DUAL CLUTCH

Abstract

A dual clutch device having an input side, a first output side, and a second output side, which are arranged rotatably about an axis of rotation, and having a first, radially outer friction clutch for producing frictional engagement between the input side and the first output side and a second, radially inner friction clutch for producing frictional engagement between the input side and the second output side. Each friction clutch has a first friction element, which engages in the input side in a torque-transmitting manner, a second friction element, which engages in the associated output side in a torque-transmitting manner, a control element for providing an axially pressing force on the friction elements, and a leaf spring element, which is spirally wound around the axis of rotation and which is arranged axially between the control element and the friction elements.

Claims

1. A dual clutch device comprising: an input side, a first output side, and a second output side arranged rotational about an axis of rotation; a first, radially outer friction clutch for generating a friction-fitting engagement between the input side and the first output side; a second, radially inner friction clutch for generating a friction-fitting engagement between the input side and the second output side, each of the friction clutches comprising the following: a first friction element, which engages in a torque-proof fashion the input side, and a second friction element engages the corresponding one of the first or second output sides in a torque-proof fashion, a control element for providing an axial compression upon the friction elements, and a leaf spring element arranged axially between the control element and the friction elements.

2. The dual clutch device according to claim 1, wherein the leaf spring element is wound spirally about the axis of rotation.

3. The dual clutch device according to claim 2, wherein an axially extending section of the input side is implemented to engage radially at an outside and in a form-fitting fashion the first friction element of the first friction clutch and radially at an inside and in a form-fitting fashion the first friction element of the second friction clutch.

4. The dual clutch device according to claim 3, wherein the axially extending section is produced in one piece from sheet metal.

5. The dual clutch device according to claim 1, wherein respectively several of the friction elements are provided.

6. The dual clutch device according to claim 1, wherein the dual clutch device is embodied to run in an oil bath.

7. The dual clutch device according to claim 1, further comprising an axial actuating element that acts upon the leaf spring element of one of the friction clutches, with the leaf spring element being embodied to compress the friction elements upon the actuating element when the axial actuating force is missing so that the friction clutch closes.

8. The dual clutch device according to claim 1, further comprising an axial actuating element that acts upon the leaf spring element of one of the friction clutches, with the leaf spring element being embodied to spread the friction elements apart from the actuating element when the axial actuating force is missing so that the friction clutch opens.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The invention is now explained in greater detail with reference to the attached figures. Here it shows in detail:

[0018] FIG. 1 a longitudinal section through a dual clutch device;

[0019] FIGS. 2 and 3 details of the dual clutch device of FIG. 1;

[0020] FIG. 4 variants of the embodiment of the dual clutch device of FIGS. 1 to 3; and

[0021] FIG. 5 a section of a friction clutch of the dual clutch device of the previous figures.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0022] FIG. 1 shows a longitudinal section through a dual clutch device 100. An input side 110 for connecting to a drive engine, a first output side 115 for connecting to a first transmission input shaft 120, and a second output shaft 125 for connecting to a second transmission input shaft 130 are arranged about an axis of rotation 105. The transmission input shafts 120 and 130 are preferably embodied coaxially in reference to the axis of rotation 105.

[0023] A first friction clutch 135 for the production of a friction-fitting engagement between the input side 110 and the first output side 115 and a second friction clutch 140 for generating a friction-fitting engagement between the input side 110 and the second output side 125 are arranged radially offset in reference to each other. In one embodiment, selected as an example, the first friction clutch 135 is opened without actuation (“normally open”) and the second friction clutch 140 is closed without actuation (“normally closed”). In FIG. 1 the first friction clutch 135 is opened because it is not actuated, and the second friction clutch 140 is opened because it is actuated.

[0024] As shown, it is preferred that an axially extending section 142 of the input side 110 is used equally for the torque-proof engagement of the first friction clutch 135 and the second friction clutch 140. This section 142 is combined with a radially extending section in an exemplary fashion; in other embodiments here a one-piece implementation of the two sections may be given as well. The section 142 is preferably implemented to embody torque-proof counter supports both for the friction elements of the outer first friction clutch 135 as well as the inner second friction clutch 140. As illustrated, the friction elements of both friction clutches 135, 140 may engage in a form-fitting fashion and preferably also in a manner axially displaceable in the section 142. For this purpose, the section 142 may carry outer gear teeth engaged by the friction elements of the first friction clutch 135, and an interior gear teeth engaged by the friction elements of the second friction clutch 140. In another embodiment the section 142 comprises a strip of circumferential material with constant thickness about the axis of rotation 105, which is formed such that alternating it extends at two different radii about the axis of rotation so that exterior gear teeth and interior gear teeth develop.

[0025] A first actuating device 145 and a first leaf spring element 150 are allocated to the first friction clutch 135, a second actuating device 155 and a second leaf spring element 160 to the second friction clutch 140. The leaf spring elements 150 and 160 act oppositely the actuating devices 145 and 155 in the axial direction. In the embodiment shown the leaf spring elements 150 and 160 each cause the closing of the friction clutches 135 and 140, while any actuation via the activation device 145 and 155 respectively cause an opening of the friction clutches 135 and 140. This constellation is also called “normally closed”; equivalently a “normally open” arrangement is also possible, in which the respective actuating device 145, 155 is used for closing and the respective leaf spring element 150, 160 for opening the allocated friction clutch 135, 140. Further, in the embodiment shown a “sliding” motion of the friction clutches 135, 140 is provided, with an axially acting compression force acting upon the activation devices 145, 155 in order to operate them. In one alternative embodiment a “tensile” activation of the devices 145, 155 may occur as well. The activation of the devices 145, 155 may for example occur via an electric or hydraulic actuator.

[0026] The friction clutches 135 and 140 respectively comprise a plurality of blades 165 and friction disks 170, which are provided alternating as axially arranged stacks. Blades 165 engage in a torque-proof fashion at the input side 110 and the friction disks 170 at the corresponding output sides 115, 125. In other embodiments blades 165 and friction disks 170 can also be inversed or exclusively blades 165 or exclusively friction disks 170 may be used. Preferably another friction coating is provided between axially contacting elements 165, 170.

[0027] FIG. 2 shows in detail the dual clutch device 100 in the proximity of the first friction clutch 135. The output side 115 comprises a radially circumferential section, engaged by the friction disks 170 in a torque-proof fashion, and an optional axially extending section for the torque-proof connection to the first transmission input shaft 120. These two sections are connected to each other in a torque-proof fashion. The first actuating device 145 comprises a control element 205, which is connected to the first output side 115. The embodiment shown represents a one-piece connection to the radial section of the output side 115. The control element 205 extends radially inwardly, with the first leaf spring element 150 being arranged between the control element and one end of the stack of blades 165 and friction disks 170. The leaf spring element 150 extends in a preferred embodiment spirally about the axis of rotation 105 or is angular with regards to the axis of rotation 105, and preferably further exhibits a strong spring-stiffness in order to transfer even a minor axial motion of the control element 205 to the stack of blades 165 and friction disks 170. This way a friction-fitting connection can be generated between the input side 110 and the output side 115 so that torque can be transmitted by the friction clutch 135. The relative rotation of the input side 110 in reference to the first output side 115 subjects the leaf spring element 150 to compression strain. This way, the leaf spring element 150 can get wedged slightly between the control element 205 and the end of the stack of blades 165 and friction disks 170 so that an axial expansion force develops which increases the compression force acting axially upon the blades 165 and the friction disks 170. The closing force upon the friction clutch 135 is in this case increased by a portion of the torque transmitted via the friction clutch 135. The compression force acting upon the blades 165 and the friction disks 170 can therefore be greater by many times than an originally caused compression force of the control element 205, before a friction-fitting engagement occurs between the blades 165 and the friction disks 170. The engagement of the friction clutch 135 can therefore occur with lower force than upon the blades 165 and the friction disks 170 so that for example via manual actuation strong torque can be coupled or decoupled securely via the friction clutch 135.

[0028] FIG. 3 shows a detail of the dual clutch 100 of FIG. 1 in the proximity of the second friction clutch 140. The second friction clutch 140 is opened by an axial actuating force upon the control element 205. The actuating force compresses the second leaf spring element 160 in the axial direction. Just like the first leaf spring element 150 the second leaf spring element 160 preferably comprises an element, angular in reference to the axis of rotation 105 or in a spiral element, which extends about the axis of rotation 105. If the axial actuation force of the control element 250 reduces in FIG. 3 towards the left, the second leaf spring element 160 relaxes and pushes the stack of blades 165 and the friction disks 170 against the counter bearings 210 such that the stack is compressed and the blades 165 come into a friction-fitting engagement with the friction disks 170. This way torque develops between the second output side 125 and the control element 205 so that the second leaf spring element 160 is compressed along its spiral direction of extension. The second leaf spring element 160 inverts the force of distortion so that an additional axial force develops. The stack of blades 165 and the friction disks 170 are therefore pressed more strongly towards the counter bearings 210 so that the friction-fitting engagement strengthens.

[0029] In this variant as well a portion of the force transmitted via the second friction clutch 140 can be used to close the second friction clutch 140. A self-enhancement of the applied actuating force develops upon the control element 205. The second friction clutch 140 can therefore also be closed tightly while applying only minor actuating forces so that even a strong torque can be transmitted between the input side 110 and the output side 125.

[0030] FIG. 4 shows a schematic illustration of a helix 400. A section of the helix 400, which covers preferably less than 360° about an axis of rotation 105, defines the preferred form of a leaf spring element 150 and 160 when it is embodied in a spiral shape. With regards to the preferred direction of transmission of torque by the dual clutch device 100 the direction of rotation of the helix 400 is selected such that the described claim for compression occurs along the direction of extension when the respective friction clutch 135, 140 shall be closed. In other words, by distorting the ends of a leaf spring element 150, 160 in the direction of compression about the axis of rotation 105 here an axial expansion force can be applied upon the ends of the spring leaf element 150, 160.

[0031] A spiral leaf spring element 150, 160 with the shape of the helix 400 shown in FIG. 4 extends in one view upon the axis of rotation 105 clockwise away from the observer. When the end facing the observer is distorted clockwise in reference to the other end about the axis of rotation 105 here an axial expansion force develops upon the ends of the leaf spring element 150, 160 along the axis of rotation, which drives the ends axially apart. In one of the previous figures the distorting motion develops in one of the friction clutches 135, 140 by the leaf spring element 150, 160 being axially compressed to elements with different rotations. By the distorting effect the compression is strengthened so that minor compression and/or actuating force can be sufficient to trigger an opening and/or closing process of the corresponding friction clutch 135, 140. A portion of the torque transmitted via the friction clutch 135, 140 is here used for providing the axial force upon the friction elements 165, 170.

[0032] In another embodiment one of the spiral leaf spring elements 150, 160 comprises several of the elements shown, which are screwed into each other. In a further embodiment one of the leaf spring elements 150, 160 is interrupted at the circumferential side.

LIST OF REFERENCE CHARACTERS

[0033] 100 Dual clutch device [0034] 105 Axis of rotation [0035] 110 Input side [0036] 115 First output side [0037] 120 First transmission input shaft [0038] 125 Second output side [0039] 130 Second transmission input shaft [0040] 135 First friction clutch [0041] 140 Second friction clutch [0042] 145 First actuating device [0043] 150 First leaf spring element [0044] 155 Second actuating element [0045] 160 Second leaf spring element [0046] 165 Blade [0047] 170 Friction disk [0048] 205 Control element [0049] 210 Counter bearing