CN106133361B - Clutch device - Google Patents
Clutch device Download PDFInfo
- Publication number
- CN106133361B CN106133361B CN201580017441.5A CN201580017441A CN106133361B CN 106133361 B CN106133361 B CN 106133361B CN 201580017441 A CN201580017441 A CN 201580017441A CN 106133361 B CN106133361 B CN 106133361B
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- China
- Prior art keywords
- friction
- clutch device
- section
- spring element
- spacing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 125000006850 spacer group Chemical group 0.000 claims abstract description 37
- 230000005540 biological transmission Effects 0.000 claims description 12
- 230000003014 reinforcing effect Effects 0.000 claims description 8
- 238000000926 separation method Methods 0.000 claims description 3
- 230000002787 reinforcement Effects 0.000 claims 5
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 239000000969 carrier Substances 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
- F16D13/69—Arrangements for spreading lamellae in the released state
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/22—Friction clutches with axially-movable clutching members
- F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
- F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
- F16D13/54—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
the invention relates to a clutch device (10; 400) for a motorcycle for selectively torque-locking connecting an input side to an output side, wherein the clutch device is rotatably mounted about a rotational axis and comprises at least one friction plate pack (50) having a friction partner (55, 60) and a further friction partner (55, 60), and a spacer device (240, 300), wherein the spacing device comprises at least one first spring element (245), wherein the first spring element is coupled with a first end (260) with the friction counterpart and with a second end (265) with the further friction counterpart, wherein the spacer device is designed to separate the friction partners from one another in the axial direction in the operating state in which the clutch device is open.
Description
Technical Field
The present invention relates to a clutch device for a motorcycle.
background
Consumers always expect clutch devices to be more comfortable and safer. In addition, in particular in clutch devices for motorcycles, reducing the operating energy of the clutch device is the most important requirement, because the clutch device is usually operated by hand. Many systems are capable of reducing the disengagement force of the clutch device by using driveline energy. For example, the clutch device can be designed as a so-called booster clutch. Such booster clutches consist of a pilot clutch and a main clutch, which are connected together by a ball ramp. The operation of the main clutch is related to the state of the drive train.
Disclosure of Invention
the object of the present invention is to provide a clutch device of improved and inexpensive design.
the clutch device according to the invention solves the stated object. In a preferred embodiment, an advantageous embodiment is described.
According to the invention, it is possible to provide an improved clutch device for a motorcycle for selectively torque-locking the input side to the output side, such that the clutch device can be rotatably mounted about a rotational axis and comprises at least one friction plate pack having a friction partner and a further friction partner, and a spacer device. The spacer device has at least one first spring element. The first spring element is coupled with a first end to a friction partner and with a second end to a further friction partner. The spacer device is designed to separate the friction partners from one another in the axial direction in the operating state in which the clutch device is open. The first spring element comprises a first section and a second section, wherein the first section is arranged adjacent to the first end and the second section is arranged adjacent to the first and second ends. The first section extends substantially in a radial direction and the second section extends at least partially in a circumferential direction, wherein the second section is free of curvature. The spacer device further comprises a spacer element arranged on the friction counterpart, wherein the spacer element extends at least partially in a radial direction, wherein the first spring element rests with the second end on the spacer element.
This configuration has the advantage that: i.e. to reduce the drag torque of the clutch device. In addition, in the case of a clutch device configured as a booster clutch, it is ensured that the booster reliably does not accidentally close the clutch. In this way, a particularly compact spring element can be provided.
Particularly advantageous are: the spacer device comprises a second spring element, wherein the second spring element is connected with a first end to the further friction partner, wherein the second spring element rests with a second end against the second end of the first spring element.
In another embodiment, the spacer element is connected with the friction partner with a fixed end. The spacer element also has a free end, wherein an abutment surface oriented parallel to the friction surface of the friction partner is provided on the free end, wherein the abutment surface is arranged axially offset relative to the friction surface in the direction of the other friction partner. In this way, the spring travel of the first spring element can be shortened.
In another embodiment, the clutch device includes a friction plate carrier. The friction disk carrier is coupled with the input side or the output side in a torque-locking manner. The friction lining carrier has a first flange element and a second flange element arranged axially spaced apart from the first flange element. In the axial direction, between the first and the second flange element, the disk carrier comprises a plurality of teeth elements distributed in the circumferential direction, which connect the first flange element to the second flange element. Between two tooth elements arranged next to one another in the circumferential direction, a recess is provided in the friction lining carrier. The spacing device is at least partially disposed in the groove. In this way, a particularly compact clutch device can be provided.
in addition, it is advantageous: the friction partner has a toothing opening which is formed in correspondence with the toothing element, wherein the first spring element, the toothing opening and the spacer element are arranged alternately in the circumferential direction.
in another embodiment, the output side comprises a hub with a fixed section. The hub part is designed to provide a connection to the transmission input shaft, wherein a reinforcing device is provided between the fastening section and the friction lining carrier, wherein the reinforcing device is designed to add a pressing force for closing the clutch device to the reinforcing force, wherein the reinforcing device preferably comprises at least one spring element, in particular a leaf spring. The clutch device can thereby be operated with a small operating force.
In a further embodiment, a counter plate is provided axially adjacent to the friction counterpart and a separating device is provided axially on the side of the counter plate arranged opposite the friction disk pair, wherein the counter plate has an opening and the friction disk carrier has a separating arm, wherein the separating arm extends in the axial direction and engages in the opening. The clutch device can thereby be particularly compactly constructed.
In addition, it is advantageous: the counter-pressure plate comprises at least one centering element, wherein the centering element extends at least partially in the axial direction and is preferably of a band-shaped configuration. The centering element engages in a centering opening of the fastening section corresponding to the centering element, wherein the centering element is arranged radially inside with respect to the reinforcing device.
Drawings
The present invention is explained in detail below with reference to the drawings. Herein, the same components are designated by the same reference numerals. Here:
Fig. 1 shows a perspective view of a clutch device according to a first embodiment;
FIG. 2 shows a half-section through the clutch device shown in FIG. 1;
FIG. 3 shows a cross-sectional view of the cross-sectional view shown in FIG. 2;
fig. 4 shows a perspective cross-sectional view through the clutch device shown in fig. 1 to 3;
Fig. 5 shows a perspective view of the counter plate of the clutch device shown in fig. 1 to 4;
fig. 6 shows a perspective view of a friction lining carrier of the clutch device shown in fig. 1 to 4;
FIG. 7 shows a perspective view of the hub of the clutch device shown in FIGS. 1 to 4;
Fig. 8 shows a perspective view of a friction element of the clutch device shown in fig. 1 to 4;
Fig. 9 shows a schematic illustration of a spacer device of the clutch device shown in fig. 1 to 4;
Figure 10 shows a perspective half-section through a clutch device according to a second embodiment; and
fig. 11 shows a schematic view of a spacer of a clutch device according to a second embodiment.
Detailed Description
fig. 1 shows a perspective view of a clutch device 10 according to a first embodiment. Fig. 2 shows a half-section through the clutch device 10 shown in fig. 1. Fig. 3 shows a sectional view of the sectional view shown in fig. 2. Fig. 4 shows a perspective sectional view through the clutch device 10 shown in fig. 1 to 3. Fig. 1 to 4 will be explained together below.
The clutch device 10 includes an input side 15 and an output side 20. The input side 15 and the output side 20 are rotatable about a rotation axis 25. The input side 15 has a primary wheel 30 with a toothing 35. Torque M from an internal combustion engine, not shown, is introduced into the clutch device 10 via the primary wheel 30. The primary wheel 30 is arranged directly adjacent to the first friction disk carrier 40 in a torque-locked manner. The first friction lining carrier 40 has an internal toothing 45. A friction plate pack 50 is arranged radially inside with respect to the internal toothing 45. The friction plate pack 50 comprises a first friction partner 55 in the form of a first friction plate and a second friction partner 60 in the form of a second friction plate. The first friction partner 55 has an external toothing 65 which engages in the internal toothing 45 of the first friction lining carrier 40. The first friction partner 55 is thereby connected to the first friction disk carrier 40 in a torque-locking manner. In the axial direction, the disk set 50 is fixed to the first disk carrier 40 by means of a fixing ring 56, which is arranged on the first disk carrier 40 on the upper side of the first disk set 50.
a second friction plate carrier 70 is disposed radially inward of the first friction plate carrier 40. The second disk carrier 70 has an external toothing 75 provided in the region of the disk pack 50. The second friction partner 60 has an internal toothing 80, which engages in the external toothing 75 of the second friction lining carrier 70. The second friction partner 60 is therefore connected with the second friction lining carrier 70 in a torque-locking manner.
In addition, the clutch device 10 includes a spring member 85. The spring element 85 is configured as a leaf spring. In this case, the spring element 85 is connected at a first longitudinal end 90 to a fastening section 91 of the second plate carrier 70, which is arranged radially inward with respect to the outer toothing 75, by means of a first riveted connection 95. The fastening section 91 extends in the radial direction from the outside inward. The fastening section is oriented transversely to the outer toothing 75 of second disk carrier 70. At the first longitudinal end 90, the spring element 85, which is in the form of a spiral at the rest, is flattened, so that the first longitudinal ends 90 have a common plane at the fastening section 91. As a result, a large bearing surface can be provided on the first riveted connection 95 and thus a good torque transmission between the fastening section 91 and the spring element 85.
Further, a hub 100 is provided radially inward of the second friction plate carrier 70. Here, the hub 100 is connected to the transmission input shaft 110 via a shaft-hub connection 105. Here, the hub 100 circumferentially surrounds the transmission input shaft 110. The hub 100 is fixed to the transmission input shaft 110 by a hub nut 115 on the transmission input shaft 110 in the axial direction by clamping on a shoulder 111 of the transmission input shaft 110.
the hub 100 has a hub portion 120 which extends from the inside to the outside in the direction of the second friction lining carrier 70. In this case, the hub portion 120 of the hub 100 is arranged axially spaced apart from the fastening portion 91 of the second friction lining carrier 70. In this case, the fastening section 91 of the second friction lining carrier 70 and the hub section 120 of the hub 100 end at a similar radial height. The spring element 85 is connected at a second longitudinal end 125 to the hub section 120 of the hub 100 by means of a second riveted connection 130. In this embodiment, the second longitudinal end 125 of the spring element 85 is of the same design as its first longitudinal end 90.
the transmission input shaft 110 is supported in a transmission housing 135 (not shown) by means of a bearing 140. The bearing 140 is configured as a needle bearing.
The clutch device comprises an operating device 141 on the side opposite the bearing 140. The actuating device 141 comprises an actuating element 142, which is arranged on the upper side in fig. 1 and surrounds a release bearing 143. An operation lever 144 is provided radially inward of the release bearing 143. The operating lever 144 can be coupled, for example, to a clutch pedal in order to axially displace the operating element 142.
fig. 5 shows a perspective view of the counterpressure plate 145 of the clutch device 10 shown in fig. 1 to 4.
A counter-pressure plate 145 of the clutch device 10 is arranged axially between the hub 100 and the hub nut 115The pressure plate extends from the radially inner part to the radially outer part into the region of the friction plate pack 50. The counterpressure plate 145 is designed to remove or to provide a reaction force F from the friction plate package 50 for providing a frictional connection between the friction partners 55, 60, which is introduced into the friction plate package 50 in fig. 2G。
Counter pressure plate 145 has a support section 150 that is disposed between hub 100 and housing 135. Here, the support section 150 is radially inward and is arranged axially between the hub nut 115 and the hub 100. The counter-pressure plate 145 has a connecting section 155 adjoining the support section 150 on the radially outer side, and only a flange 160 adjoining the connecting section 155 on the radially outer side. On this flange 160, a counter-pressure surface 165 is arranged facing the friction plate pack 50. In this case, the counter-pressure surface 165 bears in the axial direction against the adjusting spring. Alternatively, it is conceivable for the counter-pressure surface to rest against the friction plate pack 50. The counter pressure surface 165 is arranged axially offset relative to the support section 150 and also relative to the connection section 155. The axial offset of the counter pressure surface 165 is selected such that the counter pressure surface 165 is arranged in the axial direction between the connecting section 155 and the support section 150.
In the connecting section 155, a plurality of first openings 170 extending in the circumferential direction are arranged radially inward with respect to the flange 160. In addition, a second opening 175 is provided in the support section 150. In the mounted state of the clutch device 10, the transmission input shaft 110 passes through the second opening 175.
in addition, the counter-pressure plate 145 comprises a plurality of centering elements 235 arranged at uniform intervals in the circumferential direction. These centering elements are arranged radially outside on the support section 150 of the counter-pressure plate 145. Here, the centering element 235 extends in the axial direction and is of a band-type configuration. Of course, the centering elements 235 may be arranged in other ways.
Fig. 6 shows a perspective view of the second friction lining carrier 70 of the clutch device 10 shown in fig. 1 to 4. The second friction plate carrier 70 has a first flange element 180. Here, the first flange element 180 is of annular configuration. A plurality of toothed elements 185 are arranged on the first flange element 180. The toothed element 185 is configured as a flat rivet. It is also conceivable for the toothed elements to be designed as spacer bolts. The flat head rivet can have a side wall 186, which can alternatively be omitted. The toothed element 185 extends in the axial direction, wherein a second flange element 190 is arranged at the axial end of the toothed element 185 opposite the first flange element 180. The flange elements 180, 190 extend substantially perpendicularly to the axis of rotation 25. In this embodiment, the tooth elements 185 have a U-shaped basic shape, wherein the U-shape opens radially outward. Of course, it is also conceivable for the tooth elements 185 to open radially inward. The toothed elements 185 are spaced apart from one another at uniform intervals in the circumferential direction, wherein two circumferentially adjacent toothed elements 185 and two flange elements 180, 190 each form a groove 191.
in this case, second friction lining carrier 70 is of a substantially stepped configuration, so that first flange element 180 has a larger outer diameter than second flange element 190. Adjacent to the inner circumferential face 195 of the first flange element 180, a toothed element 185 is arranged. The toothed element 185 is connected to the first flange element 180 at a first longitudinal end 205 by means of a first form-locking connection 200, preferably by means of a riveted connection. The toothed element 185 is connected at its second longitudinal end 210 to the second flange element 180 by means of a second positive connection 215.
radially inwardly, the second flange element 190 has a plurality of circumferentially distributed separating arms 220. The separating arm 220 extends substantially parallel to the axis of rotation 25. The release arm 220 passes through the first opening 170 and is connected at its free end to the actuating element 142 and couples the actuating element to the second friction lining carrier 70. Instead of a belt-type configuration, the release arm 220 can also be configured as a screw. Fig. 7 shows a perspective view of the hub of the clutch device 10 shown in fig. 1 to 4. In this embodiment, the fixing section 120 of the hub 100 is oriented perpendicularly to the axis of rotation 25 and has a triangular basic shape in cross section. Of course, other basic shapes are also contemplated. Through openings 225 are provided in each corner of the triangular cross section. The through-opening 225 is required to fix the spring element 85 to the fastening section 120 by means of the second rivet connection 130. On the radial inside, on a straight line between the axis of rotation 25 and the through-opening 225, a centering opening 230 is provided, which is arranged radially inside with respect to the through-opening 225. The centering openings 230 may be arranged in other ways as well. The centering openings 230 are configured correspondingly to the centering elements 235 of the counter-pressure plate 145. Likewise, the centering openings 230 are arranged in the fixing section 120 of the hub 100 at the same uniform spacing as the centering elements 235. In the mounted state of the clutch 10, the centering element 235 engages in the centering opening 230, so that the counter pressure plate 145 is positioned on the hub 100.
The clutch device 10 is configured as a pressure clutch. In order to connect the output side 20 to the input side 15 in a torque-locking manner, the actuating element 142 is moved downward in fig. 2 and provides the contact force F. If the actuating element 142 bears on the end side against the counter plate 145 on the upper side, the pressing force F is transmitted to the counter plate 145. Counter pressure plate 145 presses counter pressure surface 165 against friction plate set 50.
the spring element 85 is arranged in a clamping manner between the hub part 100 and the second friction lining carrier 70 and fixes the second friction lining carrier 70 in its position. To compress the friction plate pack 70, the second friction plate carrier 70 provides a reaction force F against the pressing force FG. Thereby pressing the friction partners 55, 60 such that a frictional lock between the friction partners 55, 60 is provided.
Counter force FGIs reinforced by means of a spring element 85. In this case, torque is introduced from the second friction lining carrier 70 via the first riveted connection 95 into the spring element 85. The spring element 85 transmits the torque further and via the second riveted connection 130 into the hub part 100, which leads the introduced torque out via the shaft/hub connection 105 into the transmission input shaft 110. In this embodiment, due to the axial offset of the fastening section 120 of the hub 100 relative to the fastening section 91 of the second friction disk carrier 70 and thus relative to the bolt-shaped orientation of the spring element 85, the spring element 85 acts as a crank lever, so that the spring element 85 is clamped between the hub and the second friction disk carrier 70. Since the spring element 85 is clamped between the second friction plate carrier 70 and the hub 100, the reinforcing force in the direction of the axis of rotation acts as a reinforcing force via the first riveted connection95 are introduced into the fastening section 91, so that the friction partners 55, 60 are pressed firmly against one another.
Fig. 8 shows a perspective view of the friction elements of the clutch device 10 shown in fig. 1 to 4, and fig. 9 shows a schematic illustration of a spacer 240 of the clutch device shown in fig. 1 to 4.
in order to provide a secure separation of the friction partners 55, 60 in the open state of the clutch device 10, in particular after the clutch device 10 has been operated, the clutch device 10 has a spacer device 240. Spacer 240 is disposed in groove 191 of second friction plate carrier 70.
In this embodiment, the spacer 240 is arranged radially on the inside on the second friction partner 60 and on the first flange element 180 of the second friction lining carrier 70. Of course, it is also conceivable for the spacer device 240 to be arranged on the first friction partner 55 and/or radially outside the friction partners 55, 60. It is also conceivable for the spacer 240 to be arranged on the first and second friction partners 55, 60.
The spacer 240 has, for example, a first spring element 245 on the second friction partner 60. The first spring member 245 has a first section 250 and a second section 255. The first section 250 is arranged on a fastening end 260 of the first spring element 245 and is connected to the second friction partner 60. The first section 250 extends substantially in a radial direction. A second section 255 is arranged adjacent towards the free end 265 of the first spring member 245. Thus, the second segment 255 is located between the first segment 250 and the free end 265. The second segment 255 extends substantially in the circumferential direction. The second section 255 has no curvature. Of course, the first spring member 245 may be configured in other forms.
In the circumferential direction, the tooth openings 266 of the internal teeth 80 adjoin the first spring element 245. The second friction partner 60 is centered on the second friction lining carrier 70 by means of the tooth openings 266.
Adjacent to the tooth openings 266 of the inner teeth 80, the spacing device 240 has a spacing element 270. The spacer element 270 is arranged with the fastening end 275 radially on the inside on the second friction partner 60. In addition, the distance element 270 has a free end 280, on which an abutment surface 285 is provided. The contact surface 285 is arranged substantially parallel to the friction surface 290 of the second friction partner 60. In this embodiment, the contact surface 285 is arranged axially with respect to the friction surface 290 and radially inward with respect to the friction surface 290, which is of annular design.
As described above, the friction plate pack 50 has alternately the first and the second friction partner 55, 60. In this case, the second friction partners 60 are arranged offset from one another in the circumferential direction, so that, in a plan view of the friction plate pack 50, the distance element 270 is arranged at the level of the first spring element 245. In this embodiment, the spacing device 240 is arranged at an offset angle of 60 ° of the first spring element 245 relative to the spacing element 270. This ensures that the friction partners 55, 60 are evenly spaced apart without tilting. Of course, other misalignment angles are also contemplated. To achieve an offset angle of 60 °, the spacing device 240 comprises three first spring elements 245 and three spacing elements 270, respectively, on the second friction plate. Then, in the mounting of the clutch device 10, the second friction partners 60 are arranged twisted with respect to one another in the circumferential direction in the mounting of the plate pack 50. This ensures that the first friction partners 55 can be of identical design.
In this embodiment, in the installed state, the free end 265 of the spring element 245 rests on the contact surface 285 of the spacer element 270. The distance element 270 and the first spring element 245 are matched to one another in such a way that, in the installed state of the clutch device 10, when it is opened, the first spring element 245 is prestressed and pressed against the contact surface 285.
In this embodiment, the first friction partners 55 are configured as steel friction plates or aluminum friction plates and are arranged alternately with the second friction partners 60 configured as friction plates. In this case, the first spring element 245 and the spacer element 270 pass radially on the inside past the first friction partner 55, so that in the released state of the clutch device 10 two second friction partners 60 arranged next to one another are pressed apart from one another in the axial direction. Thereby, the contact between the second friction partner 60 and the first friction partner 55 is reduced, so that the drag torque of the clutch device 10 as a whole is reduced. Of course, it is also conceivable for the first spring element 245 to be arranged on the first friction partner 55 and for the spacer element 270 to be arranged on the second friction partner 60. It is also conceivable for the contact surface 285 to be arranged axially at the level of the friction surface 290. In this embodiment, the spacer device 240 is arranged on two friction partners 55, 60, which are adjacent in the axial direction and are of identical design, in particular here on the second friction partner 60, wherein the spacer device 240 is guided radially on the inside over the first friction partner 55. Of course, it is also conceivable for the spacer device 240 to be guided axially over the plurality of friction partners 55, 60 and thus to bridge them.
In order to also be able to achieve a spacing of the second friction partner 60 directly adjoining the first flange element 180 in the axial direction in the open state of the clutch device 10, the spacer device 240 also has a spacer element 270 for the second friction partner 60, which is illustrated in fig. 8, on the first flange element 180. Of course, it is also conceivable for the first spring element 245 to bear with its free end 265 directly against the first flange element 180 on the end side, so that the first flange element 180 is constructed cost-effectively.
fig. 10 shows a perspective half-section through a clutch device 400 according to a second embodiment. The clutch device 400 is constructed analogously to the clutch device 10 shown in fig. 1 to 9. In contrast, the clutch 400 is designed as a pull-type clutch device.
further, in this embodiment, the hub 100 is of two-piece construction and includes a hub sleeve 405 and a securing section disposed radially outward of and coupled to the hub sleeve 405.
The counter pressure plate 145 is part of the operating device 141 and surrounds the release bearing 143 on the radially inner side. The operating elements as shown in fig. 1 to 9 can therefore be omitted.
An adjusting spring 166 is arranged on the side of the second disk carrier 70 opposite the counter plate 145, and rests on an adjusting ring 410, which is arranged axially between the second disk carrier 70 and the adjusting spring 166.
Counter plate 145 is attached to first opening 225 of hub 100 by screws 415. The screws 415 pass through a distance sleeve 420 for definitively determining the axial distance between the fixing section 120 and the counter-pressure plate 145. The screw 415 is fastened by means of a nut 425 on the side facing away from the counter plate 145.
Fig. 11 shows a schematic view of a spacing device 300 according to a second embodiment. The spacer device 300 is modified with respect to the spacer device 240 shown in fig. 1 to 8 in that, instead of the spacer element 270, a second spring element 305 is provided, which is configured like the first spring element 245. The second spring element 305 is connected with a fixed end to the second friction partner 60 and extends in the axial direction in the process in the direction of the first spring element 245, wherein the free end 265 of the second spring element 305 bears against the free end 265 of the first spring element 245, wherein in the open clutch the two spring elements 245, 305 press the two friction partners 55, 60 apart from one another in the radial direction in order to reduce the drag torque in this way. Of course, it is also conceivable for the second spring element 305 to be connected to the first friction partner 55 and/or the first flange element 180.
The clutch device 10, 400 described above has the advantages that: it is very simple in its structure and provides a separating force, a reduction in operating energy and a limitation of pushing torque (anti-bounce function) at the same time. Due to the use of stamped plate parts, the weight and the required installation space are greatly reduced. Due to its simplicity, the clutch device 10, 400 is low cost, flexible and reliable. In addition, the clutch device 10, 400 is not restricted in use, but can be used both at low and high displacement levels or in the case of high torques to be transmitted. It is also conceivable for the clutch device 10, 400 to be modified as a car clutch device, a dual clutch and/or a hybrid clutch.
Replacement of the friction plate pack 50 and installation of the clutch device in the vehicle are facilitated by using the centrally disposed hub nut 115 as a clutch protection device. The number of components is also reduced with respect to known clutch devices. The friction lining replacement is carried out here as follows: the handling device 141 is first removed. The operating device can be lifted by hand from the center of the second friction lining carrier 70. The hub nut 115 is then opened with a standard tool. The counter plate 145 can now be pulled out manually. The retaining ring 56 is then removed, so that the friction disk pack 50 can be pulled out of the first and second friction disk carriers 40, 70 axially upward.
It is noted that, of course, the features of the clutch device 10, 400 shown in fig. 1 to 11 can be combined with one another. It is also conceivable for the clutch device shown above to be constructed without the spring element 85.
List of reference marks
10 clutch device
15 input side
20 output side
25 axis of rotation
30 primary wheel
35 tooth part of primary wheel
40 first friction plate carrier
45 inner tooth part
50 friction plate group
55 first friction partner
56 fixed ring
60 second friction partner
65 external toothing of a first friction partner
70 second friction plate support
75 outer tooth of second friction plate carrier
80 internal toothing of a second friction partner
85 spring element
90 first longitudinal end of spring element
91 fixed section of second friction lining carrier
95 first rivet connection
100 hub
105 shaft-hub-connection
110 speed variator input shaft
115 hub nut
120 hub fixation section
125 second longitudinal end of the spring member
130 second riveted connection
135 casing
140 bearing
141 operating device
142 tension member
143 release bearing
144 operating rod
145 back pressure plate
150 support section
155 connecting section
160 flange
165 back pressure surface
166 adjusting spring
170 first opening
175 second opening
180 first flange element
185 tooth element
186 side wall
190 second flange element
191 grooves
195 inner circumferential surface of the first flange member
200 first form-fitting connection
205 first longitudinal end
210 second longitudinal end
215 second form-locking connection
220 separation arm
225 through opening
230 centering opening
235 centering element
240 spacer device
245 first spring element
250 first section
255 second segment
260 fixed end of the first spring element
265 free end of the first spring element
266 tooth openings
270 pitch element
275 fixed end portion
280 free end
285 contact surface
290 friction surface
300 space equipment
305 second spring element
400 clutch device
405 hub sleeve
410 adjustment
415 screw
420-space sleeve
425 nut
Claims (9)
1. Clutch device (10; 400) for a motorcycle for selectively torque-locking connecting an input side (15) with an output side (20),
-wherein the clutch device (10; 400) is rotatably supported about a rotational axis (25),
-comprising at least one friction plate pack (50) with a friction counterpart (55, 60) and a further friction counterpart (55, 60),
-and a spacing device (240; 300),
-wherein the spacing device (240; 300) comprises at least one first spring element (245),
-wherein the first spring element (245) is coupled with a first end (260) with the friction counterpart (55, 60) and with a second end (265) with the further friction counterpart (55, 60),
-wherein the spacer device (240; 300) is configured for separating the friction partners (55, 60) from one another in the axial direction in an operating state in which the clutch device (10; 400) is open,
-wherein the first spring element (245) comprises a first section (250) and a second section (255),
-wherein the first section (250) is arranged adjacent to the first end (260) and the second section (255) is arranged adjacent to the first section (250) and the second end (265),
-wherein the first section (250) extends substantially in a radial direction and the second section (255) extends at least partially in a circumferential direction,
-wherein the second section (255) is free of bends,
-wherein the spacing device (240; 300) comprises a spacing element (270) arranged on the friction counterpart (55, 60),
-wherein the spacing elements (240; 300) extend at least partially in a radial direction,
-wherein the first spring element (245) bears with the second end (265) against the spacing element (270).
2. The clutch device (10; 400) according to claim 1,
-wherein the spacing element (270) is connected with a fixed end (275) with the friction counterpart (55, 60) and has a free end (280),
-wherein an abutment surface (285) oriented parallel to a friction surface (290) of the friction counterpart (55, 60) is provided on the free end (280),
-wherein the contact surface (285) is arranged axially offset in the direction of the further friction partner (55, 60) relative to the friction surface (290).
3. The clutch device (10; 400) according to claim 1 or 2,
-comprising a friction plate carrier (70),
-wherein the friction lining carrier (70) is coupled with the input side (15) or the output side (20) in a torque-locking manner,
-wherein the friction plate carrier (70) comprises a first flange element (180) and a second flange element (190) arranged axially spaced apart from the first flange element (180),
-wherein, in axial direction, between the first flange element (180) and the second flange element (190), the friction plate carrier (70) comprises a plurality of circumferentially distributed toothed elements (185) connecting the first flange element (180) with the second flange element (190),
-wherein a recess (191) is provided in the friction lining carrier (70) between two tooth elements (185) arranged next to one another in the circumferential direction,
-wherein the spacing device (240; 300) is at least partially arranged in the groove (191).
4. The clutch device (10; 400) according to claim 3,
-wherein the friction counterpart (55, 60) has a toothed opening (266) configured correspondingly to the toothed element (185),
-wherein the first spring element (245), the tooth openings (266) and the spacing element (270) are arranged alternately in the circumferential direction.
5. The clutch device (10; 400) according to claim 1 or 2,
-wherein the output side (20) comprises a hub (100) with a fixed section (120),
-wherein the hub (100) is configured for providing a connection to a transmission input shaft (110),
-wherein a reinforcement device (85) is provided between the fixing section (120) and the friction plate carrier (70),
-wherein the reinforcement device (85) is designed to superimpose a reinforcing force on a pressing force for closing the clutch device (40, 100),
-wherein the reinforcement means (85) comprises at least one spring element (85).
6. The clutch device (10; 400) according to claim 5,
-wherein a counter plate (145) is provided axially adjacent to the friction counterpart (55, 60) and a separating device (141) is provided axially on the side of the counter plate (145) arranged opposite the friction plate pack (50),
-wherein the counter plate (145) has a groove (170) and the friction plate carrier (70) has a separator arm (220),
-wherein the separation arm (220) extends in an axial direction and through the groove (170).
7. The clutch device (10; 400) according to claim 6,
-wherein the counter pressure plate (145) comprises at least one centering element (235),
-wherein the centering element (235) extends at least in an axial direction,
-wherein the centering element (235) engages in a centering opening (230) of the fastening section (120) which is formed in a corresponding manner to the centering element (235),
-wherein the centering element (235) is arranged radially inwards with respect to the reinforcement means (85).
8. the clutch device (10; 400) according to claim 5, wherein the reinforcement means (85) comprises a leaf spring.
9. The clutch device (10; 400) according to claim 7, wherein the centering element (235) is of a band-shaped configuration.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102014206174.1 | 2014-04-01 | ||
| DE102014206174 | 2014-04-01 | ||
| PCT/DE2015/200169 WO2015149784A1 (en) | 2014-04-01 | 2015-03-19 | Clutch device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106133361A CN106133361A (en) | 2016-11-16 |
| CN106133361B true CN106133361B (en) | 2019-12-17 |
Family
ID=53175210
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580017441.5A Expired - Fee Related CN106133361B (en) | 2014-04-01 | 2015-03-19 | Clutch device |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN106133361B (en) |
| DE (1) | DE112015001634A5 (en) |
| WO (1) | WO2015149784A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102016213657B4 (en) | 2016-07-26 | 2018-09-27 | Schaeffler Technologies AG & Co. KG | Coupling device for a drive train of a vehicle |
| US10024369B2 (en) * | 2016-09-12 | 2018-07-17 | Schaeffler Technologies AG & Co. KG | Clutch disc with axially expanded spline teeth |
| DE102018119167A1 (en) * | 2018-08-07 | 2020-02-13 | Schaeffler Technologies AG & Co. KG | Self-reinforcing multi-plate clutch with reinforcing disk pressing the inner disk and drive train with such multi-plate clutch |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6026944A (en) * | 1998-03-25 | 2000-02-22 | Shin Nippon Wheel Industries Co., Ltd. | Wet multi-plate clutch |
| DE19904136A1 (en) * | 1999-02-03 | 2000-08-10 | Mannesmann Sachs Ag | Multiple disk clutch for cars has intermediate disk between clutch pads, pressure disks pressing them against it and elastic components spacing disks from pads |
| CN101545512A (en) * | 2008-03-28 | 2009-09-30 | 本田技研工业株式会社 | Vehicle clutch |
| DE102008062644A1 (en) * | 2008-12-17 | 2010-06-24 | Daimler Ag | Clutch plate unit has clutch plate and spring unit which provides clutch plate adhesion strength, where clutch plate and spring unit are partially arranged in one piece |
| CN103375501A (en) * | 2012-04-16 | 2013-10-30 | 通用汽车环球科技运作有限责任公司 | Tabbed separation clutch plate |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102010019699B4 (en) * | 2009-05-26 | 2021-07-29 | Magna powertrain gmbh & co kg | Multi-disc clutch |
| JP4939585B2 (en) * | 2009-09-30 | 2012-05-30 | 本田技研工業株式会社 | Multi-plate clutch device |
| US8640842B2 (en) * | 2011-03-09 | 2014-02-04 | American Axle & Manufacturing, Inc. | Clutch plate having integrated separating feature |
-
2015
- 2015-03-19 WO PCT/DE2015/200169 patent/WO2015149784A1/en active Application Filing
- 2015-03-19 DE DE112015001634.1T patent/DE112015001634A5/en not_active Withdrawn
- 2015-03-19 CN CN201580017441.5A patent/CN106133361B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6026944A (en) * | 1998-03-25 | 2000-02-22 | Shin Nippon Wheel Industries Co., Ltd. | Wet multi-plate clutch |
| DE19904136A1 (en) * | 1999-02-03 | 2000-08-10 | Mannesmann Sachs Ag | Multiple disk clutch for cars has intermediate disk between clutch pads, pressure disks pressing them against it and elastic components spacing disks from pads |
| CN101545512A (en) * | 2008-03-28 | 2009-09-30 | 本田技研工业株式会社 | Vehicle clutch |
| DE102008062644A1 (en) * | 2008-12-17 | 2010-06-24 | Daimler Ag | Clutch plate unit has clutch plate and spring unit which provides clutch plate adhesion strength, where clutch plate and spring unit are partially arranged in one piece |
| CN103375501A (en) * | 2012-04-16 | 2013-10-30 | 通用汽车环球科技运作有限责任公司 | Tabbed separation clutch plate |
Also Published As
| Publication number | Publication date |
|---|---|
| DE112015001634A5 (en) | 2017-02-09 |
| WO2015149784A1 (en) | 2015-10-08 |
| CN106133361A (en) | 2016-11-16 |
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