DE2846862A1 - CLUTCH GEAR UNIT - Google Patents

Description

DIPL-CHEM. DR. ELISABETH JUNG 8000 NGdCKcN to,

DIPL-PHYS. DR. JÜRGEN SCHIRDEWAHN "Q- SUS ¹ ' ¹

DR.-ING. GERHARD S CH M ITT-N I LSON
PATENT LAWYERS

u.Z .: L 932 M + a (Dr.SchN / hm / ez) October 27, 1978

ELERO AG

Dällikon / Switzerland

"Clutch gear unit"

The invention relates to a clutch gear unit.

It has already been proposed to provide both a slip clutch and a disengagement clutch in a transmission. However, the slip clutch and the release clutch were provided as separate units.

The invention is based on the object of a clutch containing both a slip clutch and a release clutch To create clutch transmission unit with a particularly compact structure. A compact structure is also particularly important in applications Advantageous, as they are specified in the usage claims, where often cramped space conditions prevail,

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because you move the clutch gear unit as close as possible to a wall or the ceiling of the corresponding room
would like to.

The clutch gear unit is used to solve this problem
designed as indicated in the characterizing part of claim 1. Under "combined slip and release clutch"
it is understood that at least one component is both part of the slip clutch and part of the release clutch. A gear wheel or a worm wheel is particularly suitable as a torque-transmitting wheel; however, a belt pulley or V-belt pulley or a friction wheel, for example, is also conceivable.

Another solution to the problem on which the invention is based is characterized in claim 2. This second solution can
can also be combined with the first solution discussed above.

The release clutch of the clutch transmission unit can preferably be actuated from outside the housing. Compared to a clutch actuation from the inside, which is also possible in principle, this is the more space-saving option. The release clutch can be operated manually or, for example
externally operated, in particular by an electric motor, electromagnetically, by pressure fluid and the like., take place. Manual actuation and actuation by means of an electromagnet are particularly preferred.

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A further development of the invention which further improves the compactness of the clutch transmission unit is specified in claim 4. The accommodation of the bolt for engaging or disengaging the clutch in the interior of the shaft saves compared other release mechanisms outside the shaft.

The first coupling part is generally annular Coupling surface. To transfer the engagement force or the disengagement force from the bolt arranged in the shaft the larger diameter of the first coupling part is a transverse bolt protruding radially inward from the first coupling part preferred. This cross bolt extends, for example, through a radial one that is elongated in the axial direction of the shaft Long hole in order to enable the axial movement of the first coupling part without hitting the cross bolt.

The ones required to engage or disengage the disconnect clutch Forces are generally relatively large, so that a force transmission is advantageous. There are numerous for this Possibilities such as levers, hydraulic or pneumatic power transmission, etc. In a further development of the invention is a Power transmission with the help of an eccentric is particularly preferred. This eccentric acts preferably on the bolt mentioned.

In claims 7 and 8 are particularly space-saving options to adjust the play of the clutch or to readjust the clutch. The further training according to claim 8 has the particular advantage that you can also from the outside without dismantling work, -simple way the Aus

can adjust feedback.

The further development of the invention characterized in claim 9 offers the advantage that the torque-transmitting wheel at the same time serves as a second clutch part, which means a structural simplification of the clutch gear unit and in turn contributes to a further increase in compactness. The second ring pushes through the spring (s) between the first and the second ring the first ring against the first coupling surface. As will become clearer below, one can use the To engage or to disengage the first ring, either move the first ring axially directly or this displacement with the help of the second ring indirectly via the spring (s) make.

The slipping torque of the combined slipping and disengaging clutch is preferably adjustable, i.e. not just one Leave the design to be determined when designing the clutch gear unit. This is particularly easy . • Adjustability through axial adjustability of the second · Realize rings. When engaging or disengaging the first ring by moving the second ring, an adjustment of the play of the disengagement clutch also automatically leads to an adjustment of the slipping torque the slip clutch, as in the exemplary embodiments below will become even clearer.

In addition to this option, preferred options of the

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constructive solution of the axial adjustment of the second ring are given in claims 13 and 14.

If the clutch gear unit is used for speed reduction / the slip and release clutch is preferably arranged on a shaft, which is at least after the first speed reduction stage lies. In this way, the slip and release clutch does not rotate with the generally relative high input speed of the clutch gear unit, so that when the slipping clutch slips, the speed differences are not so great occur at the slip point, which is beneficial from the point of view of heating. If more than one speed reduction stage is provided, the slipping and disengaging clutch must be attached the or a shaft of medium speed favorable, since on the one hand the above-mentioned aspect of the reduced Speed difference already comes into play and there on the other hand the contact pressure of the clutch is not as great as it would be when it is mounted on the slowest gear shaft should be. In particular, also from the point of view of heating the slip and release clutch when slipping Running the slipping and disengaging clutch in an oil bath is beneficial, as this dissipates the heat from the actual slipping point will.

Particularly preferred areas of use of the invention Clutch gear unit are specified in claims 17-20. Except for the compactness, which is a very close proximity the drive shaft of the clutch gear unit to a wall

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or on the ceiling of a room, for example also a direct attachment to the usually relatively close to the The spring shaft of a sectional door attached to the wall and / or to the ceiling of a room has the clutch gear unit according to the invention nor the advantage that in the event of any malfunctions, for example in the event of a power failure, the clutch can be disengaged from the outside can be disengaged. Then the drive of the respective object to be driven, for example gate, window, rolling grille etc., done by hand. For this one can preferably provide a connection option for a manual emergency operation, and this can be done, for example, by a crank or a Pull chain take place, whereby the manual drive can act on the shaft on which the slip and disengagement clutch is also located is located. For installation cases in which the clutch gear unit Located up near the ceiling of a room is preferred for an actuation option of indentation or disengaging the clutch from the floor of the room. This can be done, for example, by means of a non-rotatable connection an operating rod with the eccentric or by providing a chain or rope that is attached to a shaft on which the Eccentric is attached, acts, done. Also a shaft deflected downwards, for example with the help of joints, which is used to rotate the eccentric, fulfills this purpose. The operability of engaging or disengaging the The clutch can also be released through appropriate openings in the wall from outside the room in which the clutch gear unit is located is arranged, provide.

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The clutch transmission unit according to the invention is explained in more detail below with the aid of partially schematic drawings of two exemplary embodiments.

1 shows a section through the most functionally essential area a first embodiment of a two-stage clutch gear unit with combined slip and Release clutch; and I.

2 shows a section through the most functionally essential area of a second exemplary embodiment of one Side adjustable and disengageable clutch gear unit.

Fig. 1 shows the most functionally essential parts of a two- ' stage clutch gear unit. Training with additional levels is possible. In this embodiment is a countershaft 3o designed as a hollow shaft is supported at both ends with a roller bearing 32 in the housing 2. The left roller bearing 32 is attached to a shaft end 34 designed with a smaller shaft diameter and is supported to the right against the central region 36 of the countershaft 3o. From the outside of the housing 2 is against the upper shell of the left roller bearing 32 a rotationally symmetrical end plate 38 opposed / the means

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Screw ο. Like. Is fixed in the housing and to the left directed axial forces occurring in the clutch transmission unit. The end plate 38 is in a stepped Inner bore 4o of the housing 2 sunk. The inner flange of the end plate 38, on its peripheral edge an oil-tight Sealing is arranged, protrudes into the smaller diameter inner bore 4o of the housing 2, in which the left roller bearing 32 is arranged. The end plate; 38 is provided with an inner bore 39 in which the shaft end 34 runs out. At a clear distance from the left roller bearing 32 are on the countershaft 3o from left to right a steel ring 44, hereinafter referred to as a second steel ring, and a first steel ring 46 arranged. Both steel rings 44 and 46 point in their facing end faces over the circumference distributed, wherein the areas of the transverse bores are omitted, several circular recesses 48, which for receiving of clutch compression springs 5o between the two steel rings 44 and 46, preferably spiral springs, are determined. The steel rings 44 and 46 are arranged mirror-symmetrically to one another, so that the respective recesses 48 to one another demonstrate. The end faces 47 of the steel rings 44 and 46 facing away from one another are both designed to be planar and closed.

The first steel ring 46 protrudes about halfway into a countersunk inner bore 52 of a countershaft 3o arranged.

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Neten worm wheel 54. The end face 47 of the first steel ring 46 is opposite in the inner bore 52 of the Worm wheel a preferably oil resistant. Friction lining 56 arranged, which is firmly riveted, glued or otherwise connected to the worm wheel 54. This attachment however, this is not necessary if a further coupling surface is provided between worm wheel 54 and friction lining 56 is.

On the right side of the worm wheel 54 there is a further countersunk inner bore 58, which, however, is a smaller one Depth than the inner bore 52 has. Both inner bores 52 and 58 have approximately the same diameter. In the right Inner bore 58 of worm wheel 54 is a steel disk 6o on countershaft 3o as a contact surface for the worm wheel 54 provided. The steel disk 6o is in turn supported axially against a gear 62, which by means of parallel key 64 is attached to the countershaft 3o. This gear 62 meshes with a driven gear 66 (not shown) larger Diameter. The gear wheel 62 is opposed by means of a shaft collar 68 with a larger diameter than the central area 36 a shift to the right secured. The countershaft is stepped to the right of the shaft collar 68 with a smaller diameter educated. This right shaft end 7o is supported by the right roller bearing 32 in the housing 2. The right one Part of the housing 2 faces from the inside to the outside

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seen first a hole 72 in which the right roller bearing 32 is arranged. The bore 72 is adjoined to the outside by an enlarged bore 74 of larger diameter.

Symmetrical to the axis of the countershaft 3o is in the extended Bore 74 a circumferential flange 76 of an eccentric housing 78 used. The circumferential flange 76 protrudes with an annular extension 8o, on the outer circumference of which an oil seal is arranged is, into the bore 72 and there lies against the outer shell j of the roller bearing 32. This system between rolling bearings 32 and Extension 8o can also take place via a support ring arranged between them. The eccentric housing 78 is over the peripheral flange 76 with screws, e.g. countersunk Allen screws, attached to the housing 2 and thus sets the right roller bearing 32 against axial forces directed to the right.

The first and second steel rings 44 and 46 each have a transverse bore 82 and 84 or a radial bore perpendicular to their axis on. In each transverse bore 82 or 84 is a transverse bolt 86 or 88, which is preferably made of hardened steel, arranged. These cross bolts 86 and 88 are each attached one perpendicular to the axis of the countershaft 3o Long hole 9o or 92 axially displaceable within certain limits. The cross bolts 86 and 88 are by means of in the peripheral wall of the steel rings countersunk screws 122 in radial

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Direction from one side / possibly also from several sides, fixed. The inner diameter of the steel rings corresponds to the outer diameter of the countershaft 3o, with sufficient play for axial displacement of the steel rings. The outer diameter of the first steel ring 46 is dimensioned such that there is a small play between it and the inner bore 52 of the worm wheel 54. This play is required to disengage the clutch. ^: '

The left shaft end of the countershaft 3o has an inner bore 94, which merges into a further inner bore 96 of smaller diameter. The inner bore 94 is internally threaded 98, into which an adjusting screw 1oo, e.g. as an Allen screw or set screw, is screwed from the left. ' The adjusting screw 1oo acts with its flat end surface on a complementary surface of a sliding bolt 1o2, which is in the Inner bore 96 is arranged displaceably with a smaller diameter. The right end 1o4 of the sliding bolt 1o2 has a cylindrical recess for adaptation to the circumference of the transverse bolt on. The end of the sliding bolt can also be made flat and a milled cut can be made on the circumference of the transverse bolt. the Inner bores 39 and 96 each have seals with respect to the shaft end 34 or with respect to the sliding bolt 1o2.

The right part of the countershaft 3o also has one Inner bore 1o6. The inner hole 1o6 is used for guidance

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of a pressure pin 1o8 inserted from the right, the left one End in the shape of a segment of a circle with the first transverse bolt 86 in engagement stands and its right end with a smooth surface can be acted upon by an eccentric shaft 11o. The eccentric shaft 11o extends preferably at right angles to the axis of the countershaft 3o. The pressure pin 1o8 is on its right The end region is guided in a bore 112 of the eccentric housing 78 that is aligned with the axis of the countershaft 3o. In the hole 112 is a seal, e.g. an oil-tight O-ring seal, intended. The eccentric shaft 11o is in a larger bore 114 running perpendicular to the bore 112 in the eccentric ■ housing 78 arranged. In FIG. 1 there is a right end face of the pressure pin 1o8 and the eccentric shaft 11o little play. In this state, the annular surface 47 of the first steel ring 46 lies with the one set via the adjusting screw 1oo Force against the friction lining 56 by means of the springs. The worm wheel 54 shown in Fig. 1 is for example of a worm shaft 114 (not shown) arranged below the countershaft 3o and extending perpendicular to it driven, which meshes with the worm wheel 54. This gear connection is, as in the second embodiment, self-locking.

The steel rings 44 and 46 have an inner bore that

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is slightly larger than the outer diameter of the countershaft 3o in the arrangement area. The outside diameter of the steel rings however, it is kept somewhat smaller than the diameter of the inner bore 52 of the worm wheel. This ensures that a relatively low-friction axial displacement of the steel ring (s) 44 or 46 can take place.

The respective circular recesses are ring-shaped in an axial view symmetrically to the axes of the transverse bores 82 and 84 arranged distributed. One of the steel rings has protruding pins on the front side, which are used for guidance and prevention mutual rotation of the steel rings protrude into corresponding bores 118 of the other steel ring.

The recesses 48, which are approximately U-shaped, are intended to receive the clutch springs 5o. In the exemplary embodiment according to FIG. 1, coil springs are 5o as clutch springs used. However, other suitable springs, for example disc springs, which do not have any recesses, may also be used 48 need to be used. The respective transverse bolt 86 or 88 can pass through a steel ring from one side are introduced into the transverse bore 82 produced with the most accurate fit possible. From the other, the bringing-in side opposite side is the cross bolt 86 or 88

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fixed with a countersunk screw 122 in the steel ring 44 and 46, respectively. The most accurate possible fit between the cross hole and the corresponding cross bolt is necessary so that axially acting Transferring the setting forces of the slipping torque or disengagement forces during the disengagement to the steel rings without play will.

The clutch transmission unit with combined slip and disengagement clutch is engaged in FIG. 1. The ring surface 47 of the first steel ring 46 lies with the through; Adjusting screw 1oo set force against the friction lining 56 at. When power is transmitted by a drive, e.g. an electric motor acting on the worm shaft 114 (not shown), the worm wheel 54 rotates according to the reduction ratio between worm wheel and worm shaft. Until the set slipping torque is reached the first and the second steel ring are entrained by the transmission of frictional force between the first steel ring 44 and the friction lining 56. The cross bolts 86 and 88 transmit the rotation of the steel rings to the countershaft 3o, on the other hand the output gear 66 (not shown) in the corresponding transmission ratio between gear 62 and output gear is driven.

To increase the slipping torque, the internal thread

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of the left shaft end 34 of the countershaft 3o screwed adjusting screw 1oo screwed axially to the right. The on The force exerted on the sliding bolt 1o2 is applied to the second transverse bolt 88, the second steel ring 44 and, via the clutch springs 5o, to the first steel ring 46 and thus to the sliding surface Transferred between the first steel ring 46 and the friction lining 56. The dimensioning of the steel rings 44 and 46 as well as the Clutch springs 5o is made so that even when compressed Steel rings prevent the clutch springs from running up against the block; there is then, for example, approx. 1 mm of spring travel.

The slip clutch of the clutch gear unit speaks, for example when stopping abruptly after opening a sectional door, then on when the slipping torque is reached " is.

On the other hand, if the drive motor fails, it is possible to quickly and easily remove the clutch gear unit disengage. The one in Fig. 1 with a cam 124 to the right For this purpose, the pointing eccentric shaft 11o is rotated by 180 °, for example by manual actuation via a cable pull. Through this a leftward axial force is transmitted to the first transverse bolt 86 via the pressure bolt 1o8, so that the first steel ring 46 is lifted or lifted from the friction lining 56. Between the two steel rings 44 and 46 is a

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such play is provided that even with maximum lifting of the steel ring from the friction lining, the distance between the steel rings is about 1 mm.

In the embodiment of the clutch gear unit according to FIG. 1, the setting of the slipping torque is corresponding from the left side possible, while the disengagement of the clutch from the right side via the eccentric shaft 11o is carried out.

The one exerted by rotating the eccentric shaft 11o by 18o ° The force to release the clutch can optionally also be provided by a lever arm connected to an electromagnet be effected. The combined slip and release clutch is particularly suitable for speeds of the shaft that supports it suitable from 6o to 3oo rpm. The setting of the slipping torque is adapted to the invention occurring shock loads are possible in a relatively large load range.

Fig. 2 shows a second embodiment of the invention Clutch gear unit. In this embodiment, both the setting of the slipping torque and the The release clutch can be released from one side, on the right-hand side in FIG. 2. The arrangement shown in section

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The lower half of the clutch gear unit shows the clutch gear unit in the coupled state and in the upper half in the disengaged state.

The clutch transmission unit of FIG. 2 is essentially one Rectangular housing block 13o installed. This housing block 13o can preferably be made from a light die-cast be made and be accessible from at least one narrow side for easier assembly. In the housing block 13o is in Section of an interior space that is rectangular in shape to accommodate a countershaft 138 and the elements arranged thereon. The interior space 132 goes in the respective side area into two stepped rotationally symmetrical side bores 134 and 136, respectively. Similar to the example of FIG a countershaft 138 designed as a hollow shaft is mounted in the side bores 134 and 136 by means of roller bearings 14o and 142. The roller bearings 14o and 142 are supported on the inner circumferential wall of the side bores 134 and 136, respectively. A graduated trained bearing cover 144 holds the outer shell of the roller bearing 14o axially, with the retaining extension of the bearing cover a seal 146 is provided adjacent to the outer shell. In an inner bore 148 of the bearing cover 144, the one has a larger diameter than the outer diameter of the countershaft 138, a radial sealing ring 15o is provided.

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In the direction of the interior, the left roller bearing 14o is through a on the countershaft 138 mounted spacer ring 152 set. This then follows in the axial direction to the right a gear 154 formed in one piece on the countershaft 138 in this exemplary embodiment. Via the gear 154, for example one arranged parallel to the countershaft 138 Output shaft (not shown) are driven.

However, it is also possible to use a stub shaft 156 directly in the inner bore of the countershaft, which is open to the left 138 to be attached, with a keyway connection between the countershaft and the output shaft for torque transmission is. Here either the output power can be decreased or this point can be used to introduce the torque for manual operation.

Adjacent to the gear 154, a disk 16o is arranged on the countershaft to support a worm gear 158. The worm wheel 158 is shell-shaped with a countersunk inner bore 162 that is open to the right. The floor 164 the countersunk bore 162 is supported to the left on the disk 16o. On the right side of the bottom 164 is a friction lining 166 attached in a known manner by riveting or gluing. The worm wheel 158 has approximately the shape in section of a lying U, with the perpendicular transverse leg

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of the U represents the bottom 164. The toothing extends only about half of the longitudinal legs. Perpendicular to the axis the countershaft 138 is a worm shaft (not shown) which is arranged in the upper region of the housing block and meshes with the tooth segments of the worm gear 158.

In the exemplary embodiment in FIG. 2, the inner bore 162 of the worm wheel completely accommodates two steel rings 169 and 17o, which, like the steel rings 44 and 46, have recesses for springs arranged in between. In this embodiment only the second steel ring 17o further removed from the friction lining 166 has a transverse bore and a transverse bolt 167. Of the Cross bolt 167 is axially displaceable in an elongated hole 171 of the countershaft 138.

The right shaft end 172 of the countershaft 138 ends in the right side bore 136 of the housing block 13o at a distance to the outer surface of the housing block. The shaft end 172 has approximately the same outer diameter as the left shaft end and is also supported by a roller bearing 142 in the side bore 136 in the housing block. The inner bearing shell 174 of the Right roller bearing 142 lies against the end face of the second steel ring via an intermediate ring 176 or a Seeger ring 17o at. This end face ends approximately in a plane with the right end face of the worm wheel 158.

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An eccentric housing 178 with an approximately U-shaped section is attached to the right-hand side of the housing block 13o. This eccentric housing 178 is attached to the housing block by means of countersunk Allen screws screwed tight. On the inner end face of the eccentric housing 178, a is pointing toward the interior of the housing block 13o circumferential extension 182 is provided. The extension 182, which has the same outer diameter as the side bore 136 and is inserted into this is sealed by an externally sealing gasket 184. The extension 182 lays the outer shell of the right roller bearing 142 axially fixed, so that forces directed axially to the right can be absorbed thereby. In the eccentric housing 178 an eccentric shaft 186 running perpendicular to the axis of the countershaft 138 is arranged. The eccentric shaft 186 engages with one to the right with a cylindrical one Recess and to the left outside with an axially protruding extension formed pressure plate 188. The through the Eccentric shaft 186 axially displaceable pressure plate 188 stands over an axial ball bearing 19o with an axially displaceable one Steel sleeve 192 in connection. The outer peripheral wall of the steel sleeve 192 is slidable in the inner bore of the right end of the shaft the countershaft 138 installed. In the steel sleeve, which is provided with a self-locking internal thread 194, there is a Screwed pressure bolt 196, the left end with a cylindrical The recess is in engagement with the transverse bolt of the steel ring 17o facing away from the friction lining 166.

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To close the left inner bore of the countershaft 138 from the inside of the housing block 13o, from the right in a radially larger inner bore of the countershaft 138 in the area of the friction lining 166, an end plate 198 with an O-ring seal 199 used. This end plate 198, which can also be designed from two disks, is provided with a Seeger ring 2oo secured to the right.

For more convenient adjustability of the slipping torque, the eccentric housing 178 can extend the axis of the countershaft 138 is provided with a suitable hole or opening for the passage of an Allen key or screwdriver be (not shown). The eccentric shaft is then likewise in the radial direction from the low point of the eccentric to the high point of the eccentric provided with a cross hole. The pressure plate 188 then also has a bore of approximately the same diameter. Of the Push bolt 196 is formed at the right end with an Allen or screwdriver engagement area. In this case it is the opening of the eccentric housing is provided with a seal so that the slipping and disengaging clutch running in the oil bath can be exposed to the outside to seal. The rotation of the pressure bolt 196 can only take place in 18 ° steps because of the cylindrical recess.

To adjust the slipping torque, for example, an Allen key can be inserted through the opening in the eccentric housing

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The transverse bore of the eccentric shaft and the bore of the pressure plate are guided to the pressure pin 196 and this can be shifted to the left in relation to the steel bushing 192. Because of this shift
the second steel ring 17o is shifted to the left, so that the spring force on the first steel ring 169 adjacent to the friction lining and thus the slipping torque increases.

When the low point of the eccentric is in contact with the pressure plate 188, the springs 2o2 can move the second steel ring 17o to the right and come into a state relieved of pressure. In this way, there is no longer any pressure force directed to the left acting on the first steel ring 169, so that the clutch is released. The high point of the eccentric is brought against the pressure plate 188 for coupling. The second steel ring 17o, which is shifted to the left as a result, then builds a pressing force acting to the left via the springs 2o2
of the first steel ring 169 against the friction lining 166.

In the case of the exemplary embodiments shown, the clutch gear unit has an approximately cuboid external shape, with the eccentric housing protruding on one of the two largest boundary surfaces. Inside this cuboid is also the
Drive motor housed. A box for making the electrical connections is attached to the cuboid shape. In addition, the cuboid housing can also have a limit switch.

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take whose moving part is driven by one of the gear shafts.

An extension of the eccentric shaft protrudes from the eccentric housing and can be operated, for example, by a crank. An extension piece between the crank and the actual eccentric shaft be provided. Actuation by means of a chain or gear transmission is also possible in order to achieve the To operate the release clutch from a location remote from the attachment location of the clutch gear unit can. You can also attach a radially projecting flat iron to the eccentric shaft or its extension, for example can be operated by a chain hoist. A securing element which the eccentric shaft is assigned to in the engaged state Holds position is either only for the installation of the clutch gear unit at the installation site or also for the following Operation planned. In the latter case, the securing element would have to be released each time before the release clutch can be operated.

The clutch transmission unit according to the invention can, for example at 28 rpm of the output shaft can be designed for torques in the range from 8 to 15 mkp. With the smaller one mentioned Torque value, the housing can be designed with the dimensions 235 mm length, 85 mm width and 14o mm height, whereby the distance

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between the axis of the output shaft and the two closest, parallel to the boundary walls of the housing about 63 iron and 77 is now.

The output side of the output shaft is on the same flat side of the housing as the eccentric housing and / or on the this flat side opposite flat side of the housing is provided.

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Claims (20)

L 932 M + a (Dr.SchN / hm / ez) October 27, 1978 A η s ρ r ü c he Clutch gear unit,
_r characterized in that a combined sliding and disengaging clutch is provided, which completely or partially in a torque-transmitting gear (54; 158) is arranged of the transmission. 2. clutch transmission unit, in particular according to claim 1, characterized in that a pair or more pairs of Surfaces (47, 56; 161, 166) from which the torque is transmitted when the clutch is engaged, too are provided as slip surfaces of the slip clutch. 3. clutch transmission unit according to one of the preceding claims with a housing, characterized in that the clutch can be actuated from outside the housing (2; 130). 4. clutch transmission unit according to one of the preceding claims, characterized in that for axial displacement a first coupling part (46; 170), which together with a second coupling part (56; 166) coupling surfaces . 030018/0519 ORIGINAL INSPECTED sets, when engaging and disengaging the clutch in a shaft (30; 138) on which the torque-transmitting wheel (54; 158) is arranged, axially displaceable bolt (108; 196) is provided. 5. clutch transmission unit according to claim 4, characterized in that that a radially inwardly projecting transverse bolt (86; 169) is attached to the first coupling part (46; 170) which the bolt acts. 6. clutch transmission unit according to one of the preceding claims, characterized in that for engagement or an eccentric (110; 186) is provided for disengaging the clutch, which is preferably indirectly or directly on ' the bolt (108; 196) acts. 7. clutch transmission unit according to one of the preceding Claims, characterized in that the effective length of the engagement mechanism for adjusting the release clutch or the release mechanism is adjustable inside the clutch gear unit, preferably by adjustability the effective length of the bolt (108; 196). 8. clutch transmission unit according to claim 6 or 7, characterized in that between the eccentric (110; 186) and the Bolt (108; 196) a pressure plate (188), a thrust bearing (190) and a bushing (192) into which the bolt is screwed, are provided, and that relative to adjusting rotation of the bolt 030018/0519 an opening (204) in the eccentric to the bushing, if necessary is provided in an eccentric housing, in the pressure plate and in the axial bearing. 9, clutch transmission unit according to one of the preceding Claims, characterized in that the torque-transmitting wheel (54; 158) is rotatable on an associated shaft (30; 138) is arranged and, preferably on a friction lining (56; 166) / has a first clutch surface; that the combined Rutschund Disengaging clutch, a first ring (46; 46; 169), the face of which interacts with the first coupling surface second coupling surface (47; 161) and on the side facing away from the second coupling surface one second ring (44; 170), wherein at least one spring (50; 202) is arranged between the first and the second ring is. 10, clutch transmission unit according to claim 9, characterized in that that the second ring (44; 170) for axial displacement of the first ring (46; 169) when engaging and disengaging the clutch is axially displaceable relative to the shaft (30; 138). 11, clutch transmission unit according to one of the preceding Claims with a housing, characterized in that the slipping torque of the slipping clutch comes from outside the Housing (2; 130) is adjustable. 030018 / OB19 12. clutch transmission unit according to claim 11, characterized in that that the second ring (44; 170) is axially adjustable to adjust the slipping torque of the slipping clutch. 13. clutch transmission unit according to claim 12, characterized in that for setting the second ring (44)
a screw (100) screwed into the shaft (30) is provided which is fastened to a second ring (44),
inwardly protruding (Jierbolzen (88) acts. 14. clutch transmission unit according to claim 13, characterized in that that the screw (100) lies axially on the side of the bolt (102) facing away from the second ring (44). 15. Clutch transmission unit according to one of the preceding Claims, characterized in that the slip and disengagement clutch on a shaft (30; 138), which with a lower Speed as the input shaft of the clutch gear unit rotates, is, with clutch gear units with more as a speed reduction stage, preferably on a medium speed shaft. 16. Clutch transmission unit according to one of the preceding claims, characterized in that the combined slip and The clutch is running in the oil bath. 030018/0519 _ η " 17. Use of the clutch gear unit according to one of the Gates, in particular claims 1 to 16 in the drive of / sliding, sectional, lifting, Roll and counterweight tilting doors. 18. Use of the clutch transmission unit according to one of claims 1 to 16 in the drive of power-operated doors or windows. 19. Use of the clutch transmission unit according to one of claims 1 to 16 in the drive of roller shutters, blinds or rolling grilles. 20. Use of the clutch transmission unit according to one of the Claims 1 to 16 in the control of valves and / or valve slides in fluid devices. 030018/0519