WO2010149130A2 - Dual clutch - Google Patents
Dual clutch Download PDFInfo
- Publication number
- WO2010149130A2 WO2010149130A2 PCT/DE2010/000671 DE2010000671W WO2010149130A2 WO 2010149130 A2 WO2010149130 A2 WO 2010149130A2 DE 2010000671 W DE2010000671 W DE 2010000671W WO 2010149130 A2 WO2010149130 A2 WO 2010149130A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- cover
- bearing
- clutches
- double clutch
- Prior art date
Links
Classifications
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/06—Ball or roller bearings
- F16C23/08—Ball or roller bearings self-adjusting
-
- 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
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/43—Clutches, e.g. disengaging bearing
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
Definitions
- the present invention relates to a dual clutch with two clutches K1 and K2, via the input shafts of a dual-clutch transmission with an output shaft of a drive unit are each connectable and a method for assembling such a double clutch.
- the transferable via a clutch torques depend on the operating forces with which the pressure plate of the clutch is pressed against the counter-pressure plate. At high torque to be transmitted and correspondingly high operating forces required are required. For example, in truck applications up to 3,300 - 3,500 Nm of torque are to be transmitted. However, disengagement forces of up to 12,400 - 15,000 N are necessary to transmit these moments.
- a dual clutch with two clutches via the input shafts of a dual-clutch transmission with an output shaft of a drive unit are each connectable, and with an actuator, the via eir> arranged on a clutch cover of the clutches cover bearing is supported and wherein a connection of the cover bearing in the clutch cover has a radial clearance and means for generating a radial biasing force is provided so that the cover bearing on the radial biasing force in conjunction with the radial clearance is centered.
- This object is achieved by a method for assembling a double clutch, wherein a preassembly assembly consisting of two clutches, connected via the common central plate and from the cover fixed arranged actuator is assembled, wherein a one-piece or multi-piece flywheel is connected to a drive shaft of a drive unit, and wherein the central plate is connected as part of this Vormontagebauuite about centering with the one-piece or multi-part flywheel.
- FIG. 1 shows a half section of an embodiment of the present double clutch with two pressed in the ground state open couplings and a cover-fixed double CPCA, the drive-side clutch K1 closed and the transmission-side clutch K2 are open,
- FIG. 2 shows an illustration of the force flow of the actuating force closed within the clutch unit when the drive-side clutch K1 is actuated, in the state according to FIG. 1
- FIG. 3 shows a half section of the exemplary embodiment of the present double clutch with two pressed in the ground state open couplings and a cover fixed double CPCA, wherein the drive-side clutch K1 open and the transmission-side clutch K2 are closed,
- FIG. 4 is an illustration of the closed in the coupling unit power flow of the actuating force upon actuation of the transmission-side clutch K2, in the state shown in FIG. 3,
- Fig. 5 shows a half section through another embodiment of the present double clutch with Diszentrierfunktion for the cover bearing and
- 6a is a detailed view of the cover bearing with Organiczentrierfunktion in the installed state of the double clutch of FIG. 5,
- Fig. 6b is an illustration of the installation situation of the cover bearing without Aerozentrierfunktion in the embodiment of FIG. 1 and Fig. 3 and
- Fig. 7 is an illustration of the dual clutch according to Fig. 1, 3 or 5 in the assembled state with pre-assembly and bolted to the coupling drive plate before introducing the centering.
- the present exemplary embodiments of the double clutch can be used in particular for vehicles with a compressed air system, that is to say, for example, for trucks.
- Fig. 1 shows schematically the structure of a double clutch with pneumatically actuated central release unit for both clutches (K1: drive-side clutch and K2: transmission-side clutch), which is used in vehicles with compressed air systems.
- the present dual clutch is arranged in the drive train of a vehicle between a drive (such as internal combustion engine) and a dual-clutch transmission, wherein between the drive and dual clutch further a torsional vibration damper element, such as a dual-mass flywheel, can be arranged (but not necessarily).
- a drive such as internal combustion engine
- a dual-clutch transmission wherein between the drive and dual clutch further a torsional vibration damper element, such as a dual-mass flywheel, can be arranged (but not necessarily).
- the dual-clutch assembly 1 comprises the drive-side clutch K1 and the transmission-side clutch K2, the designation "drive-side” and “gear-side” of the arrangements of the clutches K1 and K2 on opposite sides of a central plate 10 is owed, as will be further described below.
- This central plate 10 is in this case fastened to a flywheel (also referred to as "drive plate") 11 via centering screws 51 shown in FIG. 7, this flywheel 11 being connected via screw connections 12 to a crankshaft (not shown in detail in FIG. 1) of an internal combustion engine Radially outside a starter ring gear 13 is arranged on the flywheel 11.
- a flywheel also referred to as "drive plate”
- the drive-side partial clutch K1 also includes a pressure plate 21, which is connected via the leaf spring assemblies 52 shown in FIG. 3 to the central plate 10, whereby the pressure plate 21 rotationally fixed in the circumferential direction, but axially displaceable relative to the central plate 10. Between the pressure plate 21 and the central plate 10, a friction lining of a drive-side clutch disc 20 is arranged, wherein the drive-side clutch disc 20 may have a torsional vibration damper.
- the transmission-side clutch K2 comprises a pressure plate 31, which is connected via leaf spring packets 53 with the central plate 10 so that it is rotationally fixed in the circumferential direction, but axially displaceable relative to the central plate 10. Between the pressure plate 31 and the central plate 10, a friction lining of a clutch disc 30 of the clutch K2 is arranged.
- the clutch disc 20 of the drive-side clutch K1 is connected via a toothing with a not shown in FIG. 1 formed as a solid shaft transmission input shaft of a subsequent dual-clutch transmission.
- the transmission-side clutch disc 30 is connected via a toothing with a second transmission input shaft of the following dual-clutch transmission designed as a hollow shaft.
- the double clutch 1 further comprises a tie rod 22, which is connected via screw connections 23, which consist of spacers 23a and screws 23b, with the pressure plate 21 of the drive-side clutch K1.
- the transmission-side clutch K2 comprises a clutch cover 32, which is fastened to the central plate 10 via further screw connections 33 consisting of spacers and screws (corresponding to the connections 23 described above).
- the clutch cover 32 of the transmission-side clutch K2 is produced here in a stamping embossing process and comprises in an outer region two first bending radii 34a, 34b, so that the clutch cover 32 has a "pot-like" outer region. Within this pot-like area, a first support ring 35 is arranged, which forms an outer support for the lever spring 36.
- the lever spring 36 contacts an engagement bearing 41, which is axially displaceable via an inner piston 42, wherein the inner piston together with an inner cylinder 43, a bottom plate 44 and a guide sleeve 46, a pressure chamber 45 of the actuating device of the transmission-side clutch K2 limited.
- the inner piston 42 is axially displaceable on the guide sleeve 46, wherein the inner piston is sealed by sealing elements against the inner cylinder 43 and against the guide sleeve.
- the tie rod 22 of the drive-side clutch K1 has (comparable to the clutch cover of the clutch K2) two deformed radii, so that the radially outer region of the tie rod 22 also receives a cup-like design.
- a second support ring 24 is arranged, against which a radial outer region of the lever spring 25 abuts.
- the lever spring 25 is held on rivets serving as a bearing (which are also referred to as "hammer head rivets"). th, so that the lever spring 25 can pivot about this Auflagerung 26.
- the hammer head rivets are hereby supported on the clutch cover 32.
- the outer piston 48 defines together with the outer cylinder 49, the bottom plate 44 and the inner cylinder 43, a further pressure chamber 50 which is pressurized from the outside.
- the outer piston 48 is mounted axially displaceable on the cylinder 43, wherein the pressure chamber 50 is sealed by seals.
- the outer piston 48 forms together with the outer cylinder 49, the bottom plate 44 and the cylinder 43, the second actuator of the actuator 40, wherein displaced by displacement of the outer piston 48, the actuating bearing 47 axially and accordingly pivots the lever spring 25 to the Auflagerung 26 around becomes. Due to this pivoting about the support 26 of the tie rod 22 is displaced axially, whereby the pressure plate 21 of the clutch K1 is displaced.
- Both clutches K1 and K2 are open in the ground state.
- the pressure plates 21 and 31 are spaced from the central plate 10 by the respective leaf spring assemblies (52, 53) so that the clutch plates 20 and 30 can rotate freely.
- the pressure plates 21 and 31 are displaced in the direction of the central plate 10 and clamped at a corresponding pressure level, the pressure plates 20 and 30, whereby torque from the central plate 10 in the respective Transmission input shafts can be introduced.
- the clutch cover 32 of the clutch K2 has in a radially inner region two further radii 34c and 34d, so that in comparison to the pot-like formation of the radially outer region an elevated radially inner region is formed, in the present case no closed raised inner region formed, but single bent Tabs 35 are produced via a punching / embossing process, which are arranged along a circumference of a central opening in the clutch cover 32. These tabs 35 are connected via rivet connections (alternatively: screwing, caulking, welding or other types of connection) with a support member 36.
- the support element 36 is supported via the clutch cover 32 and the screw connections 33 on the central plate 10 and via the centering screws 51 on the drive plate 11 and correspondingly on the crankshaft.
- the support element 36 comprises in a radially inner region a hub region which receives a bearing outer ring of a cover bearing 37.
- the bearing outer ring of the cover bearing 37 in the hub region of the support element 36 according to the embodiment of FIG. 1 and FIG. 3 is fixedly arranged on the recess 38 a and the locking ring 38 b.
- the bearing inner ring of the cover bearing 37 is connected to the guide sleeve 46 of the actuating direction 40 via a sleeve 39.
- the cover bearing 37 accordingly forms a fixed bearing, which supports the actuator 40. Therefore, the actuator 40 is fully supported on the crankshaft.
- Fig. 2 the power flow is shown upon actuation of the clutch K1.
- a pressure P2 is applied to the pressure chamber 50.
- the resulting force flows through the outer piston 48, the engagement bearing 47, the lever spring 25, the tie rod 22, the screw 23, the pressure plate 21, the friction region of the clutch disc 20, the central plate 10, the screw 33, the clutch cover 32, the support member 36, the cover bearing 47 and the guide sleeve 46 in the bottom plate 44.
- the starting point and end point of the power flow the pressure chamber 50 of the actuator of the drive-side clutch K1.
- the power flow is closed within the dual clutch, whereby a force effect on actuation of the clutch K1 can be avoided on the crankshaft bearing.
- Fig. 3 the dual clutch according to Fig. 1 and 2 is shown in another operating state in which the drive-side clutch K1 open and the transmission-side clutch K2 are closed, and corresponding to the actuating device of the clutch K2 an actuating pressure P1 is present, whereas no actuating pressure is applied to the actuating device of the clutch K1.
- FIG. 4 the force flow for the double clutch in the operating state according to FIG. 3 is illustrated by the solid thick line upon actuation of the actuating device of the clutch K2, which occurs when the pressure P1 is applied by displacing the inner piston 42 along the guide sleeve 46.
- the power flow flows in accordance with the inner piston 42 via the actuating bearing 41, the lever spring 36, the pressure plate 31, the friction region of the clutch plate 30, the central plate 10, the screw 23, the clutch cover 32, the support member 36 and the actuating bearing in the guide sleeve 46, which in turn is connected to the bottom plate.
- the starting point and end point of the force flow is the pressure chamber of the first actuation, so that the force flow of the actuation force is closed within the dual clutch, whereby no force is exerted on the crankshaft and thus on the crankshaft bearing.
- a further double clutch 2 is indicated, which largely corresponds to the double clutch 1. Accordingly, reference is made in full to the foregoing. In addition, reference is made to the storage of the cover bearing 37.
- a radial clearance 100 is provided in conjunction with a spring element 101. Due to the combination of the radial clearance 100 with the radially acting spring 101 results in an additional self-centering. This allows a radial compensation possibility that may possibly occur due to imbalance of the double clutch, different friction on the lever spring tongues, or by tolerance compensation. Accordingly, the axis of the dual CPCA may shift relative to the axis of the dual clutch module and self-centering may occur.
- FIG. 6A this self-centering device is shown enlarged again and compared over Fig. 6B with the formation of the storage of FIG. 1 and 3.
- the above exemplary embodiments accordingly show a double clutch with cover-fixed double CPCA in conjunction with two compressed Normally-Open clutches.
- both couplings with lever spring alternatively, if necessary, also plate springs conceivable
- the cylinders of the actuators of the actuator 40 and the engagement bearing (actuator bearing) for depressed couplings designed.
- the double-CPCA is fixed to the fixed cover of the coupling K2, for example riveted, screwed or welded. Due to the cover fixed bearing the double CPCA is relative to the double clutch, so that an air supply is possible.
- the cover bearing is axially fixed so that small tolerances come together, but in particular no axial play.
- a double-clutch module with an integrated cover-fixed double CPCA, whereby the actuating forces on the crankshaft are reduced to zero, since the power flow for both clutches Doppelkupplungsmo- Dulintem are closed.
- the cover-fixed bearing between clutch disc of the clutch K2 and lever spring of the clutch K2.
- the cover bearing is in this case connected to the cover of the coupling K2, on tabs which pass through windows which are formed in the lever spring. This arrangement allows the use of a small bearing (cost savings, low slip torque, better life).
- the cover-resistant bearing can be configured with a self-centering.
- FIG. 7 A method for assembling the double clutch of the type described above is shown in Fig. 7, wherein in a first step, a preassembled assembly consisting of two clutches K1 and K2, connected via the common central plate 10, and assembled from the cover fixedly arranged actuator, and the one-piece or multi-part flywheel (eg, a dual mass flywheel) is connected to a drive shaft of a drive unit, and wherein in a second step, the central plate 10 is connected as part of this pre-assembly via centering screws 51 with the one-piece or multi-part flywheel.
- the preassembly assembly Prior to connecting the preassembly assembly to the flywheel, the preassembly assembly may be connected to a transmission by connecting the transmission input shafts of the transmission to the clutch disks. It therefore results in a very simple mounting option for the dual clutch, in particular because the mounting to the engine from the side of the transmission is possible.
- the above description also teaches, inter alia, a double clutch with two compressed and ground-open clutches and with a double-prime cover double (CPCA) with hydraulic or pneumatic actuation for vehicles with dual-clutch transmissions created to allow a load circuit in which - due to the compound of two compressed, open in the ground state coupling with a cover-resistant double CPCA - the actuating force is released internally in the coupling module.
- CPCA double-prime cover double
- the double clutch could also be formed with two closed couplings and cover fixed central release. Furthermore, the dual clutch could be formed with a depressed and a pulled clutch in conjunction with a cover-resistant Gottitzer.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112010002723T DE112010002723A5 (en) | 2009-06-26 | 2010-06-14 | DOUBLE COUPLING |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009030822.9 | 2009-06-26 | ||
DE102009030822 | 2009-06-26 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2010149130A2 true WO2010149130A2 (en) | 2010-12-29 |
WO2010149130A3 WO2010149130A3 (en) | 2011-04-14 |
Family
ID=42768077
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2010/000671 WO2010149130A2 (en) | 2009-06-26 | 2010-06-14 | Dual clutch |
Country Status (2)
Country | Link |
---|---|
DE (2) | DE102010023716A1 (en) |
WO (1) | WO2010149130A2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN110049890A (en) * | 2016-12-07 | 2019-07-23 | 舍弗勒技术股份两合公司 | There are four the operating assembly of adjustment mechanism, clutch and braking systems, hybrid power module and driving system for tool |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2013023638A1 (en) | 2011-08-17 | 2013-02-21 | Schaeffler Technologies AG & Co. KG | Actuating device for a clutch |
DE102011056832A1 (en) * | 2011-12-21 | 2013-06-27 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Powertrain for sports vehicle, has gear wheels meshed with casing, where edges of teeth of external teeth systems of wheels are spherically formed such that respective tooth is tapered at opposite front ends up to specified thickness |
EP2886898B1 (en) * | 2013-12-17 | 2017-08-23 | Schaeffler Technologies AG & Co. KG | Coupling with fixed cover shifter |
DE102017111757A1 (en) * | 2017-05-30 | 2018-12-06 | Schaeffler Technologies AG & Co. KG | Rotation assembly and torque transfer device |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0185176A1 (en) | 1984-12-20 | 1986-06-25 | Dr.Ing.h.c. F. Porsche Aktiengesellschaft | Double clutch for a motor vehicle transmission |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2881490B1 (en) * | 2005-01-31 | 2007-03-02 | Valeo Embrayages | DEVICE FOR MOUNTING A BEARING ON A TRANSMISSION ELEMENT. |
EP1808612B1 (en) * | 2006-01-11 | 2012-03-28 | Schaeffler Technologies AG & Co. KG | Release device for a vehicle clutch |
DE102008004150A1 (en) * | 2007-01-31 | 2008-08-07 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torque transfer device |
-
2010
- 2010-06-14 DE DE102010023716A patent/DE102010023716A1/en not_active Withdrawn
- 2010-06-14 WO PCT/DE2010/000671 patent/WO2010149130A2/en active Application Filing
- 2010-06-14 DE DE112010002723T patent/DE112010002723A5/en not_active Withdrawn
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0185176A1 (en) | 1984-12-20 | 1986-06-25 | Dr.Ing.h.c. F. Porsche Aktiengesellschaft | Double clutch for a motor vehicle transmission |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN110049890A (en) * | 2016-12-07 | 2019-07-23 | 舍弗勒技术股份两合公司 | There are four the operating assembly of adjustment mechanism, clutch and braking systems, hybrid power module and driving system for tool |
CN110049890B (en) * | 2016-12-07 | 2022-05-31 | 舍弗勒技术股份两合公司 | Operating assembly with four adjusting mechanisms, clutch and brake system, hybrid module and drive train |
Also Published As
Publication number | Publication date |
---|---|
WO2010149130A3 (en) | 2011-04-14 |
DE102010023716A1 (en) | 2010-12-30 |
DE112010002723A5 (en) | 2012-08-23 |
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