A first sealing arrangement 322 , which seals the piston chamber 304 , is designed such that, during an inward stroke of the piston 302 (to the left in FIG. 5), the piston chamber 304 is sealed off from the follow-up line 320 , so pressurized hydraulic medium from the piston chamber 304 does not escape to the follow-up line can.

However, occurs at a outward stroke (in Fig. 5 to the right) of the piston 302, a negative pressure in the piston chamber 304, the first seal assembly can flow into the piston chamber 304 322 hydraulic medium from the tracking line 320. If, for example, the connection 308 were provided with a check valve, the master cylinder GZ could be used as a reciprocating piston pump.

With reference to the arrangement according to FIG. 4, no check valve is provided for the application on which this is based, but rather the shut-off valve 232 or 238 , which can be brought into a closed position by appropriate actuation in order to draw hydraulic medium into the piston chamber by withdrawing the piston from the follow-up line 320 304 , and which can be adjusted by appropriate control into an open position in which the master cylinder is connected to the associated hydraulic slave cylinder 274 or 276 via the rotary connection 270 or 272 .

In each operating state of the master cylinder, a second sealing arrangement 324 seals the piston chamber 304 (as a secondary sealing arrangement as compared to the first (primary) sealing arrangement 322 ) and the connection region of the follow-up line 320 to the outside (in the direction of the open end of the housing receiving the piston).

In the in Fig. 5a and Fig. 5b embodiment shown, the first and the second seal assembly 322 and 324, each formed by a so-called U-ring, between which a spacer ring is disposed 323rd The guide sleeve 310 is in sealing engagement with the housing 300 by means of an O-ring 326 .

It should also be mentioned that the clutch system can have an electronic control unit which controls the servomotors assigned to the master cylinders and the valves 232 and 238 (or / and the pump 220 and the valves 260 and 262 ) and receives signals from an associated sensor arrangement and evaluates this in order to detect operating states of the clutch and / or pressure states of the hydraulic system, and which, if necessary, supplies hydraulic medium in the actuating part of the hydraulic system to compensate for leaks by correspondingly controlling the components mentioned.

Fig. 5c shows a variant of the master cylinder of FIGS. 5a and 5b. The main difference lies in the design of the piston. According to FIG. 5 c, the piston 302 is formed by a sleeve part 330 which receives a support part 332 which also fulfills the function of the ball seat part. The support part radially supports a cylindrical jacket section of the sleeve part 330 .

An example of a multiple clutch device that can be used as part of a clutch system according to the invention is explained in more detail below with reference to FIG. 6. It is specifically a double clutch device, or double clutch for short.

Fig. 6 shows a arranged in a drive train 10 between a drive unit and a transmission clutch 12 double. Of the Antriebsein unit, for example an internal combustion engine, only an output shaft 14 , possibly crankshaft 14 , is shown in Fig. 6 with a coupling end 16 for coupling a torsional vibration damper, not shown. The transmission is shown in Fig. 6 by a a transmission housing bell 18 limiting mission case portion 20 and two Getriebeein input shafts 22 and 24 represents, both of which are formed as hollow shafts, the transmission input shaft 22 extending substantially coaxially to the transmission input shaft 24 therethrough. Arranged in the interior of the transmission input shaft 22 is a pump drive shaft which serves to drive an oil pump on the transmission side (not shown in FIG. 6) (for example the oil pump 220 ), as will be explained in more detail. If at least one electric pump driven oil pump is provided, the pump drive shaft can be dispensed with.

The double clutch 12 is received in the transmission housing bell 18 , the bell interior being closed in the direction of the drive unit by a cover 28 which is pressed into a bell housing opening or / and is secured therein by a snap ring 30 . , The dual clutch as the embodiment in Fig. 6 shown, wet-running friction clutches, such as multi-disc clutches, so it is appropriate in general to make the housing for sealing engagement between the lid 28 to the clutch and formed by the transmission housing bell 18, for example, can be produced by means of an O-ring or another sealing ring. In FIG. 6, a sealing ring 32 is shown with two sealing lips.

A clutch hub 34 serves as the input side of the double clutch 12 and, for reasons to be explained in more detail below, consists of two ring sections 36 , 38 fixed to one another. The coupling hub 34 extends through a central opening of the cover 28 in the direction of the drive unit and is coupled via an external toothing 42 to the torsional vibration damper, not shown, so that there is a torque transmission connection between the coupling end 16 of the crankshaft 14 and the coupling hub 34 . If you want to dispense with a torsional vibration damper in general or at this point in the drive train, the coupling hub 34 can also be coupled directly to the coupling end 16 . The pump drive shaft 26 has at its end remote from the transmission an external toothing 44 which engages in an internal toothing 46 of the ring portion 36 of the clutch hub 34 , so that the pump drive shaft 26 rotates with the clutch hub 34 and accordingly drives the oil pump when the clutch hub 34th a rotational movement is given, as a rule by the drive unit and in some operating situations possibly also by the gearbox via the double clutch (for example in an operating situation characterized by the keyword "engine brake").

The cover 28 extends radially between a radial recess 50 of the housing bell 18 defining annular peripheral wall portion of the housing bell 18 and the ring portion 38 of the hub 34 , it being advantageous if between a radially inner wall region 52 of the cover 28 and the hub 34 , specifically the ring section 38 , a sealing or / and pivot bearing arrangement 54 is provided, especially when - as in the exemplary embodiment shown - the cover 28 is fixed to the bell housing 18 and accordingly does not rotate with the double clutch 12 . A seal between the cover and the hub will be required in particular if, as in the exemplary embodiment, the coupling arrangements of the double clutch are wet-running clutches. A high level of operational reliability, even in the event of oscillations and vibrations, is achieved if the sealing or / and pivot bearing arrangement 54 is secured axially on the cover 28 or / and on the coupling hub 34 , for example by an end portion of the cover edge 52 which is bent radially inward, such as can be seen in Fig. 6.

On the ring section 38 of the hub 34 , a carrier plate 60 is attached in a rotationally fixed manner, which serves for torque transmission between the hub 34 and an outer disk carrier 62 of a first disk clutch arrangement 64 . The outer disk carrier 62 extends in the direction of the transmission and radially inward to a ring part 66 , on which the outer disk carrier is rotatably attached and which is mounted on the two transmission input shafts 22 and 24 by means of an axial and radial bearing arrangement 68 such that both radial and axial forces are supported on the transmission input shafts. The axial and radial bearing arrangement 68 enables a relative rotation between the ring part 66 on the one hand and both the transmission input shaft 22 and the transmission input shaft 24 on the other hand. The structure and functioning of the axial and radial bearing arrangement will be discussed in more detail later.

On the ring part 66 axially further in the direction of the drive unit, an outer plate carrier 70 of a second multi-plate clutch arrangement 72 is attached in a rotationally fixed manner, the plate package 74 of which is surrounded by the plate package 76 of the first multi-plate clutch arrangement. The two outer disk carrier 62 and 70 are, as already indicated, by the ring member 66 rotatably connected to each other and are provided together on the stand in positive torque-transmitting engagement by means of an external toothing with the outer disk carrier 62 carrier plate 60 with the clutch hub 34 and - via the unillustrated torsional vibration damper - with the crankshaft 14 of the drive unit in torque transmission connection. In relation to the normal torque flow from the drive unit to the transmission, the outer plate carriers 62 and 70 each serve as the input side of the plate clutch arrangement 64 and 72, respectively.

A hub part 80 of an inner disk carrier 82 of the first multi-disk clutch arrangement 64 is arranged on the transmission input shaft 22 by means of splines or the like. In a corresponding manner, a hub part 84 of an inner disk carrier 86 of the second multi-plate clutch arrangement 72 is arranged on the radially outer transmission input shaft 24 by means of a spline toothing or the like. In relation to the control torque flow from the drive unit in the direction of the transmission, the inner plate carriers 82 and 86 serve as the output side of the first and second plate clutch arrangements 64 and 72, respectively.

Reference is once again made to the radial and axial mounting of the ring part 66 on the transmission input shafts 22 and 24 . For the radial mounting of the ring member 66 includes two radial bearing assemblies 90 and 92 are used which are effective between the radially outer transmission input shaft 24 and the ring member 66th The axial mounting of the ring part 66 takes place with respect to a support in the direction of the drive unit via the hub part 84 , an axial bearing 94 , the hub part 80 and a snap ring 96 axially securing the hub part 80 on the radially inner transmission input shaft 22 . The ring part 38 of the coupling hub 34 is in turn mounted on the hub part 80 via an axial bearing 68 and a radial bearing 100 . In the direction of the transmission, the hub part 80 is axially supported on the end bearing of the radially outer transmission input shaft 24 via the axial bearing 94 . The hub part 84 can be supported directly on a ring stop or the like or a separate snap ring or the like in the direction of the transmission on the transmission input shaft 24 . Since the hub part 84 and the ring part 66 can be rotated relative to one another, an axial bearing can be provided between these components unless the bearing 92 has both an axial bearing and a radial bearing function. The latter is assumed in relation to the execution example in Fig. 6.

Great advantages result if, as in the exemplary embodiment shown, the sections of the outer disk carriers 62 and 70 which extend in the radial direction are arranged on an axial side of a radial plane which extends orthogonally to an axis A of the double clutch 12 and which extend in the radial direction extending portions of the inner plate carrier 82 and 86 of the two plate clutch arrangements are arranged on the other axial side of this radial plane. This enables a particularly compact structure, in particular when - as in the exemplary embodiment shown - disk carriers of one type (outer disk carrier or inner disk carrier, in the embodiment, for example, the outer disk carrier) are connected to one another in a rotationally fixed manner and in each case as the input side of the respective disk clutch arrangement in relation to the power flow serve from the drive unit to the transmission.

Actuating pistons for actuating the multi-plate clutch arrangements are integrated in the double clutch 12 , in the case of the exemplary embodiment shown for actuating the multi-plate clutch arrangements in the sense of engaging. An actuating piston 110 assigned to the first multi-plate clutch arrangement 64 is arranged axially between the radially extending section of the outer plate carrier 62 of the first multi-plate clutch arrangement 64 and the radially extending section of the outer plate carrier 70 of the second multi-plate clutch arrangement 72 and on both outer plate carriers and on the ring part 66 is axially displaceable by means of seals 112, 114, 116, and between the outer disk carrier 62 and the actuating piston 110 formed pressure chamber 118 and an opening formed between the actuating piston 110 and the outer disk carrier 70 centrifugal force pressure compensating chamber sealingly guided 120th The pressure chamber 118 is connected to a hydraulic master cylinder, for example the master cylinder 230 , via a pressure medium channel 122 formed in the ring part 66 , the pressure medium channel 122 being connected to the master cylinder via a ring sleeve 66 , possibly gear-fixed, to the master cylinder. The connecting sleeve and the ring part 66 form a rotary connection. It should be mentioned in this connection that the ring part 66 is made in two parts for easier manufacture, in particular with regard to the pressure medium channel 122 and a further pressure medium channel, with two sleeve-like ring part sections inserted into one another, as indicated in FIG. 6.

One of the second multi-plate clutch arrangement 72 associated actuating piston 130 is arranged axially between the outer plate carrier 70 of the second multi-plate clutch arrangement 72 and a substantially radially extending and at a distal axial end region of the ring part 66 rotationally fixed and fluid-tightly attached wall part 132 and by means of seals 134, 136 and 138 on the outer disk carrier 70, the wall part 132 and the ring member 66 axially displaceable and between the outer disk carrier 70 and the actuating piston 130 formed pressure chamber 140 as well as between the actuating piston 130 and the wall portion 132 formed centrifugal Druckaus same chamber 142 performed sealing. The pressure chamber 140 is connected via a further (already mentioned) pressure medium channel 144 in the same way as the pressure chamber 118 to an assigned master cylinder, such as the master cylinder 236 . By means of the master cylinders, an actuating pressure can optionally (possibly also simultaneously) be applied to the two pressure chambers 118 and 140 in order to actuate the first multi-plate clutch arrangement 64 and / or the second multi-plate clutch arrangement 72 in the sense of engagement. Diaphragm springs 146 , 148 are used for resetting, that is to disengage the clutches, of which the diaphragm spring 148 assigned to the actuating piston 130 is received in the centrifugal pressure compensation chamber 142 .

The pressure chambers 118 and 140 are, at least during normal operating states of the double clutch 12 , completely filled with pressure medium (here hydraulic oil), and the actuation state of the multi-plate clutch arrangements depends on the pressure medium pressure applied to the pressure chambers. However, since the outer disk carriers 62 and 70 together with the ring part 66 and the actuating piston 110 and 130 and the wall part 132 also rotate with the crankshaft 14 when driving, there is also pressure increases in the centrifugal force caused by the pressure control device even without applying pressure to the pressure chambers 118 and 140 the pressure chambers, which could lead to an undesired engagement or at least grinding of the multi-plate clutch arrangements, at least at higher speeds. For this reason, the centrifugal pressure compensation chambers 120 , 142 already mentioned are provided, which receive a pressure compensation medium and in which centrifugal pressure increases occur in a corresponding manner, which compensate for the centrifugal pressure increases occurring in the pressure chambers.

One could think of filling the centrifugal pressure compensation chambers 120 and 142 permanently with pressure compensation medium, for example oil, whereby a volume compensation could possibly be provided to accommodate pressure compensation medium displaced in the course of actuation of the actuating pistons. In the embodiment shown in FIG. 6, the centrifugal pressure compensation chambers 120 , 142 are only filled with pressure compensation medium during operation of the drive train, specifically in connection with the supply of cooling fluid, in the exemplary embodiment shown specifically cooling oil, to the multi-plate clutch arrangements 64 and 72 via an annular channel 150 formed between the ring part 66 and the outer transmission input shaft 24 , to which the bearings 90 , 92 permeable to the cooling oil are to be attributed. The cooling oil possibly provided by the pump 220 flows from a transmission-side connection between the ring part and the transmission input shaft 24 in the direction of the drive unit through the bearing 90 and the bearing 92 and then flows in a partial flow between the end section of the ring part 66 and the hub part 84 radially outward in the direction of the disk set 74 of the second disk clutch arrangement 72 , enters the area of the disks due to passage openings in the inner disk carrier 86 , flows between the disks of the disk pack 74 or through friction lining grooves or the like of these disks to the outside radially, enters through openings in the outer plate carrier 70 and openings in the inner plate carrier 82 into the area of the plate pack 76 of the first plate clutch arrangement 64 , flows between the plates of this plate set or through lining grooves or the like of these plates to the outside and radially then flows sc finally through through openings in the outer disk carrier 62 from radially outward. The centrifugal pressure compensation chambers 120 , 142 are also connected to the cooling oil supply flow between the ring part 66 and the transmission input shaft 24 , specifically by means of radial bores 152 , 154 in the ring part 66 . Since, when the drive unit is stationary, the cooling oil serving as the pressure compensation medium in the pressure compensation chambers 120 , 142 runs out of the pressure compensation chambers due to a lack of centrifugal forces, the pressure compensation chambers are each refilled during the operation of the drive train (of the motor vehicle).

Since one of the pressure chamber 140 associated pressure impingement of the actuating piston is less than 130 and, moreover, less far radially outwards extends as one of the pressure equalization chamber 142 associated with pressure application of the piston 130 is formed a level limiting aperture 156 at least in the wall part 132, the maximum, the required centrifugal force compensation resulting radial level of the pressure compensation chamber 142 sets. When the maximum fill level has been reached, the cooling oil supplied via the bore 154 flows through the fill-level limiting opening 156 and combines with the cooling oil flow which flows radially outward between the ring part 66 and the hub part 84 . In the case of the piston 110 , the pressure application surfaces of the piston assigned to the pressure chamber 118 and the pressure compensation chamber 120 are of the same size and extend in the same radial area, so that corresponding level limiting means are not required for the pressure compensation chamber 120 .

For the sake of completeness, it should also be mentioned that further cooling oil flows preferably occur during operation. For example, at least one radial bore 160 is provided in the transmission input shaft 24 , through which a further partial cooling oil flow flows, and via an annular channel between the two transmission input shafts, which splits into two partial flows, one of which between the two hub parts 80 and 84 (through the axial bearing 94 ) flows radially outwards and the other partial flow between the end portion of the transmission input shaft 22 and the hub part 80 remote from the transmission and between this hub part 80 and the ring section 38 of the coupling hub 34 (through the bearings 98 and 100 ) flows radially outwards.

Further details of the double clutch 12 according to the described embodiment are readily apparent to those skilled in the art from FIG. 6. Thus, the axial bore in the ring portion 36 of the coupling hub 34 , in which the internal toothing 46 is formed for the pump drive shaft, is sealed oil-tight by a plug 180 fixed therein. The carrier plate 60 is axially fixed to the outer plate carrier 62 by two retaining rings 172 , 174 , of which the retaining ring 172 also axially supports the end plate 170 . A corresponding retaining ring is also provided for supporting the disk pack 74 on the outer disk carrier 70 .

With regard to further details and advantageous configurations of the double clutch 12 , reference is made to the German patent applications DE 100 04 179 A1, DE 100 04 186 A1, DE 100 04 189 A1, DE 100 04 190 A1, DE 100 04 195 A1 (all AT 01.02.2000) ; DE 100 34 730 A1 (AT 17.07.2000 ), the disclosure of which is included in the disclosure content of the present application. It is pointed out here that FIG. 6 of the present application corresponds to FIG. 1 of this application series.

Claims (21)

1. Coupling system, comprising a coupling device ( 202 ) in particular for the arrangement in a drive train between a drive unit and a transmission, and comprising an actuating device ( 230 , 236 ) for actuating the clutch device by hydraulic means, the coupling device being assigned to the drive unit Input side, at least one output side assigned to the transmission and at least one hydraulic slave cylinder ( 274 , 276 ) which is integrated in the coupling device and which, during operation, rotates with at least one hydraulic slave cylinder which rotates from the input side and the output side and is hydraulically connected to the actuating device via a rotary connection. which is assigned to a clutch arrangement ( 206 or 208 ) comprising at least one input-side and at least one output-side friction surface ( 206 or 208 ) for actuating the same, characterized in that the actuation device has at least one hydraulic master cylinder ( 230 , 236 ) which is in hydraulic connection with the hydraulic slave cylinder ( 274 or 276 ) or can be brought in and via which the associated clutch arrangement ( 206 or 208 ) can be actuated. 2. Clutch system according to claim 1, characterized in that the clutch device is a multiple clutch device, in particular double clutch device ( 202 ), with a first clutch input shaft of the transmission associated with the first clutch arrangement ( 210 ) and a second clutch input shaft of the transmission associated with the second clutch arrangement ( 208 ) and that in the coupling device a rotating first hydraulic slave cylinder ( 274 ), which is assigned to the first clutch arrangement for its actuation, and a rotating second hydraulic slave cylinder ( 276 ), which rotates to the second clutch arrangement whose operation is assigned are integrated. 3. Coupling system according to claim 2, characterized in that the actuating device has a first hydraulic master cylinder ( 230 ) which is in hydraulic connection with the first hydraulic slave cylinder ( 274 ) or can be brought and via which the first clutch arrangement ( 210 ) can be actuated, and that the actuating device has a second hydraulic master cylinder ( 236 ) which is or can be brought into hydraulic connection with the second hydraulic slave cylinder ( 276 ) and via which the second clutch arrangement ( 208 ) can be actuated. 4. Coupling system according to one of claims 1 to 3, characterized in that the coupling arrangement or at least one of the first ( 210 ) and the second coupling arrangement ( 208 ) of the NORMALERWEISE-OPEN type and against the action of an associated energy storage arrangement by means of assigned slave cylinder can be engaged. 5. Coupling system according to one of claims 1 to 4, characterized characterized in that the coupling arrangement or at least one from the first and the second clutch arrangement from NORMA LEARNED-CLOSED type is and against the action of a assigned energy storage arrangement by means of the assigned Slave cylinder can be disengaged. 6. Clutch system according to one of claims 1 to 5, characterized in that the clutch arrangement or the first ( 210 ) and the second ( 208 ) clutch arrangement (each) is / are designed as a multi-plate clutch arrangement. 7. Clutch system according to claim 6, characterized in that the multi-plate clutch arrangement ( 210 , 208 ) is provided for wet-running operation and is connected via a rotary connection to an operating medium pump ( 220 ) comprising operating medium supply. 8. Coupling system according to one of claims 1 to 7, characterized in that the actuating device has at least one electromotive actuator (M) for actuating the master cylinder (GZ) or at least one master cylinder of the first ( 230 ) and second ( 236 ) master cylinder. 9. Coupling system according to claim 8, characterized in that the electromotive actuator (M) via a gear mechanism (GM) with non-linear transmission characteristic with the encoder cylinder is coupled. 10. Coupling system according to claim 9, characterized in that the gear mechanism (GM) in the case of a clutch arrangement of the NORMALLY OPEN type at the end of an engagement path a more indirect translation than at the beginning of the engagement path provides. 11. Coupling system according to claim 9, characterized in that the gear mechanism in the case of a clutch arrangement from NORMALLY CLOSED type at the beginning of a dome a more indirect translation than at the end of the disengagement path provides.   12. Coupling system according to claim 10 or 11, characterized records that the gear mechanism at least one of one Eccentric drive arrangement (GM, Z, H1, H2) of a toggle lever arrangement (GM) and an over-center spring arrangement. 13. Coupling system according to one of claims 1 to 12, characterized by a hydraulic medium supply device ( 230 , 236 , 232 , 238 ; 220 , 260 , 262 ), which has a sensor arrangement for monitoring at least one system state of the coupling system and is designed for it , in response to at least a predetermined system state to compensate for a leakage-related loss of hydraulic medium from the master cylinder, the slave cylinder and a hydraulic system connecting this connecting hydraulic system comprising hydraulic medium to be fed into the hydraulic system or into a subsystem comprising at least the slave cylinder thereof. 14. Coupling system according to claim 13, characterized in that the hydraulic medium supply device ( 230 , 236 , 232 , 238 ; 220 , 260 , 262 ) is designed for an actuating pressure of the hydraulic system which, in the case of a coupling device of the NORMALLY OPEN type essentially occurs at the end of an engagement path and in the case of a NORMALLY-CLOSED-SEN type clutch device at the beginning of an engagement path. 15. Coupling system according to claim 13 or 14, characterized records that the sensor arrangement is designed to Detect hydraulic pressure in the hydraulic system. 16. Coupling system according to one of claims 13 to 15, characterized characterized in that the sensor arrangement is designed to a  Slip state or slip states of the clutch device too to capture. 17. Coupling system according to one of claims 13 to 16, characterized in that the hydraulic medium supply device has a hydraulic medium pump ( 220 ) which is designed to at least briefly supply hydraulic medium under pressure into the hydraulic system or subsystem. 18. Coupling system according to claim 17, characterized in that the hydraulic medium pump ( 220 ) is associated with an operating medium supply, in particular cooling oil supply, the coupling device and / or the transmission and is provided and designed for this purpose, operating medium for at least one component ( 206 , 208 ) of the coupling device ( 202 ) or the transmission. 19. Coupling system according to one of claims 13 to 18, characterized in that one of the slave cylinder ( 274 ; 276 ) of the subsystem of the hydraulic system and a master cylinder ( 230 ; 236 ) having subsystem of the hydraulic system by means of a shut-off valve arrangement ( 232 ; 238 ) against each other can be shut off and that the master cylinder ( 230 ; 236 ) can be operated in conjunction with the shut-off valve arrangement as a pump cylinder for supplying hydraulic medium to the hydraulic system and / or the subsystem comprising the master cylinder. 20. Coupling system according to claim 19, characterized in that for the supply of hydraulic medium in the hydraulic system and / or the subsystem having the master cylinder, a master piston ( 250 or 252 ; 302 ) of the master cylinder ( 230 or 236 ) from a partially or completely in a cylinder position retracted stroke position by a pump stroke is first extendable and then retractable, whereby when the master piston is extended, hydraulic medium from a hydraulic medium reservoir in the cylinder space ( 254 or 256 ; 304 ) can be traced, preferably with the intermediation of a / the valve arrangement. 21. Coupling system according to claim 20, wherein a sealing arrangement assigned to the master piston ( 322 ) serves as a valve arrangement which, when the master piston ( 302 ) extends, admits hydraulic medium from the hydraulic medium reservoir into the cylinder space ( 304 ) and, when the master piston retracts, contains a part containing hydraulic medium under pressure seals the cylinder chamber.