GB2330186A - Clutch actuator having a modular construction - Google Patents

Abstract

A clutch actuator comprises a first sub-unit 2 having a drive motor 4 driving a gearbox and a second sub-unit 3 containing power and/or control electronics. The sub-units 2, 3 each form a closed module and may be connected together by a mechanical connection, eg screws, rivets etc, which secure the two modules together via holes 8a-8c in the first sub-unit 2 and corresponding holes (23a-23c, fig 1) in the second sub-unit 3. Alternatively an electrical plug/socket connection 5, 24 may form the mechanical connection as well as an electrical connection. The sub-units 2, 3 can also be provided with a keyed snap-fit or an adhesive connection. First sub-unit 2 is manufactured from metal and the second sub-unit 3 is made of plastics. Both sub-units 2, 3 are furnished with dust tight and/or fluid tight seals. The completed structure may be fixed to a vehicle by the same connection as that which secures the sub-units together and the second sub unit is equipped with an electrical plug connection for other vehicle electronic units and/or sensors. The actuator may also be provided with a slip clutch between the motor 4 and an output element.

Description

1 OPERATING DEVICE 2330186 The invention relates to an operating device

for the automatic operation of a clutch in the drive train of a motor vehicle with a drive unit, such as drive motor and an output element on the output side, as well as with a gearbox converting the drive movement of the drive motor into an output movement of the output element.

Operating devices of this kind which have been known for example from DE 195 04 847 have as a rule an increased structural space and at the same time a generally unfavourable degree of efficiency. Similarly these devices are generally difficult to fit and dismantle.

The object of the present invention is to provide an operating device which requires less structural space. The operating device should also be capable of simple manufacture and fitting. Furthermore the invention is also to provide an operating device which has the best possible degree of efficiency with the best possible selflocking of the gearbox of the device.

This is achieved according to the invention in that the first and second sub units are each formed indi vidually as a closed module and can be connected into one structural unit by a mechanical connection and the first sub-unit has an electrical plug connection and the second sub-unit has an electrical plug connection and the two subunits are connectable electrically by means of these electrical plug connections.

It is thereby advantageous if at least one of the two sub- units has its own housing and the sub-unit with the housing is formed as a module closed per se. It is 2 further advantageous if at least one sub-unit provided with a housing is formed as a sealed sub-unit dust-tight and/or fluid-tight, such as water- tight. It is likewise advantageous if a mechanical connection is provided between the sub-units by means of the electrical plug connection. Both the electrical and the mechanical connection can be carried out by means of the plug.

Furthermore it is expedient if a mechanical connection is formed between the two sub-units by means of at least one mechanical keyed snap-fit connection wherein one element of one part engages and snaps in a socket of the other part.

It is likewise advantageous if a mechanical connection is formed between the sub-units by means of at least one connecting means such as a screw, rivet or adhesive connection.

Furthermore it is expedient if a mechanical connection is formed between the sub-units by means of at least one connecting means and this at least one connecting means also serves to fix the complete structural unit inside the motor vehicle. The connection of the sub-units thus takes place solely through the fixing means for fixing the subunits on the vehicle and through the electrical connection.

It is thereby advantageous if the one electrical plug 30 connection is formed as a plug and the other electrical plug connection is formed as a socket.

It is particularly advantageous if the housing of the second sub-unit which holds an electronics such as power and/or control electronics unit consists of at least two housing shells which are connectable together wherein the 3 - electronics are mounted between the housing shells. it is thereby expedient if at least one housing shell of the second sub-unit consists of plastics. It is likewise advantageous if at least one housing shell of the second sub-unit consists of metal. Furthermore it is advantageous if the second sub-unit has a further electrical plug connection for producing an electrical connection with other vehicle electronics units and/or sensors.

According to a further idea according to the invention, with an operating device for the automated operation of a clutch in the drive train of a motor vehicle with a drive unit such as drive motor and an output output side, as well as with a gearbox drive movement of the drive motor into an of the output element, it is advantageous has at least two partial gearboxes and a element on the converting the output movement if the gearbox slip clutch is mounted in the force flow between the drive unit and output element of the device. It is thereby particularly advantageous if the gearbox consists of at least two gearbox parts and one gearbox part has at least one spur wheel gear. Furthermore it is advantageous if the gearbox consists of at least two gearbox parts and one gearbox part has at least a spindle gear. It is thereby expedient if the spindle gear is connected in the force flow after the spur wheel gear.

It is expedient if the spur wheel gear is formed with two meshing gearwheels such as spur wheels wherein one gearwheel is mounted in the force flow on the drive side and one gearwheel is mounted in the force flow on the output side.

It is advantageous if the spur wheel gear is formed as a 35 twin-stage gearbox with three gearwheels such as spur wheels wherein each two gearwheels mesh with each other - 4 and a gearwheel on the drive side and a gearwheel on the output side as well as an intermediate gearwheel are mounted in the force flow.

It is likewise expedient if the gearwheel on the drive side is housed rotationally secured on an output shaft of the drive unit. Furthermore it is advantageous if the slip clutch is mounted in the force flow between the gearwheel of the spur wheel gear on the output side and the element of the spindle gear such as spindle on the drive side. This can be for example a hub of the spindle or the spindle itself or can be an element in active connection therewith.

It is expedient if the slip clutch is mounted in the force f low between the output shaf t of the drive unit and the gearwheel of the spur wheel gear on the drive side. It is thus advantageous if the slip clutch is mounted in the force flow between the gearbox parts.

It is likewise advantageous if the slip clutch is mounted radially inside the spatial area provided for the teeth of a gearwheel of the spur wheel gear. It is likewise expedient if the slip clutch is mounted axially inside the spatial area which is provided for the teeth of a gearwheel of the spur wheel gear and has an axial extension. Furthermore the slip clutch is integrated in a gearwheel, thus the slip clutch is mounted inside the gearwheel and where applicable individual component parts of the slip clutch such as friction surface are connected to the gearwheel or are formed integral with same. Such an arrangement of the slip clutch as an integrated structural part saves space according to the invention which is always important with the present day spatial conditions inside vehicles.

- It is expedient if the slip clutch has a f irst element which supports a first contact surface and a second element which has a second counter contact surface wherein the two elements are biased against each other by means of an energy accumulator wherein the energy accumulator is preferably a plate spring. The use of a plate spring as energy accumulator according to the invention also serves to save structural space. The plate spring likewise serves with its cogged marginal areas radially inside and/or radially outside to transfer torque between the one friction ring and the hub. This saves structural space according to the invention and at the same time an element such as the plate spring is occupied with a multiple function (contact pressure and torque transfer) whereby according to the invention the number of parts of the device can be reduced. A reduced number of parts thus leads to simplified assembly conditions.

It is can likewise be advantageous if the energy 20 accumulator is a coil spring with round, oval or angular wire-like material cross-section or the energy accumulator is an undulating spring with round, oval or angular wire like material cross-section.

It is likewise expedient if the first element supporting the first contact surface is formed integral with a gearwheel. It is likewise expedient with a further embodiment if the first element supporting the first contact surface is connected in keyed engagement with a gearwheel. This keyed connection can be formed by way of example through an engagement of a cam or teeth in a socket area.

It is advantageous if the first element supporting the 35 first contact surface is formed with a substantially circular ring-shaped friction or contact surface.

6 - Furthermore it is expedient if the second element supporting the second contact surface is formed as a substantially circular ring shaped element. It is thereby expedient if the circular ring shaped element has an arm extending substantially in the radial direction and supporting the contact surface. It can thereby be expedient if the circular ring shaped element has an arm extending substantially in the axial direction and producing a keyed connection with an energy accumulator.

It is likewise advantageous if the first and/or second substantially circular ring shaped friction surface or contact surface is flat.

According to a further idea according to the invention it is advantageous if the first and/or second substantially circular ring shaped friction face or contact surface is formed as an axially modulated shape or contour. This can be achieved for example in that individual circular ring segments viewed circumferentially are set up axially and have a pitch. A sinusoidal path of the circular ring face could likewise be formed with modulation in the axial direction.

It is particularly expedient in one embodiment if the axially modulated shape or contour of the friction surface is formed so that a part of the circular ring segments of the friction surface, viewed in the circumferential direction has a rising pitch in the axial direction and another part of the circular ring segments of the friction surface, viewed in the circumferential direction, has a falling pitch in the axial direction wherein the segments alternate with rising and falling pitch.

It is thereby expedient if the amount of the incline of 35 the falling segments is equal to the amount of the incline of the rising segments.

- 7 In another embodiment it is advantageous if the amount of the incline of the falling segments is not equal to the amount of the incline of the rising segments. This irregularity produces with the same axial force a different tensioning moment in the push and pull direction of the electric motor, thus a different effect of the slip clutch release force in the event of forces engaging on the output side. This can take place in addition to the effect of the spindle of the spindle gear which acts differently in the push and pull directions.

It is advantageous if at least one of the two elements is biased by means of at least one energy accumulator such as plate spring and the contact surface and counter contact surface are thereby biased relative to each other in friction contact. Furthermore it is expedient if the first element which supports the contact surface is the gearwheel on the output side. It is likewise advantageous if an output shaft of the drive unit and the axis of the output element are mounted parallel to each other.

According to a further idea according to the invention it is expedient if the spindle gear has a threaded spindle and a nut wherein the nut is mounted angularly movable but rotationally secured relative to the housing by means of a bearing. It is thereby particularly advantageous if the nut is mounted rotationally fixed relative to the housing but movable with adjustable angle by means of a spherical bearing. The spherical bearing can compensate a slight incline of the nut relative to the housing.

It is likewise expedient if the spherical bearing is formed so that the nut has a substantially spherical contour with two substantially semi-spherical surfaces such as side faces and teeth are provided between the 8 surfaces wherein the spherical faces are housed axially inside one hollow cylinder of two axially biased semi spherical shells wherein the hollow cylinder has internal teeth for holding the teeth of the nut and the cylinder is held axially movable but rotationally secured in teeth inside the housing by means of external teeth.

It is further expedient if at least one semi spherical shell of the spherical bearing is connected rotationally secured to the hollow cylinder. It is thereby likewise expedient if at least one semi spherical shell of the spherical bearing is connected rotationally secured to the hollow cylinder by means of teeth or snap-fit connection.

It is advantageous if the two semi spherical shells and the nut are biased against each other by an elastic element. It is thereby expedient if the elastic element is an energy accumulator such as a spring or the elastic element is a plastics or elastomer element such as rubber ring.

According to a further idea according to the invention it is expedient with an operating device if between the housing of the device and the output element or an element connected therewith is an energy accumulator which exerts spring force on the output element. This force action through the energy accumulator on the output element assists the operating process through the drive motor such as electric motor. The energy accumulator can be formed as a pressure spring.

Embodiments of the invention will now be explained with reference to the drawings in which:

- 9 Figure 1 shows a diagrammatic illustration of a subunit of the device according to the invention; Figure 2 shows a diagrammatic illustration of a sub5 unit; Figure 3 shows a device according to the invention; Figure 4 is a view of the mechanics of the device; Figure 5 is a sectional view of the device; Figure 5a shows a section of Figure 5; Figure 5b shows a section of Figure 5; Figure 6 shows a section illustrating the spherical bearing; Figure 7 shows a device according to the invention; Figure 8 shows a section illustrating the slip clutch; Figure 9a is a sectional view showing the slip clutch; Figure 9b is a sectional view showing the slip clutch; 20 Figure 10 is a sectional view showing the slip clutch.

Figure 1 shows an embodiment of an operating device 1 for the automated operation of a clutch, such as friction clutch, dry friction clutch, wet running clutch running in a fluid, multi- plate clutch, converter bridging clutch or another clutch in the drive train of a motor vehicle with a drive motor and a gearbox. The operating device 1 has a first sub-unit 2 and a second sub-unit 3.

The first sub-unit 2 comprises a drive motor 4 of the operating device, an electrical plug connection 5 such as plug or socket, as well as a housing 6 and an output element 7. Inside the housing 6 is a gearbox which converts the movement of the motor output shaft into a movement of the output element 7. The housing 6 is provided with fixing means 8a, 8b and 8c, such as fixing eyes, which are used to fix the first sub-unit where applicable to the second sub-unit and/or where applicable to a body part and/or to a gearbox component or engine component of the vehicle. Further fixing means such as screws or pins can engage through the fixing eyes to connect the operating device to a support element on the vehicle. The one fixing eye 8c is preferably mounted between the cylindrical area 6b and the electric motor 4.

The housing 6 and the f ixing eyes 8a to 8c can be made of metal such as cast aluminium or of plastics such as for example polyamide or fibrereinforced plastics such as for example glass fibre reinforced polyamide. Likewise individual areas of the housing can be made of metal and other areas can be made of plastics. The fixing eyes 8a to 8c are formed as hollow cylindrical areas which are injection moulded on the housing in advantageous manner. The axes of the hollow cylinder preferably stand perpendicular to the axis of the electric motor 4.

The plug connection 5 can also be provided as mechanical connection with snap fit connections so that the mechanical connection of the first subunit with the second sub-unit is also by means of the plug connection. The electrical plug connection serves for the electrical connection of the electric motor 4 and where applicable sensors arranged inside the housing or pole top of the engine, such as speed or path sensors, with an electronic control unit and/or electrical power supply.

The output element 7 is moved axially when the electric motor 4 is energised. At its end area the output element 7 has a substantially Lshaped area 10 which supports an attachment or a stud 11 for a ball joint, a universal joint or another connection. The housing in the area of 11 the axially movable output element 7 is sealed by means of a seal 9 such as folding bellows so that the one end area of the folding bellows 9a is connected sealingly to the output element and the other end area 9b is connected sealingly to the housing. The folding bellows 9 is preferably made of a flexible material.

The drive motor 4 has a base plate 4a which is fixed against a fitting surface 6a of the housing 6 by means of fixing means such as screws through the fixing openings in the base plate 4a.

The housing 6 has a tubular or cylindrical area 6b in which the output element 7 is substantially housed. This cylindrical area has in at least one partial area a tooth- an internal teething is provided in the inside of the housing 6b. it is advantageous if the housing 6b is made of plastics. The area of the inner teeth can preferably be formed in to the cylindrical housing section 6b in an injection moulding process.

like outer contour 12 since in this area The housing 6 has a housing cover 30 which can be fixed sealed on the housing by means of a sealing element. As sealing element can be used for example an 0 ring inserted into a circumferential groove of the housing 6. The cover 30 is fixed by fixing means such as screws on the housing 6. To this end socket areas 31 are provided on the housing with axial bore or thread which hold the screws.

Figure 2 shows a view of the second sub-unit 3 of the operating device 1 according to the invention. The subunit consists of a housing 20, a first housing part 21 and a second housing part 22 such as a base plate. Inside the housing 20 is the power and/or control electronics for controlling the operation of the clutch. The base plate 12 22 is made for example as a metal part and can simultaneously act as a cooling plate. The other housing part 21 can be made for example of plastics. The housing parts have openings 23a to 23c for assembly wherein the 5 alignment and arrangement of the openings 23a to 23c correspond to the alignment and arrangement of the openings 8a to 8c such as fixing eyes. The housing furthermore has concave areas 26 and 27 which serve as locators for the cylindrical elements of the first subunit 2 such as the cylindrical area 6b and electric motor 4. The area 28 is formed flat since this holds the housing area of the gearbox.

The housing of the second sub-unit 3 has electrical plug connections 24 and 25. The plug connection serves to connect the electric motor 4 through the plug 5 of the first sub-unit 2 to the electronics of the second sub-unit 3. The plug connection 25 serves to connect the operating device 1 with the power supply and the signal connection connects the operating device 1 to sensors and other control units for example through a data bus.

The two sub-units 2 and 3 can be mounted as self-contained modules or function units and can be checked for functional reliability as separate sub-units in the manufacturing process before they are connected together into one unit 1 in a further manufacturing step. This connection can however also be made only during assembly in the vehicle on the production line of the vehicle.

Figure 3 shows the assembly of the first sub-unit 2 with the second subunit 3 wherein the plug connection between the elements 5 and 24 is guaranteed.

The operating device 1 operates a clutch 500 in the drive train 507 of a vehicle 501 with an engine 502 anda 13 gearbox 503, on the output side of which is mounted a drive shaft 504 and driven axles 505 as well as driven wheels 506.

Figure 4 shows diagrammatically the mechanical structure of the operating device 100 starting from the engine 101 up to the output element 150. The drive motor 101 has an output shaft 103 on which a gear wheel 102 is mounted rotationally secured. The gearwheel 102 has for example a central socket which has a shape different from a cylindrical opening so that a non-cylindrical drive shaft 103 of the engine 101 can engage with keyed engagement in the socket. The gearwheel 102 meshes with an intermediate gearwheel 104 which is mounted rotatable on the axis 105.

The axis 105 is for example mounted or housed on one side at one of its end areas in the housing 6 or in the cover 30 of Figure 1. Likewise the axis can be mounted and housed on both sides at its end areas both in the housing and in the cover. The gearwheel 104 meshes with the gearwheel 106 to transfer the drive power on the engine side to the output element 150.

In a further embodiment according to the invention the gearwheel 102 can also mesh directly with the gearwheel 106 without the presence of an intermediate gearwheel. Furthermore in a further embodiment a second intermediate gearwheel could also be provided.

The arrangement of at least one intermediate gearwheel 104 has the advantage according to the invention that the gearwheels 102 and 106 are smaller with the sameaxial distance so that the structural space required by the gearwheels can be kept small.

A spindle 107 is in drive connection with the gearwheel 106 wherein between the spindle 107 and the gearwheel 106 14 there is preferably a slip clutch 108, shown only in part in Figure 4, which restricts the torque transferable by the gearwheel 106 to the spindle 107. The slip clutch thereby has two elements which are supported against each other in friction contact whereby the one element is part of a gearwheel or is connected for torque transfer therewith and the second element is connected for torquetransfer with the spindle or is formed in one piece with same.

The spindle is mounted rotatable in the area of the attachment or stud 109 in a housing of the device by means of a bearing, such as slide bearing or rolling bearing.

The spindle engages into a nut (not shown) which is connected rotationally secured to the cylindrical element 110 through a centring device. This rotationally secured connection can be formed for example by a pair of teeth, that is external teeth on the nut and internal teeth on the cylindrical element. A small number of teeth can indeed serve for the rotationally secured guide, such as at least one tooth of the nut engaging in a socket of the cylindrical element. Likewise the cylindrical element 110 can have at least one radially inwardly projecting element such as at least one projection which can engage into the socket of the nut. A rotationally secured connection can thus be produced between the cylindrical element 110 and the nut. The nut is formed by a component part with inner thread wherein the outer contour of the nut can assume a substantially cylindrical or even spherical shape which can be formed by recesses or settings of the teeth or similar.

Through the rotary movement of the spindle 107 the 35 rotationally secured but axially displaceable nut and the thus substantially axially fixed socket such as the cylindrical element 110 are axially displaced. The cylindrical element 110 has at its one area an articulation or socket area on which an energy accumulator such as spring, is at least supported or housed at its end area 120b. The energy accumulator 120 is supported or housed at its other end area 120a on the housing or on an articulation 121.

The output element 150 with a rod like element 112 is formed in one piece or in active or drive connection with the cylindrical element 110. An L-shaped component part is mounted at the end area of the element 113 and supports a ball head 114 of a ball joint or an articulation of an articulated connection.

Figure 5 as well as Figure Sa show in section a crosssection of the device 200 according to the invention for the automated operation of a clutch such as friction clutch. The control device can be mounted inside a subunit or however can also be mounted in a separate housing in another embodiment. Inside the one sub-unit is preferably the electronics control device 202 of the device wherein in another embodiment the control device is also mounted inside another such as separate housing. The control unit can also be mounted inside a central control device for example integrated with the engine control and/or gearbox control.

The actor such as the device for operating the clutch can 30 be formed as a sub-unit which is connectable with the sub- unit of the control device into a compact unit, such as structural unit.

The sub-unit 205 of the actor is electrically connectable by the plug 206 and socket 203 to the sub-unit ofthe control device. At the same time a mechanical connection is also produced by means of this plug 206 and socket 203 when the plug and socket engage in each other.

The plug connection 204 such as the socket or plug serve for the electrical connection and electronic signal connection between the device and the electrical power supply of the vehicle such as vehicle battery and other vehicle control control braking system, control units or with sensors. By other vehicle units is included at least one of the following units: engine control, gearbox control, anti- lock system control, anti-slip regulation control CAN bus etc.

The actor such as the mechanical operating device 205 has an electric motor 210. The motor 210 has an output shaft 211 which can be mounted at its end area remote from the motor inside the housing 220 of the actor 205. The shaft 211 can also be mounted inside the motor housing 221. A gear wheel 212 is mounted rotationally secured on the shaft 211. In one embodiment the gearwheel 212 is formed with internal teething 214 which is formed for example as notched teeth. This internal teething 214 engages with external teeth of the motor shaft 211. The gearwheel 212 is secured axially on the shaft by a security ring 213 such as a spring washer wherein the security ring engages in a circumferential groove of the shaft and secures the gearwheel against axial displacement.

The gearwheel 211 meshes with an intermediate gearwheel 215 which is mounted rotatable by means of the bearing pin 216. The bearing pin is to this end housed in atleast one of its end areas in a socket 217 of the housing. it is advantageous if the two axial end areas of the bearing pin 216 are housed in sockets 217. The sockets can be formed as holes or bores in the housing/housing cover with slide or rolling bearing.

G 17 The gearwheel 215 meshes with the gearwheel 225. The gearwheel 225 is mounted rotatable on the hub 226 by the gearwheel 225 having radially inside a surface which is housed rotatable or slidable radially outwards by the substantially radially outer face of the hub. The gearwheel 225 has on its one side radially inside the teeth 225a a radially circular ring shaped contact surface 227 which is in active connection with a counter contact face 228 of a friction ring 229. The friction ring 229 thereby has a radially expanded substantially circular ring shaped sector or arm which forms the counter contact face 228. Furthermore the friction ring 229 has an axially extended substantially ring shaped area 230. The axially extended or protruding area 230 has teething or at least a recess or a projection.

The friction ring 229 is force biased axially by an energy accumulator 231 such as a plate spring so that the contact face 227 of the gearwheel 225 is in friction connection with the counter contact face 228 of the friction ring 229. The energy accumulator 231 has on its radially outer edge area 231a a radially outer teething or at least one recess or projection. This teething or at least one recess or projection engages in a socket, teething or a projection of the friction ring 229 so that the energy accumulators 231 and the friction ring 229 are mounted or connectedtogether substantially rotationally secured.

The energy accumulator 231 has in its radially inner edge area 231b teething, at least one recess or a projection which engage in teething, projections or recesses provided for same so that the energy accumulator is connected rotationally secured to the hub 226.

The hub 226 has in its radially inner area an internal teething 232 such as for example notch teething which engages in radially outer external teething 233 of the spindle shaft 234 of the threaded spindle 235.

The gearwheel 225 is axially secured on the shaft 234 through the security rings such as spring washers236, 236a and the socket 237. The security rings 236 and 236a thereby each engage in circumferential grooves of the shaft 234. The socket 237 can be mounted or housed in a circumferential groove.

The force flow starting from the force introduction at the area of the external teeth of the gearwheel 225 is transferred through the contact face 227 and counter contact face 228 of the friction ring 229 and through the friction ring 229 and the external teeth 231a of the energy accumulator 231 through the inner teeth 231b of the energy accumulator to the hub 226 and from the hub 226 through the toothed pairing to the shaft 234 of the spindle 235.

The energy accumulator is pretensioned and produces a basic adhesive friction for torque or force transfer between the contact face of the gearwheel and the counter contact face of the friction ring. If the torque to be transferred is greater than the basic adhesive friction the arrangement becomes a slip clutch and the contact surface slips relative to the counter contact surface.

The shaft 234 is mounted both radially and axially in the housing 220 by means of the bearing 271, such as rolling bearing, grooved ball bearing, slide bearing or similar.

The bearing 271 takes up both radial forces and axial forces. The bearing 271 is fixed with an elastic such as resilient disc 272, such as energy accumulator inside the 19 - socket 220a. The housing 220 thus forms an attachment 220a which supports the radially outer bearing ring wherein the shaft supports the radially inner bearing ring. With axial forces appearing from the output side on to the output element the axial force is transferred from the output element through the nut to the spindle and from there through the bearing 271 to the housing where it is supported. This axial force is not guided through the slip clutch. Thus a moment shock on the output side according to the invention cannot lead to the slip clutch slipping through. The bearing socket of the bearing 271 is closed in sealed manner by a cover 273, such as cap, provided with a sealing ring 274.

The spindle 235 is housed by a nut 240 which is mounted by a spherical bearing 250 inside the plunger bearing. The plunger thereby consists substantially of a cylindrical element 241 inside which the nut 240 is mounted. The plunger rod 242 is connected to the cylindrical element 241 and in turn supports the output element 243. The plunger rod 242 is connected at its end area 242a to the cylindrical element 241. e.g. hung, clipped on, tensioned, screwed or stuck on. Likewise the cylindrical element can be made of plastics and injection moulded on the plunger rod.

rod has a thread or a predeterminable number of circumferential grooves which engage in the circumferential projections or threads of the cylindrical element. At its other end 242b the plunger rod 242 engages in a socket of the output element 243. The plunger rod engages through an opening 245 in which a spherical bearing 246 is mounted. Additionally the housing is protected by the elastic bellows 244 which are fixed at the relevant end areas by clamping rings on the plunger rod and on the output element and housing.

For advantageous connection the plunger - An energy accumulator such as a compression spring 245 is mounted between the plunger rod and housing in order to support the force of the electric motor.

The fixing eyes serve for fixing whereby at least two, preferably three fixing eyes are provided.

Figure 5b shows in an enlarged sectional view the spherical bearing 250 of the nut 240 of the spindle drive.

The spindle 235 drives the nut 240 which is formed so that it has a substantially spherical contour 251 and has radially inside a thread 252. On its radially outer area the nut likewise has teething 253 which engage in counter teething 254 of the cylindrical element. The nut is thereby coupled rotationally secured to thecylindrical element 241. The spherical nut 240 has in addition to the external teeth 253 two substantially semi spherical shaped areas. Inside the cylindrical element is a hollow cylindrical area which holds a first ring-shaped element which has a contour of hollow ball wherein the nut adjoins against this hollow spherical shaped contour. The nut is in turn held or housed by the second ring-shaped element 256 so that the ball is housed axially between the two ring-shaped elements 235 and 256. Furthermore an elastic ring 259 is mounted between the ring-shaped element 255 and the cylindrical element. This elastic ring 259 is preferably an 0 ring which tensions the two bearing shells 255, 256 towards each other and against the spindle nut 240.

The cylindrical element 241 has at its outer edge area teeth 257 which engage in counter teeth 258. The counter teeth 258 are formed so that the cylindrical element 241 is axially displaceable inside the housing but is nevertheless held rotationally secured by the teeth.

21 At least one of the bearing shells 255, 256 is preferably connected axially secured to the cylindrical element 241 by a snap-fit connection. At least one movable element of the bearing shells engages in a socket of the cylindrical element. This engagement produces a locking so that the part is mounted safe against loss.

The operating actor is preferably formed as a motor-driven actor with electric motor. The formation of the overall mechanics of the actor is such that a control device 201 can be pushed onto the mechanical components or connected therewith as further structural group or sub-unit. The control device is thereby stored in its own housing and sealed against the surroundings. This can preferably be reached by a seal between the housing and housing cover.

With one embodiment the housing of the control device is pushed onto the electrical /mechanical part such as sub- unit and screwed on additionally. The mechanical part can be used both for a fully integrated solution and also with a further embodiment wherein the mechanical part is stored separate from the control device.

The motor 205 thereby transfers the torque to a gearwheel or pinion 212 which meshes with an intermediate gearwheel 215 which in turn engages with a third gearwheel 225. The use of an intermediate wheel has the advantage that relatively small structural gearwheels can be used with given axial spacing. The axial spacing A in turn is produced from the motor diameter and the diameter required for the following spindle stage. This first transmission ratio stage consisting of at least two, preferably three gearwheels 212, 215, 225 represents a first reduction.

The torque is thereby increased and the speed lowered.

22 In a further embodiment a design of the first transmission ratio stage as a belt drive is also advantageous which is in the position, like the spur wheel stage described, both to produce the transmission ratio and to bridge a given axial spacing A.

A slip clutch is located in one of the gearwheels 212, 215, 225 preferably in the gearwheel 225 on the output side. This clutch serves to transfer the torque up to a certain torque transfer and on exceeding a certain torque moment to interrupt the torque flow. It can thereby be ensured that the mechanical components of the actor are not overloaded.

Furthermore the slipping through of the overload clutch can be sensed by the path measurement integrated in the actor and in conjunction with a conscious moving upof stops can serve to compensate the internal path measurement.

The gearwheel 225 on the output side drives a spindle 235 which in conjunction with a rotationally secured spindle nut 240 converts the rotary movement of the motor into a linear movement of an output element. This spindle 235 is mounted on one side close to the gearwheel 225 by means of a rolling bearing 241, preferably a grooved ball bearing.

This bearing takes up both radial forces from the teeth and from the output and also axial forces. The bearing itself is fixed with a resilient disc 242. The one-sided bearing of the shaft of the spindle allows slight angular mobility of the spindle relative to the housing. The spindle nut 235 has a substantially spherical geometry and is mounted outer in two likewise spherically designed bearing shells 255, 256. The spindle nut 240 furthermore has noses or teeth 253 on the circumference which engage with slight play in guide tracks 254 in a - 23 further output part 241 in which in turn the bearing shells 255, 256 are formed. This arrangement allows angular mobility between the spindle nut 240 and the output component 242. The torque can be transferred free of compulsion from the spindle nut 240 to the output component 242. The bearing shells 255, 256 are pretensioned with an elastic component preferably an 0ring 259 against the spindle nut 240. Thus on the one hand freedom of play is achieved between these component parts. Furthermore a possible retardation or wear of plastics parts which may be used is compensated within certain limits. The output component part 242 moreover serves to take up the forces which are applied by a spring 245 used for compensation. The spring 245 is thereby supported at its other end against the housing. The spring plate 260 in this arrangement undertakes the radial support of the output component part against the housing and the deflection of the torque. To this end the output component 241 likewise has on the circumference at least one nose or noses 257 or teeth which run axially displaceable with slight play in guide paths 258 of the housing and can transfer torque to the housing.

The guide paths 258 together form with the teeth 257 of thecylindrical element a straight guide wherein the guide paths 258 of the straight guide are worked into the housing of the device or are in one piece therewith. This can be achieved preferably by injection moulding using plastics. Thus no additional structural element will be used for the straight guide which according to the invention reduces structural space in the radial direction.

The output component 242 is mounted at a further point in 35 a spherical bearing 246 in the housing and is sealed with folding or rolling bellows 244 against the housing. This overall assembly reliably prevents the forcing of the spindle opposite the spindle nut or other parts against the housing.

The axial movement of the output component is transferred through a force introduction component such as a ball head

261 to the disengagement system of the clutch. An additional advantage of the arrangement described is that individual component parts can be varied individually to match other clutches. For example the transmission ratio of the spur wheel stage can be varied by retaining the spindle pitch wherein all other parts can be reused.

Figure 6 shows the individual parts 300 of the spherical bearing 301 and of the output element. The spherical bearing 301 consists substantially of the cylindrical element 310, which has a hollow cylindrical area 312, which has inner teeth 311 such as guide paths. At its one end area the cylindrical element 310 has in its one hollow cylindrical area 312 longitudinal slits 313 which divide the hollow cylindrical area 312 over a predetermined axial length into axial tongues 316. The tongues 316 have radially a predetermined elasticity. Inside these tongues there are at least in part openings 314 in which projections 330 of the at engage. The cylindrical engage in sockets of the housing rotation.

least one bearing shell 331 element has noses 315 which to secure against An O-ring 320 of elastic material is placed in the cylindrical element 310. A bearing shell 332 is then inserted which has a substantially hollow semi spherical inner contour 333. One side of the nut 340 with a semi spherical shape 341 is placed against this inner contour 333. The nut 340 has two semi spherical areas 341, 342 which are mounted and biased against one and the other bearing shells 332 and 331. Between the two semi spherical bearing areas 341 and 342 is a substantially ringshaped area of teething 343 wherein the teeth 343 engage in sockets 311. The plunger 350 is connected to the cylindrical element 310 and transfers the operating force of the electric motor to the clutch.

Figure 7 shows in a diagrammatic view a further embodiment of the device according to the invention. The electric motor 400 drives a wheel 401 on the motor shaft which is in driving connection through a contact element 403, such as toothed belt, belt, chain or the like, with a second wheel 402. The wheel 401 and the wheel 402 can each be formed as non-cogged wheel or as a gearwheel. The wheel 402 is in active connection with the spindle 404 and drives same.

Figure 8 shows a view of a slip clutch 500 in the spatial area inside a gearwheel 501 of the operating actor, preferably radially inside the teeth 502 of the gearwheel 501. The slip clutch 500 is in a further advantageous variation of the invention mounted both radially and axially inside the space required for the teeth 502 of the gearwheel 501. The gearwheel 501 has a contact face 502 which is biased by the counter contact face 504 of a ring shaped element 505, such as a friction ring- The contact face 503 of the gearwheel 501 is formed as a substantially circular ring shaped radially extended or extending face.

The face is flat. In another embodiment the contact face has an axially modulated surface.

The axially modulated surface 503 is comprised for example of different partial surfaces. The one partialsurface has viewed circumferentially a positive pitch in the axial direction and the other partial surfaces have viewed circumferentially a negative pitch in the axial direction 26 wherein each adjoining face alternate axially with this pitch. Viewed circumferentially this produces an axially modulated rising and falling slope path. A ramp ring is thereby formed which has alternately a surface with rising 5 surface part and a surface with falling surface part.

The counter contact surface 504 of the friction ring 505 is produced in its partial ring running in the radial direction wherein the axially protruding partial ring 505a supports teething 506 at the end area.

The energy accumulator 507 such as the plate spring has at its radially outer ring area teething 508 wherein the teeth of the teething 508 engage in the tooth spaces of the teething 506 and produce a rotationally secured keyed connection between the ramp ring 505 and the plate spring 507. The plate spring furthermore has in its radially inner edge area internal teething 509 which engage in the teething 511 of the hub 510. Thus a rotationally secured connection is produced between the plate spring 507 and the hub 510. The gearwheel 501, the slip clutch ring 505, the plate spring 507 and the hub 510 are housed on the shaft 520 and are axially secured by thediscs security rings 521, 522 and 523. The security rings as spring washers 521 and 523 thereby engage circumferential grooves 524, 525 of the shaft of spindle.

and such in the The energy accumulator 507 is installed in the gearwheel under pretension so that the pretension force ofthe energy accumulator 507 applies the required normal force so that the friction connection between the gearwheel and friction ring allows torque transfer.

In one embodiment it is advisable to design the mechanical components of the operating actor so that driving - 27 individual components against a rigid stop is possible. The dynamic strains can thereby be taken into account with predefined dimensions of the component parts.

In a further embodiment a further advantageous design is produced so that the inner stops of the actor are made softer and are driven up to same.

In a further embodiment a slip clutch or overload clutch is provided in the force flow of the operating actor between the drive and output to break or restrictthe force flow on exceeding a maximum force and thus protect the component parts of the operating actor against overload.

In an advantageous additional component additional structura clutch or overload reacts to inner and no useful actor path design no or only very few simple parts and no or only very little 1 space is required for the slip clutch. This overload protection outer stops. Through this mechanism is lost.

Identifying the slip-through can be carried out simply with software technology whereby for example when the motor is energised or with a given drive power a high speed of the drive without a correspondingly high operating speed of the output is detected. Likewise in a further embodiment it can be detected when the motor is fully charged.

With a suitable design of the components it is possible to utilise a conscious release, thus conscious movement against the stop to compensate the sensors for incremental path measurement.

28 - In an embodiment of the actor the path sensor for position regulating the electric motor is designed as an analogue system. One advantage of the analogue system is that the signal which can be measured in analogue manner contains 5 direct information on the absolute position of the releasable clutch. The engagement state of the clutch can thus be detected accurately and reliably at each time point. Driving against a known stop can thus be reliably prevented through the control.

In another embodiment the actor has an incremental path measurement. The incremental path measurement can only measure a relative position change. The absolute position is for example calculated by counting or integration. if counting errors occur then the measured position drifts away from the real position and a fault in determining the absolute position or engagement state occurs.

In one embodiment of the invention an over-moment coupling is proposed. Very good response behaviour with low hysteresis and exact coupling points are offered by embodiments wherein, when released, rolling bodies roll on defined curved paths. These rollers can be mounted in Figure 8 between the contact face and counter contact face.

Slip clutches utilise only the friction value and the contact pressure force for defining the breakaway moment.

An advantageous embodiment is produced in the form of ramp rings. Through the action of steep planes of the individual partial faces of the contact face and counter contact face the normal force required is reduced.

Through this structural space integrated arrangement no additional is required. The overload clutch consists substantially of the parts shown in Figure 8, the gearwheel 501, ramp ring 505, plate spring 507, hub 510 and run-up disc 522. In addition two security rings 521 and 523 are shown here for axial fixing. The drive is produced through the teeth of the gearwheel, the output is produced through the output shaft shown here as a spindle 524.

The gearwheel 501 is advantageously made of plastics wherein a fibre reinforced material such as glassfibre reinforced polyamide (PA) or polyoximethylene (POM) can be used. Thus the first ramp ring 503 can be produced at practically neutral cost in the gearwheel, for example can be injection moulded by the injection moulding technique.

The second ramp ring 505 is pressed by a plate spring 507 against the first ramp ring 503. The second ramp ring can be formed as a plastics part or as a metal part, such as sheet metal part. The plate spring 507 serves to produce the contact pressure force to transfer the torque from the ramp ring 505 to the hub 510 and as axial tolerance compensation.

Furthermore the plate spring 507 can be used to axially pretension further elements which directly adjointhe structural group (for example the inner ring of a rolling bearing) and thus to mount same play-free. The hub 5 10 directs the torque from the plate spring 507 to the output shaft 524 which is designed here as a spindle. To this end the hub 510 has on the outside round the circumference short webs to introduce moment and teeth (not shown) on the inside, for example notched teething or a polygon or a wedged groove profile. The external teeth of the shaft 520 engage in the inner teeth of the hub 510.

The gearwheel 501 is advantageously mounted radially without further socket on the hub 510 since the gearwheel - 501 turns opposite the hub 510 only in the event of release and then only few parts of a turn. The hub 510 can possibly be formed as a cold-shaped part, as a rotary milled part or as a cast zinc part. The hub 510 is used to introduce torque into the shaft 520.

The gearwheel 501 runs opposite the ramp ring 505 against a simple disc. The elements for axial fixing are marked 521 and 523.

In normal operating mode the moment or force flow takes place from the gearwheel 501 through the inclined ramp faces to the ramp ring 505, from there through the outer tongues to the plate spring 507, from the plate spring 507 through the inner tongues to the noses of the hub 510 and from the hub 510 into the output shaft 520.

The gearwheel is here shown without gear rim and in section, with structurally fixed moment the ramp rings lift away from each other whereby the moment flow is at first interrupted, and later possibly even reversed when the ramps engage in each other again. The sharp moment drop through a relatively large turning angle is good enough to be recognised by the control. Thus a slipping of the clutch is characterised by the correlation engine moment drop and high turning angle or high speed. With the presence of both signals a slipping can then be identified by the control unit. Even if the dynamic load is not sufficient to bring the overload clutch to slip through fully, the rising force path over the ramp path leads to good detection of the stop. The overload clutch acts up to release like a soft stop, in any case also on reaching an external obstruction.

Figures 9a and 9b show an embodiment of Figure 8 in side view. The gearwheel 501 is thereby shown without external 31 - teeth 502. The contact face 503 is shown with its ramplike configuration. The counter contact face 504 is formed with the axially extended edge area. The contact face 503 and the counter contact face 504 are not turned relative to each other and contact one another substantially over an entire surface. Furthermore the teeth 508 of the plate spring 507 are shown in engagement with the teeth of the ring area. Likewise the hub 510 is seen radially inside the energy accumulator whereby the arrangement of the hub and gearwheel are secured axially through the security rings 521 and 523 and furthermore the run-up disc is mounted axially between the spring 550 and the gearwheel 501.

Furthermore the opposing circular ring shaped faces of the slip clutch biased by means of the energy accumulator such as plate spring 508 have two repeating circular ring shaped segments 552 and 553 wherein the one segment 552 has a rising pitch and the other segment 553 has a falling pitch viewed circumferentially and these segments have an extension in the axial direction.

In Figure 9b the gearwheel is turned relative to the friction ring 504 so that slipping through can be detected from the non- surface contact of the parts 503 and 504.

Figure 10 shows a further design according to the invention with two flat friction faces 503 and 504 which are opposite one another.

The embodiments described above have an actor with a motor with motor output shaft which is rotatable about an axis.

After the motor output shaft is a two-stage gearbox which in a f irst stage contains a spur wheel gear and as the second gear stage has a spindle gear. At least one of the gear stages can also be formed by means of chain wheels - 32 and a chain or with other contact gearbox or traction means gearbox, such as toothed belt drive. Furthermore a spur wheel step can be used with an intermediate gearwheel. In a further application case it can be advantageous if the axes of the electric motor and an output element are connected through a bevel wheel gearbox wherein the axes are mounted parallel or with an angle other than 180 degrees so that the axes cross one another at least in their extensions. An electric motor is fixed on the actor housing and a spur wheel is located on the shaft and is connected rotationally secured to same. Through this spur wheel a second spur wheel is driven which is mounted rotatable but non-displaceable in the housing. The spur wheel is mounted rotatable by the bearing and is axially fixed. This axial f ixing of the bearing and thus of the spur wheel can take place by means of a holding and securing element. The teeth of the spur wheel are meshed by the teeth of the spur wheel so that a drive connection is produced. The second spur wheel undertakes the function of the nut of the spindle gear. The gear wheels can be formed for example as an injection moulded part or as metal parts wherein the nut of the spur wheel can be formed as a threaded sleeve. The nut need not however be formed as a solid nut with thread in the spatial area around 180 degrees. The nut can also be formed as an angular segment with an angular area of the teeth of less than 360 degrees, such as advantageously less than 180 degrees. The spindle is mounted in the housing by means of a torque -supporting linear guide so that this bearing can at the same time undertake the function of an antirotational lock.

accumulator is mounted coaxial with the at its one end adjoins the housing and at housed by a socket element such as a active connection with the spindle accumulator supports the electric motor An energy linear guide and the other end is pot which is in The energy during operation of the torque transfer system wherein this spring is supported both on the housing and on the plate.

In the illustration of the actor there are two 5 possibilities for connecting an output part wherein on the right hand side a master cylinder or a disengagement lever can be attached in the area directly or through an articulated joint. On the left hand side of the drawing a Bowden cable for example can be attached in the area or likewise directly a disengagement lever wherein the output element is biased with traction and the output element is biased with pressure.

With one design with only one output element, one side or the other can be closed by the housing.

Furthermore an embodiment can be formed so that the energy accumulator in reverse manner biases the spindle. It is the end fixed on the housing facing the spur wheel wherein the movable end of the energy accumulator is remote from the spur wheel. It is thereby reached that the force direction of the torque transfer system is opposite the force direction of the actor. Thus in one area an operating pressure is applied and in another area an operating pull is applied. Through this exchange of traction and pressure forces it may be necessary to exchange the spring bearings such as the spring bearing fixed on the housing or the entrained spring bearing. The linear guide likewise changes the position in this embodiment.

The above illustrations show an actor with a multi-stage such as twinstage gearbox wherein the first stage is a spur wheel gear and the second stage is a spindle gear. The spur wheel is mounted rotatable but axially fixed by a bearing and the body of the spur wheel forms the nut of 34 the spindle gear wherein the spindle is mounted rotationally secured but axially displaceable by means of a bearing, such as linear guide.

A further variation has a motor which drives the spur wheel by means of the motor shaft wherein the spur wheel drives the spur wheel which ismounted rotatable but axially fixed by means of the bearing. The spur wheel has an extension which is connected to the threaded spindle.

Thethreaded spindle engages in the nut which is mounted rotationally secured but axially displaceable wherein the output element is the slider of the nut. In this embodiment the spindle rotates with the spur wheel and the rotational lock or linear guide is mounted between the spindle and spur wheel wherein the nut rotationally secured but axially displaceable.

is mounted A further variation has a drive motor which drives by means of the motor output shaft a spur wheel which in turn drives a spur wheel. The spur wheel is mounted rotatable but axially fixed by the bearing. The spur wheel and spindle are mounted rotationally secured but axially displaceable relative to each other and the nut of the spindle gear is mounted rotationally fixed with the housing so that during rotation of the spindle the spindle is moved axially at the same time.

A further variation shows a motor with a motor output shaft and a spur wheel and further a spur wheel which is mounted axially fixed and rotatable by means of the bearing. The nut is mounted with the spur wheel rotationally fixed but axially displaceable and the threaded spindle is mounted fixed on the housing so that during rotation of the spur wheel the nut is set in rotation and is axially displaced so that the element can act as an operating element.

- The patent claims filed with the application are proposed wordings without prejudice for obtaining wider patent protection. The applicant retains the right to claim further features disclosed up until now only in the description and/or drawings.

References used in the sub-claims refer to further designs of the subject of the main claim through the features of each relevant sub-claim; they are not to be regarded as dispensing with obtaining an independent subject protection for the features of the sub- claims referred to.

The subjects of these sub-claims however also form independent inventions which have a design independent of the subjects of the preceding claims.

The invention is also not restricted to the embodiments of the description. Rather numerous amendments and modifications are possible within the scope of the invention, particularly those variations, elements and combinations and/or materials which are inventive for example through combination or modification of individual features or elements or process steps contained in the drawings and described in connection with the general description and embodiments and claims and which through combinable features lead to a new subject or to new process steps or sequence of process steps insofar as these refer to manufacturing, test and work processes.

36

Claims (53)

1. operating device for automated operation of a clutch in the drive train of a motor vehicle with a first sub unit which has a drive motor and an output element on the output side, as well as with a gearbox converting the drive movement of the drive motor into an output movement with a second sub-unit which has an as power and/or control electronics, the f irst and second sub units are module and can be by a mechanical an electrical plug an electrical plug are connectable electrical plug of the output element, electronics unit such characterised in that each formed individually as a closed connected into one structural unit connection and the first sub- unit has connection and the second sub-unit has connection and the two sub-units electrically by means of these connections.

2. operating device according to claim 1 characterised in that at least one of the two sub-units has its own housing and the sub- unit with the housing is formed as a module closed per se.

3. Operating device according to claim 1 or 2 characterised in that at least one sub-unit provided with a housing is formed as a sealed sub-unit dust-tight and/or fluid-tight, such as water-tight.

4. Operating device according to claim 1 or 2 characterised in that a mechanical connection is provided between the sub-units by means of the electrical plug connection.

5. Operating device according to claim 1 or 2 characterised in that a mechanical connection is formed between the two sub-units by means of at least one mechanical keyed snap- fit connection.

6. Operating device according to claim 1 or 2 characterised in that a mechanical connection is formed between the sub-units by means of at least one connecting means such as a screw, rivet or adhesive connection.

7. operating device according to one of the preceding 10 claims characterised in that a mechanical connection is formed between the subunits by means of at least one connecting means and this at least one connecting means also serves to fix the complete structural unit inside the motor vehicle.

8. Operating device according to claim 1 or 2 characterised in that the one electrical plug connection is formed as a plug and the other electrical plug connection is formed as a socket.

9. Operating device more particularly according to claim 1 characterised in that the housing of the second sub-unit which holds an electronics such as power and/or control electronics unit consists of at least two housing shells which are connectable together.

10. operating device more particularly according to claim 1 characterised in that at least one housing shell of the second sub-unit consists of plastics.

11. operating device more particularly according to claim 1 characterised in that at least one housing shell of the second sub-unit consists of metal.

12. operating device more particularly according to claim 1 characterised in that the second sub-unit has a further 38 electrical plug connection for producing an electrical connection with other vehicle electronics units and/or sensors.

13. operating device for the automated operation of a clutch in the drive train of a motor vehicle with a drive unit such as drive motor and an output element on the output side, as well as with a gearbox converting the drive movement of the drive motor into an output movement of the output element, characterised in that the gearbox has at least two partial gearboxes and a slip clutch is mounted in the force flow between the drive unit and output element of the device.

14. Operating device according to claim 13 characterised in that the gearbox consists of at least two gearbox parts and one gearbox part has at least one spur wheel gear.

15. Operating device according to claim 13 characterised in that the gearbox consists of at least two gearbox parts and one gearbox part has at least a spindle gear.

16. Operating device according to claim 13 characterised in that the spindle gear is connected in the force flow after the spur wheel gear.

17. Operating device according to one of claims 13 to 16 characterised in that the spur wheel gear is formed as a single-step gearbox with two meshing gearwheels such as spur wheels wherein one gearwheel is mounted in the force flow on the drive side and one gearwheel is mounted in the force flow on the output side.

18. Operating device according to one of claims 13 to 16 characterised in that the spur wheel gear is formed as a twinstage gearbox with three gearwheels such as spur wheels wherein each two gearwheels mesh with each other and a gearwheel on the drive side and a gearwheel on the output side as well as an intermediate gearwheel are mounted in the force flow.

19. operating device according to one of claims 17 or 18 characterised in that the gearwheel on the drive side is housed rotationally secured on an output shaft of the drive unit.

20. Operating device according to one of the preceding claims 13 to 19 characterised in that the slip clutch is mounted in the force flow between the gearwheel of the spur wheel gear on the output side and the element of the spindle gear such as spindle on the drive side.

21. operating device according to one of the preceding claims 13 to 18 characterised in that the slip clutch is mounted in the force flow between the output shaft of the drive unit and the gearwheel of the spur wheel gear on the drive side.

22. Operating device according to one of the preceding claims 13 to 21 characterised in that the slip clutch is mounted radially inside the spatial area provided for the teeth of a gearwheel of the spur wheel gear.

23. operating device according to one of the preceding claims 13 to 22 characterised in that the slip clutch is mounted axially inside the spatial area provided for the teeth of a gearwheel of the spur wheel gear.

24. Operating device according to one of the preceding claims characterised in that the slip clutch is integrated in a gearwheel.

-

25. Operating device more particularly according to one of the preceding claims characterised in that the slip clutch has a first element which supports a first contact surface and a second element which has a second counter contact surface wherein the two elements are biased against each other by means of an energy accumulator.

26. Operating device according to claim 25 characterised in that the energy accumulator is a plate spring.

27. Operating device according to claim 25 characterised in that the energy accumulator is a coil spring with round, oval or angular wire-like material cross-section.

28. operating device according to claim 25 characterised in that the energy accumulator is an undulating spring with round, oval or angular wire like material crosssection.

29. operating device according to claim 25 characterised in that the first element supporting the first contact surface is formed integral with a gearwheel.

30. operating device according to claim 25 characterised in that the first element supporting the first contact surface is connected in keyed engagement with a gearwheel.

31. Operating device according to at least one of the preceding claims characterised in that the first element supporting the first contact surface is formed with a substantially circular ring-shaped friction or contact surface.

32. Operating device according to one of the preceding claims characterised in that the second element supporting - 4 1 the second contact surface is formed as a substantially circular ring shaped element.

33. Operating device according to one of the preceding claims characterised in that the circular ring shaped element has an arm extending substantially in the radial direction and supporting the contact surface.

34. Operating device according to one of the preceding claims characterised in that the circular ring shaped element has an arm extending substantially in the axial direction and producing a keyed connection with an energy accumulator.

35. operating device according to at least one of the preceding claims characterised in that the first and/or second substantially circular ring shaped friction surface or contact surface is flat.

36. operating device according to at least one of the preceding claims characterised in that the first and/or second substantially circular ring shaped friction face or contact surface is formed as an axially modulated shape or contour.

37. operating device according to at least one of the preceding claims characterised in that the axially modulated shape or contour of the friction surface is formed so that a part of the circular ring segments of the friction surface, viewed in the circumferential direction has a rising pitch in the axial direction and another part of the circular ring segments of the friction surface, viewed in the circumferential direction, has a falling pitch in the axial direction wherein the segments alternate with rising and falling pitch.

42

38. Operating device according to claim 37 characterised in that the amount of the incline of the falling segments is equal to the amount of the incline of the rising segments.

39. Operating device according to claim 37 characterised in that the amount of the incline of the falling segments is not equal to the amount of the incline of the rising segments.

40. operating device according to one of the preceding claims characterised in that at least one of the two elements is biased by means of at least one energy accumulator such as plate spring and the contact surface and counter contact surface are thereby biased relative to each other in friction contact.

41. operating device according to one of the preceding claims characterised in that the first element which supports the contact surface is the gearwheel on the output side.

42. operating device according to one of the preceding claims characterised in that an output shaft of the drive unit and the axis of the output element are mounted parallel to each other.

43. operating device more particularly according to one of the preceding claims characterised in that the spindle gear has a threaded spindle and a nut wherein the nut is mounted axially movable but rotationally secured relative to the housing by means of a bearing.

44. operating device according to at least one of the preceding claims characterised in that the nut is mounted - 43 rotationally fixed relative to the housing but movable with adjustable angle by means of a spherical bearing.

precedin

45. Operating device according to at least one of the claims characterised in that the spherical bearing is formed so that the nut has a substantially spherical contour with two substantially semi-spherical surfaces such as side faces and teeth are provided between the surfaces wherein the spherical faces are housed axially inside one hollow cylinder of two axially biased semi spherical shells wherein the hollow cylinder has internal teeth for holding the teeth of the nut and the cylinder is held axially movable but rotationally secured in teeth inside the housing by means of external teeth.

46. operating device according to claim 45 characterised in that at least one semi spherical shell of the spherical bearing is connected rotationally secured to the hollow cylinder.

47. Operating device according to claim 45 characterised in that at least one semi spherical shell of the spherical bearing is connected axially secured to the hollow cylinder by means of teeth or snap-fit connection.

48. Operating device according to claim 45 characterised in that the two semi spherical shells and the nut are biased against each other by an elastic element.

49. operating device according to claim 48 characterised in that the elastic element is an energy accumulator such as a spring.

50. Operating device according to claim 48 characterised in that the elastic element is a plastics or elastomer element such as rubber ring.

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51. Operating device according to at least one of the preceding claims characterised in that between the housing of the device and the output element or an element connected therewith is an energy accumulator which exerts spring force on the output element.

52. operating device for operating an automated clutch characterised by its special configuration and method of 10 operation according to the present application documents.

53. Operating device for operating an automated clutch substantially as herein described with reference to the accompanying drawings.