DE202015007761U1 - Coupling arrangement with sensor and securing means - Google Patents

Abstract

Coupling arrangement comprising a drive part (6) which can be driven in rotation about a rotation axis (X), a driven part (7) rotatable relative to the first drive part (6), a clutch (2) arranged in the power path between the drive part (6) and the driven part (7) ) with a first coupling part (18) which is rotatably connected to the drive part (6) and axially movable, and a second coupling part (19) which is fixedly connected to the output part (7), a controllable actuator (3) with a axially movable piston (28) for axial loading of the first coupling part (18) relative to the second coupling part (19) in a closed position, return means (26), which act on the first coupling part (18) relative to the second coupling part (19) in an open position, and a sensor (42) for detecting a signal representing the axial position of the piston (28), characterized in that securing means (39) are provided which allow relative axial movement of the piston Prevent the piston (28) away from the first coupling part (18).

Description

The present invention relates to a clutch assembly, comprising a rotatable about a rotational axis drivable drive part, a rotatable relative to the first drive part output part, arranged in the power path between the drive part and the driven part coupling with a first coupling part, which is rotatably connected to the drive member and axially movable , and a second coupling part which is fixedly connected to the driven part, a controllable actuator with an axially movable piston for axially urging the first coupling part relative to the second coupling part in a closed position, return means which act on the first coupling part relative to the second coupling part in an open position , and a sensor for detecting a signal representing the axial position of the piston.

From the DE 10 2013 111 891 A1 a drive arrangement with a clutch is known, which has a sensor for detecting switching positions of the clutch. For this purpose, a donor element in the form of an annular disc is fixed radially on the outside of a first coupling part, which moves on actuation of the coupling together with the first coupling part. Between a housing of the clutch and the annular disc sits a return spring with a bias and acts on the washer against a thrust washer of the first coupling part in an open position. Radially outside the actuator, the sensor is arranged in the form of a Hall sensor, which detects the distance to the annular disc without contact.

The present invention has for its object to provide a clutch assembly, in particular for use in the drive train of a motor vehicle, which is compact and robust and allows reliable detection of the switching state of the clutch.

This object is achieved in a coupling arrangement of the type mentioned above in that securing means are provided which prevent relative axial movement of the piston away from the first coupling part.

The invention is therefore based on the idea to determine the switching state of the coupling via the axial position of the piston. For this purpose, the invention proposes to secure the piston relative to the first coupling part in order to be able to reliably conclude a conclusion on the switching state of the coupling on the basis of the detected axial position of the piston.

Specifically, the securing means prevents relative axial movement of the piston away from the first coupling part. In other words, the piston is coupled with respect to a movement away from the first coupling part in the direction of the actuator to the first coupling part. During operation of the clutch arrangement, the piston can be moved axially back and forth depending on the activation of the actuator. When the piston is moved in the direction of the second coupling part, the first coupling part is acted upon relative to the second coupling part in the closed position. In the closed position, the clutch is closed, that is, the first coupling part is connected for torque transmission to the second coupling part. When the piston is moved in the opposite direction away from the second coupling part, the first coupling part is acted upon in the open position relative to the second coupling part. In the open position, the clutch is opened, that is, the first coupling part is separated from the second coupling part, whereby the torque transmission is interrupted, respectively, the free torque compensation is possible. The securing means ensure that the piston can only be moved away from the second coupling part together with the first coupling part. In this way, the switching state of the clutch based on the axial position of the piston can be determined safely. In addition, the clutch assembly is compact and robust, because it can be dispensed with additional components, such as a donor element in the form of an annular disk.

The coupling is preferably designed as a positive coupling, in particular in the form of a toothed coupling or a dog clutch. It is understood that other forms of coupling are conceivable that can produce or interrupt a torque transmission, for example, a non-positive coupling such as a Reiblamellenkupplung. For example, the clutch assembly may be configured as a shiftable clutch or a hang-on clutch to transfer torque as needed from a longitudinal drive shaft of the motor vehicle to the side shafts of a rear wheel axle. Likewise, the clutch assembly, for example, connect an electric drive associated with the rear axle with the side shafts to be used in conjunction with an electric drive axle for hybrid systems. Furthermore, the clutch assembly be an electronically controlled switchable limited slip differential, which is actuated by an electronic control unit. In principle, when the clutch is engaged, the first and the second clutch part are non-rotatably connected to the clutch housing. In contrast, the free torque compensation is possible with an open clutch.

The first coupling part can according to the technical teaching of DE 10 2013 111 891 A1 arranged outside a housing Have ring portion, on which circumferentially distributed cam elements are formed. These extend axially through housing openings into the interior of the housing, so that the first coupling part rotates together with the rotationally driven housing. In this context, the technical teaching of the DE 10 2013 111 891 A1 Referenced. Likewise, the first coupling part may be arranged within the housing, as for example in the DE 10 2009 056 088 A1 is described in their technical teaching in this context also expressly incorporated. Accordingly, the rotationally fixed with the drive member and axially movable first coupling part on a second coupling part facing end face for torque transmission with the second coupling part have positive locking means in the form of a toothed ring. On a side remote from the toothed ring end face of the first coupling part are distributed circumferentially axially projecting cam elements formed, which extend through housing openings of the housing to the outside. In both aforementioned embodiments, the actuator cooperates with the first coupling part by means of the axially movable piston, so that when the actuator is actuated the first coupling part is acted upon by the piston relative to the second coupling part in the closed position.

Conveniently, the securing means are arranged such that the first coupling part axially overlaps the securing means. This provides a particularly compact design. In particular, the piston extends into the first coupling part. Preferably, the securing means interact directly or indirectly with the piston and directly or indirectly with the first coupling part to ensure an axial support of the piston on the first coupling part in the direction of the actuator, respectively away from the second coupling part.

In particular, the securing means may be arranged on the piston. In this way, the piston can be used according to its basic definition for applying the first coupling part relative to the second coupling part in the closed position and serve as a holder for the securing means on the one hand. As a result, a compact and easy to produce clutch assembly is provided. Alternatively or additionally, the securing means may be arranged, for example, on the first coupling part.

Furthermore, the securing means may comprise a securing ring. This can, for example, engage in a circumferential groove formed on the piston. About the locking ring, the piston can be axially supported on the first coupling part to prevent relative movement of the piston away from the first coupling part. The design of the securing means as a retaining ring provides a robust and easy-to-manufacture fuse. Alternatively or in addition to the securing ring, the securing means may comprise, for example, a securing pin passing through the piston, a nut screwed onto an end portion of the piston, or a securing pin arranged on the first coupling part or on the pressure disk, for example supported on a shoulder of the piston without being limited thereto to be.

Furthermore, a pressure disk with a central opening can be provided on the first coupling part, through which an end portion of the piston extends into the first coupling part. In particular, the piston can have an annular axial shoulder facing the pressure disk, the pressure disk being arranged axially between the securing means and the axial shoulder. Thus, the piston may have a stepped basic shape in longitudinal section, so that it can press with its axial shoulder against the pressure plate in order to act on the first coupling part relative to the second coupling part in the closed position. In particular, starting from the axial shoulder, the end portion of the piston, which is elongated in comparison to conventional pistons, extends into the first coupling part. The end portion is in particular annular. The securing means are expediently arranged on the end section of the piston located inside the first coupling part, so that the pressure plate is arranged axially between the securing means and the axial shoulder. In this way, the securing means can be axially supported on a facing away from the actuator, respectively, the second coupling part facing end side of the pressure plate to prevent relative movement of the piston away from the coupling parts.

Preferably, an axial gap is formed at least in the closed position when the actuator is actuated between the securing means and the thrust washer. In this way, a frictional contact between the rotating pressure plate and the rotatably held piston is prevented at least when properly opening the clutch. Conveniently, the axial gap is to be dimensioned such that it is smaller than an axial distance between the first coupling part and the second coupling part in its open position. Only in the event that the securing means must prevent the relative axial movement of the piston away from the first coupling part, the axial gap is bridged, so that then the securing means are supported axially on the thrust washer. Usually, the properly clutch will open as soon as the piston, the first coupling part is no longer against the restoring force of the return means in the closed position is applied. In other words, with proper functioning of the clutch, the first clutch part and the piston will always move together back into the open position, without it would require the assistance of the securing means. Only in the event that the clutch is not functioning properly because, for example, the return means are defective or the axially movable first coupling part jammed, prevent the securing means a backward movement of the piston away from the first coupling part. Thus, the securing means are only a fuse that only comes into play when the first coupling part does not open, although the piston is no longer applied to the closed position. However, according to the invention, during normal operation of the clutch, it may also occur that the piston moves slightly axially with respect to the first coupling part, that is to say that there is play between the piston and the first coupling part, and this maximum within the width of the axial gap.

According to one aspect of the present invention, it is provided that the outer diameter of the thrust washer is smaller than the outer diameter of the actuator. This provides a particularly compact design. Because the sensor detects a signal representing the axial position of the piston and does not measure the distance to an annular disk, as in the case of a Hall sensor, for example, it has been shown that the pressure disk can be made smaller.

Furthermore, the sensor may be arranged on an end face of the actuator facing the first coupling part. In other words, the sensor is not arranged radially outside of the actuator, but in a radially overlapping with the actuator area on the actuator.

Furthermore, the actuator may have an electromagnet with an annular magnet housing, in which the piston is guided in an axially movable manner, wherein the piston acts on the first coupling part in the closed position when the electromagnet is energized. In this embodiment of the actuator, which may also be referred to as a solenoid, the piston is guided in the magnet housing parallel to the axis of rotation, respectively axially movable. In this case, the particular freely oscillating piston engages with a longitudinal region remote from the first coupling part into a coil of the electromagnet enclosed by the magnet housing. When the electromagnet is energized with a switching voltage, the piston is acted upon in the closed position, wherein the piston is disengaged and presses the first coupling part in the closed position. In order then to continue to hold the closed clutch in the closed position, the electromagnet can be energized with a lower compared to the switching voltage holding voltage which acts on the piston against the restoring force of the return means in the direction of the closed position. As soon as the actuator is no longer energized or de-energized, the clutch opens due to the restoring force of the return means, wherein the piston is engaged by the first coupling part back into the annular magnet housing. In this case, the securing means ensure that the piston, which is now freely movable due to the de-energized electromagnet, only engages into the magnet housing when the coupling is actually opened or in the open position. For example, transverse forces acting in the direction of the electromagnet during a car drive, which would pull the floating in the de-energized state of the electromagnet piston in the magnet housing, although the clutch jams and does not open. Then, the securing means prevent relative axial movement of the piston away from the first coupling part. As a result, a robust clutch arrangement is provided which reliably detects the switching state of the clutch.

Preferably, the piston comprises an anchor element, which consists in particular of a ferromagnetic material. Furthermore, the piston may have a sleeve firmly connected to the anchor element, which consists in particular of a paramagnetic material. An electromagnetic actuator offers advantages in terms of installation space. It is understood, however, that instead of an electromagnet and an electric motor, hydraulic or pneumatic actuator can be used.

In particular, the sensor may be designed for measuring the inductance. This provides a reliable and wear-free measuring method for detecting the axial position of the piston axially movable in the spool. For example, the sensor has its own sensor coil. Due to the axial movement of the piston, the inductance of the sensor coil may change. This effect can be advantageously reinforced by ferromagnetic anchoring element, which may be magnetized by the movement within the coil of the electromagnet. Likewise, the inductance change of the coil of the electromagnet can be measured. When the piston is engaged in the magnet housing, or the immersion depth of the ferromagnetic armature element of the piston is maximum, the measured inductance is maximum. In contrast, the measured inductance is minimal when the piston is disengaged, respectively, the immersion depth of the anchor element is minimal, and the first coupling part is in the closed position.

Basically, by detecting a signal representing the axial position of the piston, the switching state of the clutch can be accurately and reliably detected. This in turn allows accurate and rapid control of the clutch assembly and thus a reliable and rapid control of the drive torque to the clutch assembly associated drive axle of the motor vehicle. In addition or as an alternative to a sensor measuring the inductance, it is also possible to use other sensors which operate, for example, according to a mechanical, optical or magnetic operating principle, in order to determine the axial position of the piston. In particular, the at least one sensor is a non-contact sensor, wherein basically at least one touching sensor is conceivable and possible to detect the axial position of the piston.

Advantageously, the sensor is connected to the magnet housing of the electromagnet. In particular, the sensor is integrated in the magnet housing. By this arrangement, a compact arrangement is provided, which also has short cable paths, since the sensor can be arranged spatially directly adjacent to the cable terminals of the coil of the electromagnet.

According to another aspect of the present invention, the piston may be axially supported against the thrust washer via a sliding washer seated on the piston. Thus, a sliding disk can be arranged between the pressure disk and the actuator. As a result, the wear of the piston is minimized when operating the clutch. The sliding disk may be made of a friction-reducing material, such as bronze, in particular sintered bronze, so that the wear due to relative rotational movement between the piston, in particular the anchor member, and the sliding disk is reduced. For example, the sliding disk may be cup-shaped on the side facing the first coupling part. As a result, the sliding disk can be supported axially in the amount of the coupling toothing on the first coupling part in order to minimize the lever action between the piston engaging radially further inside the sliding disk and the first coupling part. Furthermore, the sliding disk can also be formed pot-shaped on the side facing the actuator. Thus, the sliding disk can be either cupped on one side or on both sides. Alternatively, the sliding disk may be formed as an annular disc or sleeve. Furthermore, the sliding disk can either be structurally separated on the end face of the pressure disk facing the actuator or seated in an annular recess in the end face of the pressure disk.

In particular, an outer diameter of the sliding disk can overlap radially with a coupling toothing of the first coupling part. As a result, the leverage on the sliding disk, which results from the radially further inside engaging piston and the radially outer coupling teeth of the first coupling part, minimized. In addition, the axial support of the sliding disk is improved on the pressure plate.

According to a first embodiment of the present invention, the thrust washer and the first coupling part can be manufactured as one component. Thereby, a connection between the first coupling part and the pressure plate can be made particularly robust. The first coupling part with the integrally formed pressure plate can be arranged outside the housing, wherein the first coupling part engages with an end face remote from the pressure plate through housing openings into the interior of the housing, in order to cooperate with the second coupling part in the closed position.

In this case, it can be provided, in particular, that the actuator, the sliding disk, the first coupling part with the integrally formed pressure disk and the securing means form a preassembled assembly. In this way, the clutch assembly is advantageously easy to maintain and easy to assemble or disassemble. Thus, for example, the first coupling part with the integrally formed pressure disk, the axially on the pressure disk supporting sliding disk and the actuator with extending into the first coupling part extending piston, at its end located within the first coupling part, the securing means are arranged, detached from the other Components of the coupling assembly captive pre-assembled and / or assembled or disassembled. Furthermore, the return means may be part of the preassembled module.

According to a second embodiment of the present invention, the pressure plate can be made as a separate component which is detachably connected to the first coupling part. In this way, the first coupling part can be arranged within the housing, wherein an end face of the first coupling part facing the second coupling part interacts with the second coupling part and axial projections, respectively cams, on the actuator facing end side of the first coupling part pass through housing openings to the outside where the pressure plate can be attached as a separate component. The thrust washer can be fastened in a simple manner to the portion of the first coupling part lying outside the housing, in particular by a clip connection. Other solvable Connections are also conceivable and possible, such as a screw connection.

Also in this embodiment, the actuator, the sliding disk, the pressure plate and the securing means can be a preassembled module. In this way, the clutch assembly is advantageously easy to maintain and easy to assemble or disassemble. Thus, for example, the thrust washer, the axially mounted on the thrust washer sliding disk and the actuator with the extending through the sliding disk and the thrust washer piston, at its end of the actuator view behind the thrust washer the securing means are arranged, detached from the other components the clutch assembly pre-assembled and / or assembled or disassembled. Furthermore, the return means may be part of the preassembled module.

Preferred embodiments of the invention are illustrated in the drawings and described below. Hereby shows:

1 a coupling arrangement according to the invention in a first embodiment in the semi-longitudinal section in the open position of the clutch;

2 an enlarged partial view of the clutch assembly 1 ;

3 the clutch assembly 1 in the closed position of the clutch;

4 a coupling arrangement according to the invention in a second embodiment in the semi-longitudinal section in the open position of the coupling;

5 an enlarged partial view of the clutch assembly 4 ; and

6 the clutch assembly 4 in the closed position of the clutch.

The 1 to 3 , which will be described together below, show a clutch assembly 1 according to a first embodiment of the present invention.

The coupling arrangement 1 includes a clutch 2 , an actuator 3 for actuating the clutch 2 and a sensor unit 4 , The coupling 2 Optionally, torque can be applied to a transmission unit connected downstream in the power path 5 transfer. The gear unit 5 is designed in the form of a differential gear, without being limited thereto. The coupling arrangement 1 and the gear unit 5 , which together can also be referred to as a drive arrangement, serve for use in the drive train of a motor vehicle. Specifically, by the drive arrangement an introduced torque can be distributed to the two side shafts of the motor vehicle, wherein a torque transmission between a drive source of the motor vehicle and the side shafts by means of the clutch 2 Optionally manufactured or interrupted as needed. In the 1 is the clutch 2 shown closed for torque transmission, that is in the closed position. In contrast, the clutch 2 in the 3 shown open, that is in the open position in which no torque is transmitted.

Specifically, the clutch 2 in the power path between a drive part 6 and a stripping section 7 arranged. The drive part 6 is designed in the form of a rotationally driven about a rotational axis X housing in which the clutch 2 is included. In this respect, the drive part 6 Also referred to as a clutch housing. The coupling housing 6 is with a drive wheel 8th firmly connected, in particular by welding, with other types of connections such as screw are conceivable. About the drive wheel 8th can torque from a drive motor, not shown here in the drive assembly for driving the gear unit 5 be initiated. The coupling housing 6 is by means of storage 9 rotatably mounted about the axis of rotation X in a stationary housing, not shown.

In the clutch housing 6 is the gear unit 5 added. The relative to the clutch housing 6 rotatable output part 7 is in the form of a differential carrier of the gear unit 5 designed. The differential carrier 7 has a substantially cylindrical outer surface 10 on, by means of the differential carrier 7 opposite a corresponding inner cylindrical surface portion 11 of the coupling housing 6 is rotatably mounted to slide about the rotation axis X.

In the differential carrier 7 are two radial to the axis of rotation X extending holes 12 provided in which a pin 13 plugged in and fixed. On the cone 13 are two differential wheels 14 rotatably mounted about a pin axis Y. The two differential wheels 14 are with a first and a second Seitenwellenrad 15 . 16 in toothing engagement, which are arranged coaxially to the axis of rotation X. The two side shaft wheels 15 . 16 each have a spline 17 , in which a corresponding counter-toothing of a side shaft not shown for torque transmission can be inserted.

The coupling 2 is present in the form of a positive coupling, in particular a toothed coupling designed. It goes without saying, that other forms of clutches can be used, such as a friction clutch. The positive coupling 2 comprises a first coupling part 18 that with the clutch housing 6 rotatably and axially movably connected. Furthermore, the clutch 2 a second coupling part 19 on that with the differential carrier 7 is firmly connected. For transmitting a torque, the first coupling part 18 axially in the second coupling part 19 be engaged so that in a closed position of the clutch 2 a positive connection between the two coupling parts 18 . 19 is made. By disengaging the first coupling part 18 in an open position, the torque transmission is interrupted again.

The second coupling part 19 has as a form-fitting means a toothed ring, which at one end face of the differential carrier 7 is integrally formed. Accordingly, the first coupling part 18 a gegengleichen toothed ring, within the clutch housing 6 is arranged. Next has the first coupling part 18 several axial extensions distributed over the circumference 20 through corresponding housing openings 21 of the coupling housing 6 outward in the direction of the actuator 3 pass.

Outside the coupling housing 6 is a pressure washer 22 on the first coupling part 18 releasably secured, releasable on the lugs 20 is clipped. The pressure disc 22 extends substantially radially to the axis of rotation X. Radially inside, the pressure plate 22 a plurality of distributed over the circumference and extending in the axial direction resilient locking elements 23 on, with their ends in one or more corresponding undercuts 24 the approaches 20 of the first coupling part 18 interlock positively. The pressure disc 22 has at its radially outer end a cylindrical shell portion 25 whose outer diameter is radially inside the actuator 3 remains. Thus, the outer diameter of the thrust washer 22 smaller than the outer diameter of the actuator 3 , Between the clutch housing 6 and the jacket section 25 the pressure disk 22 are return means in the form of a return spring 26 arranged. The return spring 26 is presently designed in the form of a plate spring, it being understood that other forms of springs, such as coil springs, can be used. The return spring 26 acts on the first coupling part 18 in the open position, so that the first coupling part 18 in the direction of the actuator 3 can move out.

By appropriate activation of the actuator 3 can the first coupling part 18 relative to the second coupling part 19 be engaged again to a torque from the drive wheel 8th on the gear unit 5 transferred to. This includes the actuator 3 an electromagnet 27 and an axially movable piston 28 , Here is the actuator 3 designed such that during energizing a coil 29 of the electromagnet 27 The piston 28 the first coupling part 18 relative to the second coupling part 19 against the restoring force of the return spring 26 acted upon in the closed position.

Specifically, the electromagnet faces 27 an annular magnet housing 30 on, by means of a support element 31 on a sleeve shoulder of the clutch housing 6 is arranged. The magnet housing 30 has on one of the clutch 2 facing the front a central opening 32 through which the inside of the magnet housing 30 axially movable guided piston 28 axially outward in the direction of the first coupling part 18 protrudes.

The piston 28 includes one inside the coil 29 guided anchor element 33 from a ferromagnetic material, such as a ferrous material. The anchor element 33 encloses a radially inner sleeve 34 of a paramagnetic material, for example of stainless steel, copper or aluminum. In that the anchor element 33 is made of a ferromagnetic material, it is when you press the electromagnet 27 in the direction of the clutch 2 emotional. In the fully disengaged position, the anchor element comes 33 inside the magnet housing 30 against a housing shoulder 35 to the plant, whereby a frictional contact arises. The sleeve 34 is paramagnetic to prevent unwanted magnetic flux leakage to other components.

The sleeve 34 is axially longer than the anchor element 33 , In addition, the sleeve 34 in longitudinal section to form an axial shoulder 36 graduated. When the electromagnet 27 energized and the piston 28 in the direction of the first coupling part 18 is moved, is the axial shoulder 36 with one between the thrust washer 22 and the axial shoulder 36 arranged sliding disk 37 in Appendix. The sliding disk 37 sits on an annular end section 38 the sleeve 34 on, starting from the axial shoulder 36 in the first coupling part 18 extends into it. At one of the first coupling part 18 facing side is the sliding disk 37 also axially on the pressure plate 22 supported. The sliding disk 37 is cup-shaped, with an axially in the direction of the first coupling part 18 extending and circumferentially circumferential collar 44 the sliding disk 37 with the approaches 20 of the first coupling part 18 or with the coupling teeth of the first coupling part 18 radially covered. Thus, the outer diameter of the sliding disk overlaps 37 radially with the coupling teeth of the first coupling part 18 to the piston 28 over the sliding disk 37 against the pressure disc 22 axially support.

At the inside of the first coupling part 18 lying end portion 38 of the piston 28 are securing means in the form of a retaining ring 39 provided in a circumferential groove 40 the sleeve 34 intervenes. The pressure disc 22 is axially between the circlip 39 and the axial shoulder 36 arranged so that the circlip 39 a relative axial movement of the piston 28 from the first coupling part 18 prevented away. This may cause the piston 28 only together with the first coupling part 18 in the direction of the magnet housing 30 move. Thus, the piston 28 only in the magnet housing 30 be engaged when the first coupling part 18 in the in 3 is shown open position. To operate the clutch 2 a friction welding between the circlip 39 and the pressure disc 22 to prevent is between the circlip 39 and the pressure disc 22 an axial gap 41 educated. This will ensure that the piston 28 not engaged in rotation when engaged. In addition, the sliding disk 37 continue to work as a speed coupling. The axial gap 41 is to be dimensioned such that the axial gap 41 is smaller than an axial distance between the first coupling part 18 and the second coupling part 19 in the open position. Advantageously, the axial gap 41 both in the open position and the closed position of the clutch 2 educated.

By the axial movement of the anchor element 33 inside the magnet housing 30 the inductance changes, the sensor unit 4 is designed for measuring the inductance. If the measured inductance is minimal, then the axially movable piston 28 disengaged and the clutch 2 is in the closed position. In contrast, the measured inductance is maximum when the axially movable piston 28 in the coil 29 is indented. By coupling the piston 28 to the axial movement of the first coupling part 18 by means of the retaining ring 39 is the piston 28 always engaged only when the clutch 2 is actually in the open position. By measuring the inductance, the sensor unit detects 4 thus one the axial position of the piston 28 representing signal over the reliable switching state of the clutch 2 can be recognized.

Specifically, the sensor unit 4 a sensor 42 for measuring itself by the movement of the anchor element 33 changing inductance. This is the sensor 42 radially to the central opening 32 of the magnet housing 30 in one of the clutches 2 facing end face of the magnet housing 30 arranged. Thus, the actuator 3 also as a solenoid with integrated sensor 42 be designated. At the first coupling part 18 facing end face of the magnet housing 30 is a not shown in detail circuit board of the sensor unit 4 attached to the sensor 42 is electrically connected. By means of the printed circuit board, the detected signals are converted and to a control unit, not shown, for switching the clutch 2 transfer. The sensor 42 and the circuit board are spatially close to not shown cable connections, which are the electrical power supply of the coil 29 serve to cabling the electrical components 4 . 27 as short as possible.

The actuator 3 with the integrated sensor unit 4 , the pressure washer 22 on the approaches 20 of the first coupling part 18 clipped, and the piston 28 attached circlip 39 form a pre-assembled module here. The module can be retrofitted in the coupling arrangement 1 be integrated by the piston 28 by means of the retaining ring 39 opposite the pressure disc 22 is secured, the pressure plate 22 on the approaches 20 by means of the locking elements 23 snapped on, and the actuator 3 by means of the carrier element 31 on the sleeve shoulder of the clutch housing 6 is attached. Furthermore, also the return spring 26 Part of the preassembled module, before the clipping the thrust washer 22 on the approaches 20 can be deferred.

The 4 to 6 , which will be described together below, show a clutch assembly 1 according to another embodiment of the present invention. This corresponds largely to the embodiments according to the 1 to 3 so that the similarities are referred to the above description. The same or modified components are provided with the same reference numerals, as in the 1 to 3 ,

A special feature of the embodiment according to the 4 to 6 lies in the fact that the first coupling part 18 and the pressure disc 22 form an integral component, that is, manufactured as a component. In a further difference from the previous embodiments, the first coupling part 18 not inside the coupling housing 6 but from the outside of the clutch housing 6 stated. Specifically, the first coupling part 18 between the clutch housing 6 and the actuator 3 arranged. At one of the second coupling part 19 facing end face are cam elements 43 formed by the housing openings 21 inside the clutch housing 6 engage and in the closed position with the opposite claw ring of the second coupling part 19 co.

The actuator 3 with the integrated sensor unit 4 , the first coupling part 18 with the molded pressure disk 22 and the piston 28 attached circlip 39 form a pre-assembled module here. The module can be retrofitted in the coupling arrangement 1 be integrated by the piston 28 by means of the locking ring 39 opposite the first coupling part 18 is secured, the first coupling part 18 through the housing openings 21 is used and the actuator 3 by means of the carrier element 31 on the sleeve shoulder of the clutch housing 6 is attached. Furthermore, the return spring 26 Part of the preassembled assembly, before the insertion of the cam elements 43 in the housing openings 21 on the first coupling part 18 can be deferred.

LIST OF REFERENCE NUMBERS

1

clutch assembly

2

clutch

3

actuator

4

sensor unit

5

gear unit

6

driving part

7

stripping section

8th

drive wheel

9

bearing means

10

outer surface

11

surface section

12

drilling

13

spigot

14

differential gears

15

sideshaft

16

sideshaft

17

spline

18

first coupling part

19

second coupling part

20

approaches

21

housing opening

22

thrust washer

23

locking element

24

undercut

25

shell section

26

Return spring

27

electromagnet

28

piston

29

Kitchen sink

30

magnet housing

31

support element

32

opening

33

anchor member

34

shell

35

housing shoulder

36

axial shoulder

37

sliding disk

38

end

39

circlip

40

circumferential groove

41

gap

42

sensor

43

cam member

44

collar

X

axis of rotation

Y

pin axis

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102013111891 A1 [0002, 0008, 0008]
• DE 102009056088 A1 [0008]

Claims (18)

Coupling arrangement, comprising a driving part which can be driven in rotation about a rotation axis (X) ( 6 ), a relative to the first drive part ( 6 ) rotatable output part ( 7 ), one in the power path between the drive part ( 6 ) and the stripping section ( 7 ) arranged coupling ( 2 ) with a first coupling part ( 18 ), which with the drive part ( 6 ) rotatably and axially movably connected, and a second coupling part ( 19 ), which with the output part ( 7 ), a controllable actuator ( 3 ) with an axially movable piston ( 28 ) for the axial loading of the first coupling part ( 18 ) relative to the second coupling part ( 19 ) in a closed position, return means ( 26 ), which is the first coupling part ( 18 ) relative to the second coupling part ( 19 ) in an open position, and a sensor ( 42 ) for detecting a the axial position of the piston ( 28 ) representing signal, characterized in that securing means ( 39 ) are provided which a relative axial movement of the piston ( 28 ) of the first coupling part ( 18 ) away. Coupling arrangement according to claim 1, characterized in that the piston ( 28 ) in the first coupling part ( 18 ), wherein the securing means ( 39 ) are arranged such that the first coupling part ( 18 ) the securing means ( 39 ) axially overlapped. Coupling arrangement according to claim 1 or 2, characterized in that the securing means ( 39 ) on the piston ( 28 ) are arranged. Coupling arrangement according to Claim 3, characterized in that the securing means comprise a securing ring ( 39 ) located in one of the pistons ( 28 ) formed circumferential groove ( 40 ) intervenes. Coupling arrangement according to one of the preceding claims, characterized in that on the first coupling part ( 18 ) a pressure disk ( 22 ) is provided with a central opening through which an end portion ( 38 ) of the piston ( 28 ) in the first coupling part ( 18 ) extends into it. Coupling arrangement according to claim 5, characterized in that the piston ( 28 ) one of the printed letters ( 22 ) facing annular axial shoulder ( 36 ), wherein the pressure disk ( 22 ) axially between the securing means ( 39 ) and the axial shoulder ( 36 ) is arranged. Coupling arrangement according to claim 5 or 6, characterized in that at least in the closed position when actuated actuator ( 3 ) between the securing means ( 39 ) and the pressure disk ( 22 ) an axial gap ( 41 ) is formed. Coupling arrangement according to one of claims 5 to 7, characterized in that the outer diameter of the pressure plate ( 22 ) smaller than the outer diameter of the actuator ( 3 ). Coupling arrangement according to one of the preceding claims, characterized in that the sensor ( 42 ) on a first coupling part ( 18 ) facing the end face of the actuator ( 3 ) is arranged. Coupling arrangement according to one of the preceding claims, characterized in that the actuator ( 3 ) an electromagnet ( 27 ) with an annular magnet housing ( 30 ), in which the piston ( 28 ) is guided axially movable, wherein the piston ( 28 ) with electromagnet energized ( 27 ) the first coupling part ( 18 ) is acted upon in the closed position. Coupling arrangement according to claim 10, characterized in that the sensor ( 42 ) is designed for measuring the inductance. Coupling arrangement according to 10 or 11, characterized in that the sensor ( 42 ) on the magnet housing ( 30 ) of the electromagnet ( 27 ) is arranged. Coupling arrangement according to one of claims 5 to 12, characterized in that the piston ( 28 ) via one on the piston ( 28 ) sliding disc ( 37 ) against the pressure disc ( 22 ) is axially supported. Coupling arrangement according to claim 13, characterized in that an outer diameter of the sliding disk ( 37 ) radially with a coupling toothing of the first coupling part ( 18 ) covered. Coupling arrangement according to one of claims 5 to 14, characterized in that the thrust washer ( 22 ) and the first coupling part ( 18 ) are manufactured as a component. Coupling arrangement according to claim 15, characterized in that the actuator ( 3 ), the sliding washer ( 37 ), the first coupling part ( 18 ) with the molded pressure disc ( 22 ) and the securing means ( 39 ) form a preassemblable assembly. Coupling arrangement according to one of claims 5 to 14, characterized in that the thrust washer ( 22 ) is manufactured as a separate component, which with the first coupling part ( 18 ) is releasably connected. Coupling arrangement according to claim 17, characterized in that the actuator ( 3 ), the sliding washer ( 37 ), the pressure disc ( 22 ) and the securing means ( 39 ) form a preassemblable assembly.

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