WO2012152243A1 - Doppelkupplung für kraftfahrzeuge - Google Patents
Doppelkupplung für kraftfahrzeuge Download PDFInfo
- Publication number
- WO2012152243A1 WO2012152243A1 PCT/DE2012/000413 DE2012000413W WO2012152243A1 WO 2012152243 A1 WO2012152243 A1 WO 2012152243A1 DE 2012000413 W DE2012000413 W DE 2012000413W WO 2012152243 A1 WO2012152243 A1 WO 2012152243A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- bearing
- vibration damper
- torsional vibration
- supported
- Prior art date
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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
- F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
-
- 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
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
- F16D25/085—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation the clutch actuation being of the pull type
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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
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
- F16D25/087—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation the clutch being actuated by the fluid-actuated member via a diaphragm spring or an equivalent array of levers
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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
- F16D25/00—Fluid-actuated clutches
- F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
-
- 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
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
- F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections
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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
- F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
- F16D2013/703—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members the pressure plate on the flywheel side is combined with a damper
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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
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0607—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate
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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
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0669—Hydraulically actuated clutches with two clutch plates
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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
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0692—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric with two clutches arranged axially without radial overlap
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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
- F16D2300/00—Special features for couplings or clutches
- F16D2300/12—Mounting or assembling
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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
- F16D2300/00—Special features for couplings or clutches
- F16D2300/24—Concentric actuation rods, e.g. actuation rods extending concentrically through a shaft
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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
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
- F16D25/086—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation the clutch being actuated by a push rod extending coaxially through the input or output shaft
Definitions
- the present invention relates to a dual clutch for motor vehicles or trucks according to the preamble of claims 1 to 3.
- clutches transmit the rotational movement of the engine to the transmission input shafts of a transmission. At the same time they are subjected to different forces (for example, actuating, centrifugal, inertial and centrifugal forces). Therefore, clutches must be supported rotatably but also axially and radially fixed.
- coupling with (only) a bearing point are usually supported by the crankshaft or are connected to a rolling bearing with the transmission input shafts or the clutch housing.
- a double clutches with two bearings is known from DE 102008019949A1, in which the double clutch is supported on the transmission side via a cover bearing axially and radially on the transmission housing and additionally on the motor side via the dual mass flywheel radially on the crankshaft.
- the double clutches according to the invention with two bearing points have a short, manageable and insensitive tolerance chain: “short”, since geometrical deviations of the dampers (eg DMF) have no influence on the bearing orientation, “controllable”, since all internal clutches Radial offsets can be measured and compensated after assembly, and “insensitive”, since the distance between the bearings is relatively large, whereby remaining inaccuracies in the bearing alignment cause only a slight tilting of the coupling.
- FIG. 1 shows an exemplary embodiment of a double clutch, in which a part of an actuating device of a partial clutch is arranged in the clutch bell,
- FIG 3 shows a further embodiment of a double clutch with two-sided storage, using a removable support on the crankshaft,
- FIG. 5 shows a further embodiment of a double clutch with two-sided support, using a rigid support on the crankshaft,
- FIG. 6 shows a further embodiment of a double clutch with two-sided support, using a rigid support on the crankshaft, wherein a device for compensating for radial offset, disposed between the transmission-side bearing and the clutch cover, is provided
- 7 shows a further embodiment of a double clutch with two-sided support, in which a wide support base is realized
- FIG. 8 shows another embodiment of a double clutch with two-sided radial bearing and a separate thrust bearing
- the double clutch 1 can also be composed of partial clutches 2, 3, which have the same direction of actuation. This is e.g. in the combination of a wound up and a compressed coupling the case. If, for safety reasons, two self-opening partial clutches must be used, two compressed, one compressed and one closed or two engaged clutches can also be used.
- both partial clutches 2, 3 are each arranged on one side of a central flywheel mass 8, which at the same time acts as an intermediate pressure plate, so that the pressure plates 6, 7 of both partial clutches 2, 3 face one another.
- an external damper 9 is arranged between the drive unit and the dual clutch 1.
- the crankshaft 10 of the internal combustion engine is connected via screw 11 fixed to an input part 32 of the damper 9.
- the input part 32 of the damper 9 has substantially the shape of a radially extending annular disc, which forms a vibration damper cage radially outward. Radially outside a starter ring gear 23 is applied to the input part 32.
- At least one energy storage device in particular a spring device, is at least partially accommodated in the vibration damper cage.
- a spring device an output part 33 of the damper 9 engages.
- Radially inside the output part 33 of the damper 9 is detachably connected by a spline 20 with a clutch cover 5.
- a sensor spring 34 is arranged between this clutch cover 5 and one with the pressure plate 7 in operative connection disc spring 24, a sensor spring 34 is arranged.
- This sensor spring 34 is to be connected to the disc spring 24 by means of a suitable connection for the purpose of realizing the wear adjustment 31 provided on this partial clutch 2.
- the connection can be made, as in this example, by means of a plurality of distributed over the circumference arranged connecting elements 35.
- connection can also be produced, for example, by means of a bayonet connection with a tow hook. These hooks can be worked out of the material of the components to be joined together. These can also be attached to the components in addition. To facilitate assembly, the ends of these connecting elements 35 may have a bayonet connection option.
- this connection can also be realized by at least one riveted with the sensor spring 34 or the plate spring 24 stepped bolt 35 or flat rivet.
- the connecting elements 35 can also be designed so that they are made flat, so that at least two are connected to each other.
- the connecting elements 35 thus executed are then provided with a plurality of connection points to the side of the plate spring or even to the sensor spring.
- the connecting elements 35 are made of sheet metal as a stamped or stamped bent part or as a wire bending part.
- the intermediate pressure plate 8 of the double clutch 1 is fixed by means of screw 21.
- friction linings of a first clutch disc 26 can be clamped between the pressure plate 7 and the intermediate pressure plate 8.
- This first KupplungsSE26 is rotatably connected via a hub part with a first transmission input shaft 28, which is designed as a hollow shaft.
- the first transmission input shaft 28 is rotatably arranged in a second, also designed as a hollow shaft transmission input shaft 29.
- a hub portion of a second clutch plate 27 is rotationally fixed connected to the drive-side end of the second transmission input shaft 29.
- On the second clutch disc 27 are fixed radially outside friction linings, which can be clamped between the intermediate pressure plate 8 and the pressure plate 6.
- a clutch cover 4 is also fastened by means of screw 22.
- the first transmission input shaft 28 is traversed by a pull rod 19 when using this type of part clutches 2, 3, so that it is mounted in the center of both transmission input shafts 28, 29.
- a floating bearing 20 forming spline of the clutch cover 5 is connected with the interposition of the external damper 9 for transmitting torque to the crankshaft 10.
- the double clutch 1 is actuated via actuators with actuating bearings 16, 17. These actuating bearings 16, 17 in turn interact with actuating levers 24, 25 or actuating devices, such as the actuating device 15 shown together.
- the actuating levers 24, 25 are on the one hand a plate spring 24 and on the other hand a lever spring 25. By means of this, the two pressure plates 6, 7 in the axial direction relative to the intermediate pressure plate 8 are limited displaced.
- the actuating bearings 16, 17 operatively connected to the actuators are hydraulically pressurized.
- the pull rod 19 serves to actuate the actuating bearing 16, which is arranged on this end.
- This pull rod 19 is pressurized by means of an actuating device arranged outside the clutch bell, which preferably consists of a hydraulic cylinder, so that it is axially movable. This saves installation space in the clutch bell and facilitates the hydraulic venting of the externally arranged hydraulic cylinder.
- the end of this tie rod 19 is threaded, so that by means of a nut 18, the actuating bearing 16 can be fixed on this.
- the actuating bearing 16 with the plate spring 24 in operative connection.
- the bearing inner ring of the actuating bearing 17 is designed so that it can form an operative connection with the lever spring 25.
- the actuation of the actuating bearing 17 is effected by an axial movement of the bearing in the housing of the slave cylinder 15 piston, which is hydraulically acted upon by a pressure force. If, however, the dual clutch 1 is constructed from two partial clutches which have the same direction of actuation, as in the case of the combination of a retracted and a compressed clutch, then due to the changed actuation direction, the tension rod 19 mounted in the center of the transmission input shafts 28, 29 becomes a push rod.
- the bearing of the double clutch 1 is based on the fixed bearing floating bearing principle.
- the fixed bearing 14 is formed by an inserted into the clutch cover 4 bearing, which is arranged on the side of the transmission housing 12.
- the double clutch. 1 firmly connected to the transmission housing 12.
- the fixed bearing 14 Since the direction of actuation of both partial clutches 2, 3 of the double clutch 1 is in each case opposite, the fixed bearing 14 must be selected so that this axial forces can be transmitted in both directions.
- the direction of the axial forces that the fixed bearing 14 has to transmit depends on the respective operating state of the double clutch 1.
- the changes in the loading direction make high demands on the fixed bearing 14. For this reason, preferably deep groove ball bearings with four-point ground, four-point bearings or double row angular contact ball bearings are used.
- the floating bearing 20 is formed for the dual clutch 1 by the mounting of the clutch cover 5 on the output part 33 of the external damper 9.
- This bearing 20 supports the dual clutch 1 in the radial direction on the crankshaft 10 from.
- a sliding or rolling bearing 37 Between the output part 33 and the input part 32 of the damper 9 is a sliding or rolling bearing 37, whereby the double clutch 1 can be supported on the crankshaft 10 via the damper 9.
- the desired axial degree of freedom of this bearing 20 is formed by the spline formed at this point. In this case, can be dispensed with a defined bearing point for the dual clutch 1 by the output member 33 is not stored on the input part 32, but only via the spline.
- the dual clutch 1 is only supported by the fixed bearing 14, whereby the axial offset in the radial direction between the crankshaft 10 and the bearing 14 can be compensated, since in this case the radial compensation takes place in the bow spring channel of the damper 9.
- the fixed bearing 14 is supported via a connecting flange 30 on the housing of a slave cylinder 15 arranged concentrically around the transmission input shaft 29.
- This connecting flange 30 is by means of screw 13 a solid connection to the subsequent transmission 12 produced.
- the partial region of the connecting flange 30 which is connected to the fixed bearing 14 as an inner ring of the fixed bearing, so that an additional bearing inner ring could be dispensed with.
- connection point 13 between the fastener formed in this example as a flange 30 and the gearbox 12 must be accessible for assembly.
- This access which can be realized by recesses in the coupling parts, can be done in a radial or axial manner.
- the at least one connection point 13 can be arranged on a pitch circle which is larger than the outer diameter of the double clutch 1.
- a space-saving variant, however, is that at least one attachment point 13 lies on a smaller pitch circle diameter.
- This accessibility through the entire double clutch 1 can be ensured by recesses are provided in the individual, the compound concealing components that are at least temporarily or in certain operating conditions on top of each other.
- the axial accessibility to ensure at least one connection point is that the dual clutch 1 is not connected as a fully assembled unit with the gear 12, but is gradually connected as a set of subassemblies set with the gear 12. The assembly of the double clutch 1 is then carried out as follows:
- the actuator 15 is fixed to the housing 12 of the transmission. However, this assembly step can be omitted if the actuator 15 is already connected in advance with parts of the dual clutch 1. Thereafter, the first subassembly is inserted into the clutch housing. This first subassembly consists essentially of the bearing 14, the clutch cover 4, the actuating lever 25 and the pressure plate 6 together. Subsequently, the first subassembly is connected to the transmission 12. The accessibility to the connection points can be made possible by recesses in the cover 4 and between the actuating levers 25. Subsequently, the clutch plate 27 is attached to the transmission input shaft 29. Thereafter, the second subassembly is placed on the already mounted coupling components.
- This subassembly consists essentially of the between flywheel 8 and the spline 20 arranged components. Subsequently, this second subassembly is connected to the first subassembly, for example by means of screwed connections. Thereafter, the actuating bearing 16 is fixed to the actuating rod 19. Now, the external damper 9 is bolted to the crankshaft 10 of the drive motor, not shown. Finally, both the drive motor and the transmission 12 are assembled with the dual clutch 1 and connected to this. When joining both units, the provided with a spline 20 output part 33 of the damper 9 is brought into operative connection with the cover 5 of the motor-side part clutch 2.
- the clutch can be further completed by the intermediate pressure plate 8 is inserted into the clutch cover 4 and connected by means of screw 22 on the circumference with the clutch cover 4.
- the first clutch plate 26 is pushed onto the hub profile of the first transmission input shaft 28 with its correspondingly formed inner region.
- the pressure plate 7 is placed.
- the wear adjustment 31 which is above the step pin 35 with the plate spring 24 in conjunction.
- the thus prepared assembly is closed with the clutch cover 5, which has recesses corresponding to the circumference into which screwed connections 21 can be inserted, via which the clutch cover 5 is fastened with the threaded bores provided in the intermediate plate 8.
- the actuating bearing 16 is placed on the end of the push rod 19 inserted into the center of the transmission input shafts 28, 29, which is fixed in position on the latter by means of the nut 18.
- the spline 20 can be realized, so that the entire dual clutch 1 is interviewedstecken only on this output part 33 to connect to the crankshaft 10 and thus the not shown To be able to produce drive.
- the actuating devices of both partial clutches 2, 3 must be arranged in the clutch bell, as a result of which the axial space is further shortened, the actuating rod 19 of FIG. 1 is replaced by a fixed tube and the actuating device 36 for the first partial clutch 2 between this tube 19 and the actuating bearing 16, as shown in FIG.
- the remaining structure of this double clutch 1 shown in Figure 2 is the same as in Figure 1.
- the dual clutch shown in Fig. 3 has a transmission side disposed rolling bearing 114 which connects the clutch cover 104 of the clutch housing with the gear housing 112 and the clutch 100 axially and radially supported.
- the motor-side clutch cover 105 (which is connected to the central plate 108 and the transmission-side clutch cover 104 via the screw connection 121) is radially inwardly connected (eg screwed) to a cup-shaped connecting component 105A, this plug-shaped connecting component 105A having a pilot pin 105B, wherein the pilot pin 105B is arranged coaxially with the axis of rotation X of the transmission input shafts 128, 129 and the dual clutch 100 and the DMF 109.
- At least two bearing points are also to arrange the axes of rotation of these bearings coaxial to each other, wherein the coaxiality of the bearings is more important than the aforementioned coaxiality between bearings and transmission input shafts you have to decide on one of the two conditions due to the tolerance situation.
- the pot-shaped connecting element 105A completely close a motor-side opening of the clutch cover 105, wherein in the connection region between the clutch cover 105 and pot-shaped connecting element 105A sealing devices may be arranged for liquid-tight closure of the coupling interior of the dual clutch 100.
- the connection between the cup-shaped member 105A and clutch cover 105 for example be realized via fittings.
- a driver gear rim 120A may be arranged on the clutch cover 105, for example in an intermediate position between the cup-shaped connecting element 105A and the clutch cover 105.
- This driver gear rim 120A includes a toothing, in which engages a further toothing of a Popeflansches 133 of the DMF 109th Via a bracing device 133A, a backlash-free connection between the teeth of the ZMS output flange 133 and the driver toothed ring 120A can be realized.
- the driver gear rim 120A can also be formed integrally with the cup-shaped connecting element 105A.
- the clutch 107 results in a removable support of the dual clutch on the crankshaft 110.
- the clutch 100 is thereby supported directly on the crankshaft 110, for example by a sliding or rolling bearing 106 in the pilot bearing bore 110A.
- the bearing alignment after coupling assembly is already identical to the later state in the vehicle. This provides the option to check bearing alignment after coupling assembly and adjust if necessary. This possibility exists even if the motor-side bearing bracket or bearing pin 105B - as here in the present embodiment of FIG. 3 - for assembly reasons releasably connected to the clutch, since it can still be selectively paired with the clutch and arranged. With the dampers or flywheels this is logistically hardly possible because the flywheel is part of the engine and the clutch (dual clutch) is part of the transmission.
- FIG. 4 shows another embodiment of the present dual clutch 200 in which the bearing 206 on the crankshaft 210 is directly connected to the clutch cover 205 of the engine side (sub) clutch, i. the division into a clutch cover 105 and a detachably connected with this cup-shaped connecting element 105A is eliminated.
- This configuration is always requested when transmission input shafts or their adjacent components no longer need to be accessible after assembly of the engine-side part-coupling.
- the seal of the clutch interior is improved. In the embodiment shown in Fig. 4, this is achieved by the motor-side actuating bearing 216 is connected to the plate spring tongues 224 and during assembly only on the
- Push rod 219 is attached.
- the sectional view shown in Figure 4 is presently chosen such that the type of connection of the pressure plate (which may also apply to the other embodiments shown) is apparent.
- the pressure plate 205 of the transmission-side clutch is connected via leaf spring pawls 205A to the clutch cover 205 of the transmission-side clutch.
- the pressure plate 207 is connected to the clutch cover 205 of the engine-side clutch via leaf spring assemblies 205B.
- the clutch covers 205 and 204 are connected to the central counter press plate 208 via separate screw connections, resulting in a different assembly sequence, especially in connection with the connection of the pressure plate to the clutch covers and the formation of corresponding preassembly assemblies.
- one of the two clutch cover can be attached to the central plate 208 via first fittings (to form a first subassembly) and the second cover (with its subassembly) are connected via second screw with the first cover (as in Figure 3 with the screw 121st shown).
- first fittings to form a first subassembly
- second cover with its subassembly
- second screw with the first cover (as in Figure 3 with the screw 121st shown).
- a wear adjustment between the plate spring 225 and the pressure plate 205 of the transmission side Clutch can be arranged a wear adjustment.
- an annular element 226 may be provided for forming a defined support point between the pressure plate 205 and plate spring 225.
- an adjusting device for the motor-side coupling can be provided between the clutch cover 205 and the plate spring 224.
- Push rod 219 which is pressed by a corresponding pressure force in conjunction with the selected Auflagerungsige between disc spring 224 and clutch cover 205, the motor-side coupling.
- Fig. 5 shows another dual clutch 300 in which the engine-side bearing 306 (e.g., rolling or plain bearing) is attached to the crankshaft 310 but is not disposed in the pilot bearing bore 310A.
- the engine-side bearing 306 is arranged in front of the crankshaft 310 and attached directly or indirectly to the inner ring 306A thereof.
- the coupling 300 is radially supported.
- the arrangement in front of the crankshaft 310 has the advantage that the bearing dimensions are not dependent on the pilot bearing bore and can be chosen more freely and application-specific.
- bearings which can transmit not only radial but also axial forces, can be realized by a sliding bearing seat (preferably between the clutch and bearing or bearing and crankshaft) an axial compensation.
- the axial clamping forces which occur due to remaining axial tolerances or the operation of the clutch, are then determined by the axial spring action (softness) of the clutch cover.
- FIG. 6 corresponds to the embodiment of FIG. 3.
- FIG. 6 shows a further dual clutch 400, in which the motor-side bearing 406 (eg rolling or sliding bearing), although attached to the crankshaft 410, but not arranged in a pilot bearing bore.
- the engine-side bearing 406 is arranged in front of the crankshaft 410 and attached to the outer ring 406A on this directly or indirectly.
- On the other bearing inside the clutch 400 is radially supported.
- the arrangement in front of the crankshaft 410 has the advantage that the bearing dimensions are not dependent on the pilot bearing bore and can be chosen more freely and application-specific. If bearings are used at this point, which can transmit not only radial but also axial forces, can be realized by a sliding bearing seat (preferably between the clutch and bearing or bearing and crankshaft) an axial compensation.
- FIG. 6 corresponds to the embodiment of FIG. 3 and FIG. 5.
- the engine-side movable bearing 506 is arranged as in some variants already described in the pilot bearing bore 506A and therefore already in the engine already maximum facing position.
- the bearing 514 is displaced in the region usually reserved for the disengagement system on the rear wall of the transmission near the transmission input shafts.
- the fixed bearing 514 on the actuating system is arranged axially behind the hydraulic cylinder and the actuating bearing 517.
- the bearing 514 it is also possible for the bearing 514 to be radially above the cylinder and / or the actuator. positioning bearings.
- a bearing 514 displaced in this way in the direction of transmission can also be fastened separately to the transmission, so that the bearing 514 and the actuating system are connected to the transmission independently of one another (as shown, for example, in FIG. 3).
- Another possibility is to attach the actuation system to the bearing 514 (preferably to its stationary part). The electrical or hydraulic actuation or signal transmission of the actuation system can then optionally take place via or through the bearing components, or be guided past the bearing.
- the exemplary embodiment according to FIG. 8 shows a double clutch 600 with two actuating systems arranged on the transmission side, with the support already known from FIG. 3 on the crankshaft and a transmission-side mounting which is based on a thrust bearing 602 and a radial bearing 601.
- the central plate 603 is provided with a tubular extension 604 extending axially between the two transmission input shafts gearbox and at the end of a bearing (preferably in radially flat design example, a needle bearing) is arranged.
- a bearing preferably in radially flat design example, a needle bearing
- a thrust bearing 602 which is fixed to the inner transmission input shaft and the clutch 60 is supported via the central plate or its adjacent components.
- a thrust bearing 602 which is fixed to the inner transmission input shaft and the clutch 60 is supported via the central plate or its adjacent components.
- other types of bearings such as e.g. axial ball bearings, deep groove ball bearings or angular contact ball bearings are used.
- the clutch can also be axially supported via the outer transmission input shaft.
- FIG. 9 shows a similar principle in which the transmission-side support takes place through a single bearing 701 on one of the transmission input shafts.
- the following describes the possibility of compensating misalignments.
- bearings can be permanently aligned with each other.
- measures for alignment and permanent fixation for individual separation points are described.
- the methods can be transferred in principle to all separation points between the two bearings.
- all the methods described can also be combined with one another or with other fastening methods (for example screwed or riveted joints).
- Variant I compensation at a provided for the subsequent assembly process separable connection
- connection between motor-side bearing and the central plate is made divisible, eg for the assembly of actuation bearings or securing elements in the field of transmission input shafts, this separation point is a good way there to align the two bearings to each other. This can be done, for example, by the bearing carriers are aligned individually and then this position is fixed permanently reproducible (eg by pinning or another exactly reproducible joining method).
- Another way of compensating for the radial offset of the coupling is to provide a bearing carrier for each coupling with a coupling specially adapted to the respective coupling. select or produce a set (offset between bearing and joint) so that the offset between coupling and bearing carrier cancel each other out.
- the bearings can be adjusted by targeted alignment of the partial clutches.
- a positive connection of the aligned components makes sense. This can be done, for example, by an embossing process, which presses the lid material, which is located after the alignment in front of a special depressions in the central plate in this (Fig. 5, connection between the central plate and motor side Kupplungsdeckel).
- Variant II Compensation at a connection point that no longer needs to be opened for the subsequent assembly process.
- the radial offset of the bearings can also be compensated by components in the circumferential direction are rotated against each other and these rotational movements are deliberately not exactly concentric.
- Fig. 6 shows such a construction.
- Bearing and clutch cover are connected via an intermediate ring 401, the inner and outer cylindrical surface are not concentric to each other.
- the gearbox-side bearing has ' a ring connected to the coupling (eg bearing outer ring) whose connection geometry (eg bearing outer diameter) is also eccentric to the ball raceway.
- the coupling eg bearing outer ring
- connection geometry eg bearing outer diameter
- the two components can be moved radially until the bearings are aligned and then bolted or otherwise connected in this position.
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP12721717.2A EP2707616A1 (de) | 2011-05-11 | 2012-04-23 | Doppelkupplung für kraftfahrzeuge |
CN201280022802.1A CN103547826B (zh) | 2011-05-11 | 2012-04-23 | 用于机动车的双离合器 |
DE112012002022.7T DE112012002022A5 (de) | 2011-05-11 | 2012-04-23 | Doppelkupplung für Kraftfahrzeuge |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102011101149.1 | 2011-05-11 | ||
DE102011101149 | 2011-05-11 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2012152243A1 true WO2012152243A1 (de) | 2012-11-15 |
Family
ID=46124239
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2012/000413 WO2012152243A1 (de) | 2011-05-11 | 2012-04-23 | Doppelkupplung für kraftfahrzeuge |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2707616A1 (de) |
CN (1) | CN103547826B (de) |
DE (2) | DE112012002022A5 (de) |
WO (1) | WO2012152243A1 (de) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20140151181A1 (en) * | 2011-08-05 | 2014-06-05 | Schaeffler Technologies AG & Co. KG | Clutch assembly |
US9657784B2 (en) | 2014-02-26 | 2017-05-23 | Schaeffler Technologies AG & Co. KG | Double clutch mounting assembly |
WO2017215705A1 (de) * | 2016-06-16 | 2017-12-21 | Schaeffler Technologies AG & Co. KG | Doppelkupplung mit wälzlager und labyrinthähnlicher dichtungsanordnung |
WO2018029400A1 (fr) * | 2016-08-11 | 2018-02-15 | Valeo Embrayages | Système d'embrayage, kit de montage et procédé de montage ou de démontage d'un système d'embrayage |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2015014360A1 (de) * | 2013-08-01 | 2015-02-05 | Schaeffler Technologies Gmbh & Co. Kg | Ausrückvorrichtung für eine kupplung |
DE102014224111A1 (de) | 2013-12-11 | 2015-06-11 | Schaeffler Technologies AG & Co. KG | Verbrennungskraftmaschinenseitige Belüftung über Kühlöffnungen in der Dämpfungseinheit |
EP3123044B1 (de) * | 2014-03-27 | 2018-03-21 | Schaeffler Technologies GmbH & Co. KG | Blechanpressplatte und drucktopf als gemeinsames bauteil |
DE102015207156A1 (de) | 2015-04-20 | 2016-10-20 | Schaeffler Technologies AG & Co. KG | Doppelkupplungsgetriebe |
DE102016201948B4 (de) * | 2016-02-10 | 2017-09-14 | Schaeffler Technologies AG & Co. KG | Doppelkupplung mit einem zur Demontage optimierten Mitnehmerring |
CN107054046A (zh) * | 2016-12-21 | 2017-08-18 | 重庆长安汽车股份有限公司 | 一种混合动力耦合机构与双离合变速器导向连接结构 |
DE102018126286A1 (de) * | 2018-10-23 | 2020-04-23 | Schaeffler Technologies AG & Co. KG | Antriebsmodul mit einer getriebeseitigen Abstützlagereinrichtung |
DE102019129848A1 (de) * | 2019-10-02 | 2021-04-08 | Schaeffler Technologies AG & Co. KG | Kupplungsaggregat, insbesondere für ein Hybridmodul, zum gedämpften Ankuppeln einer Brennkraftmaschine an einem Antriebsstrang eines Kraftfahrzeugs |
DE102019129814A1 (de) * | 2019-10-02 | 2021-04-08 | Schaeffler Technologies AG & Co. KG | Kupplungsaggregat, insbesondere für ein Hybridmodul, zum gedämpften Ankuppeln einer Brennkraftmaschine an einem Antriebsstrang eines Kraftfahrzeugs |
DE102020114131B4 (de) * | 2020-05-27 | 2022-08-18 | Schaeffler Technologies AG & Co. KG | Aktorvorrichtung für eine Kupplungsbaugruppe eines Fahrzeuges und Kupplungsbaugruppe eines Fahrzeuges |
DE112020007611T5 (de) * | 2020-09-17 | 2023-07-06 | Schaeffler Technologies AG & Co. KG | Befestigungselement für eine Doppelkupplung, Doppelkupplung und Verfahren zum Zusammenbau eines Getriebes |
DE102022114607A1 (de) | 2022-06-10 | 2023-12-21 | Schaeffler Technologies AG & Co. KG | Drehmomentübertragungsvorrichtung |
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FR2851547A1 (fr) * | 2003-02-20 | 2004-08-27 | Valeo Embrayages | Dispositif comportant un module d'embrayage/de debrayage centre. |
DE102008019949A1 (de) | 2007-04-25 | 2008-10-30 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Doppelkupplung |
WO2011124203A1 (de) * | 2010-04-08 | 2011-10-13 | Schaeffler Technologies Gmbh & Co. Kg | Doppelkupplung |
Family Cites Families (2)
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BR0108393A (pt) * | 2000-02-15 | 2003-03-11 | Luk Lamellen & Kupplungsbau | Dispositivo transmissor de torque |
DE10310831A1 (de) * | 2002-04-10 | 2003-11-06 | Luk Lamellen & Kupplungsbau | Antriebsstrang und Verfahren zu dessen Betrieb |
-
2012
- 2012-04-23 EP EP12721717.2A patent/EP2707616A1/de not_active Withdrawn
- 2012-04-23 CN CN201280022802.1A patent/CN103547826B/zh not_active Expired - Fee Related
- 2012-04-23 WO PCT/DE2012/000413 patent/WO2012152243A1/de active Application Filing
- 2012-04-23 DE DE112012002022.7T patent/DE112012002022A5/de not_active Withdrawn
- 2012-04-23 DE DE102012206658A patent/DE102012206658A1/de not_active Withdrawn
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2851547A1 (fr) * | 2003-02-20 | 2004-08-27 | Valeo Embrayages | Dispositif comportant un module d'embrayage/de debrayage centre. |
DE102008019949A1 (de) | 2007-04-25 | 2008-10-30 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Doppelkupplung |
WO2011124203A1 (de) * | 2010-04-08 | 2011-10-13 | Schaeffler Technologies Gmbh & Co. Kg | Doppelkupplung |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20140151181A1 (en) * | 2011-08-05 | 2014-06-05 | Schaeffler Technologies AG & Co. KG | Clutch assembly |
US9657784B2 (en) | 2014-02-26 | 2017-05-23 | Schaeffler Technologies AG & Co. KG | Double clutch mounting assembly |
WO2017215705A1 (de) * | 2016-06-16 | 2017-12-21 | Schaeffler Technologies AG & Co. KG | Doppelkupplung mit wälzlager und labyrinthähnlicher dichtungsanordnung |
WO2018029400A1 (fr) * | 2016-08-11 | 2018-02-15 | Valeo Embrayages | Système d'embrayage, kit de montage et procédé de montage ou de démontage d'un système d'embrayage |
CN109715966A (zh) * | 2016-08-11 | 2019-05-03 | 法雷奥离合器公司 | 离合器系统、用于安装或拆卸离合器系统的套件和方法 |
Also Published As
Publication number | Publication date |
---|---|
DE112012002022A5 (de) | 2014-02-06 |
CN103547826A (zh) | 2014-01-29 |
DE102012206658A1 (de) | 2012-11-15 |
CN103547826B (zh) | 2016-08-24 |
EP2707616A1 (de) | 2014-03-19 |
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