WO2010006576A1 - Dry-running clutch - Google Patents
Dry-running clutch Download PDFInfo
- Publication number
- WO2010006576A1 WO2010006576A1 PCT/DE2009/000899 DE2009000899W WO2010006576A1 WO 2010006576 A1 WO2010006576 A1 WO 2010006576A1 DE 2009000899 W DE2009000899 W DE 2009000899W WO 2010006576 A1 WO2010006576 A1 WO 2010006576A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- dry
- clutch according
- actuating
- cover
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/04—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube
- F16D25/042—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube the elastic actuating member rotating with the clutch
- F16D25/044—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube the elastic actuating member rotating with the clutch and causing purely axial movement
-
- 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
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0212—Details of pistons for master or slave cylinders especially adapted for fluid control
Definitions
- the present invention relates to a dry clutch, in particular a dry dual clutch with two friction clutches with a common clutch housing.
- Double clutches are used in vehicles to allow a load circuit. Especially in applications where a high torque must be transmitted, high actuation forces (disengaging forces or engagement forces) occur. For example, in applications in trucks torques in the order of 3,300 Nm to 3,500 Nm to be transmitted. In order to transmit such torques actuation forces in the order of 12,400 N up to 15,000 N on.
- the actuating forces of the clutch must be supported either via the crankshaft bearing or via a gearbox bearing, wherein depending on the respective direction of the actuating forces twice the actuation force must be supported.
- the aim is therefore to minimize the actuation forces in order to avoid a strong design of the bearings and the associated changes in the housing.
- a dry clutch with a device for pneumatic or hydraulic actuation of the clutch with an actuating cylinder and a displaceable due to the action of the actuating cylinder transmission element (hereinafter also referred to as "piston"), wherein actuating cylinder and transmission element (“piston”) with the parts intended for torque transmission of the dry clutch are rotatably connected, and wherein the actuating cylinder can be supplied via a rotary inlet with pressure medium.
- Pneumatic actuation is preferred because at least small amounts of leakage of compressed air can be tolerated.
- the actuating cylinder can be rotatably connected to a clutch cover of the dry clutch.
- a pressure medium supply to the actuating cylinder via the clutch cover of the dry clutch take place.
- the clutch cover be constructed in several parts, with a pressure medium channel is created in the clutch cover due to the multi-part construction.
- the Kupplungsdeckei of two levels preferably via a screw, clamped sheets, between which by inserting at least one intermediate element of the pressure medium channel is integrated.
- the clutch cover of two non-planar in particular via a screw, clamped together sheets, between which due to corresponding non-planar structures of the clamped sheets of pressure medium channel is integrated.
- the rotary inlet can have an inner part connected to a pressure medium supply and not rotating with the coupling, and an outer part connected to the clutch cover, wherein the outer part is mounted on the inner part via a fixed bearing and a movable bearing.
- the actuating cylinder may be formed as a Membranzyiinder, wherein a pressure chamber of the actuating cylinder between the diaphragm and clutch cover is formed, so that a friction hysteresis minimized and thereby a pressure control is possible.
- the membrane may be formed in two parts, in particular divided into a radially inner and a radially outer partial membrane.
- the actuating cylinder may be formed as a rolling diaphragm cylinder in which the membrane roll in pressure medium supply to an inner wall of the rolling diaphragm cylinder formed by a tubular member and an outer wall of the rolling diaphragm cylinder formed by a cylindrical member. Both the tubular component and the cylindrical component are preferably rotationally symmetrical. In this case, the tubular member and the cylindrical member may be connected to the clutch cover. The tubular member may also form the rotating with the clutch outer part of the rotary inlet.
- the transmission element is composed of at least two individual molded sheets for increasing the rigidity of the transmission element.
- the dry clutch is designed as a dry double clutch, the means for pneumatic or hydraulic actuation of the dry dual clutch a first pneumatically or hydraulically actuated actuating cylinder and a relative to the actuating cylinder displaceable first transmission element (hereinafter also referred to as the first "piston”) Actuating a first friction clutch and a second pneumatically or hydraulically actuatable actuating cylinder and a second transmission element (hereinafter also referred to as a second "piston”) which is displaceable relative to the actuating cylinder for actuating a second friction clutch, wherein actuating cylinders and transmission elements (“pistons”) with the parts provided for torque transmission rotatably connected and can be supplied via a rotary inlet with pressure medium.
- actuating cylinders and transmission elements (pistons) with the parts provided for torque transmission rotatably connected and can be supplied via a rotary inlet with pressure medium.
- both actuating cylinder rotatably connected to the clutch cover of the dry dual clutch and arranged on opposite sides of this clutch cover. Furthermore, a pressure medium supply to both actuation cylinders via the clutch cover of the dry double clutch can be done.
- the clutch cover of two in particular via a screw, clamped together sheets, between which supply channels are formed, via which the actuating cylinder can be supplied with pressure medium.
- Both actuating cylinders may be formed as a diaphragm cylinder, which are arranged on opposite sides of the clutch cover of the dry double clutch, wherein the pressure chambers of the actuating cylinder between the respective membrane and this clutch cover are formed so that a friction hysteresis minimized and thereby a pressure control are possible.
- the membrane of both actuating cylinders may be formed in two parts.
- both actuation cylinders can be formed as rolling diaphragm cylinders, in which the membrane in compressed air supply to inner walls of the rolling diaphragm cylinder formed by a common tubular component and on formed on opposite sides of the Kupplungsdeckeis the dry dual clutch separate cylindrical components outer walls of the rolling diaphragm cylinder roll.
- the transmission elements can in each case have a multi-part construction and have a first component directed in the direction of the respective diaphragm and a second component in communication with the pressure plate of the respective partial clutch, wherein an inner gap of the diaphragm between the respective first component and the common tubular component and an outer roll gap of the membrane between the respective first component and the respective separate cylindrical components are formed.
- a two-channel rotary inlet can be provided, the clutch cover-side outlets are arranged in the plane of the clutch cover, so that pressure medium can be directed from there into the respective supply channels in the clutch cover.
- the common tubular member may be connected to the clutch cover of the transmission-side part clutch of the dry dual clutch and form a rotating with the clutch and the actuating cylinders common outer part of the rotary inlet.
- the rotary inlet can have a co-rotating with the clutch outer part and a co-rotating with the clutch inner part, wherein the outer part is mounted on the inner part via a fixed bearing and a floating bearing.
- separate channels can be created as supply channels to the actuating cylinders via sealing collars.
- Interiors of the sealing collars can be filled with grease for lubrication of the sealing point.
- the sealing collars can be pressed axially with sleeves, shims and the bearings on the outer part of the rotary union and connected in rotation with the outer part.
- the sealing collars can be arranged between the fixed bearing and floating bearing, so that the sealing collars are protected against external influences.
- both partial clutches of the dry double clutch are designed as "normally open", wherein a force for releasing the partial clutches is applied by leaf springs which are arranged between pressure plates of the partial clutches and a central plate.
- a maximum Lsellweg the partial clutches may be limited by stops in the actuator cylinder housing.
- the device for the pneumatic or hydraulic actuation of the dry double clutch can be screwed on the clutch cover to the central plate.
- the inner part of the rotary input can be supported on one of the transmission input shafts.
- the central plate of the coupling can be connected to the drive via a gimbal, which is flexible and torsionally stiff.
- the present invention further teaches a method for assembling a dry clutch according to one of the preceding embodiments, wherein from the clutch plates, the pressure plates, the central plate and the clutch cover of the transmission-side part clutch on which the device for pneumatic or hydraulic actuation of the dry dual clutch is arranged Pre-assembly is formed, the coupling Thereafter, the discs are radially centered and the clutch discs are then fixed in this centered position by a preload generated by means of pressure medium.
- the pre-assembly connected to the transmission may thereafter be connected by screw connections to a flywheel or a torsional vibration damper or a flex-plate which has been previously arranged on a drive shaft.
- 1 is a schematic representation of a dry dual clutch with pneumatic direct actuation as half-section, wherein the section shows the pressure channel for the transmission-side part clutch K2,
- FIG. 2 shows a further schematic illustration of the dry dual clutch according to FIG. 1, wherein the section shows the pressure channel for the engine-side partial clutch K1,
- Fig. 3 shows a portion of the dry dual clutch of FIG. 1 and 2, with a
- FIG. 4 is a schematic representation of the preassembly assembly comprising the clutch plates, pressure plates, central plate and clutch cover of the transmission-side part clutch, wherein the clutch cover the entire device for pneumatic or hydraulic actuation of the dry dual clutch is fixed,
- Fig. 5 shows another embodiment of the dry dual clutch with pneumatic or hydraulic direct actuation, wherein the inner part of the rotary inlet is mounted on the outer transmission input shaft and
- Fig. 6 is a schematic representation of the preassembly assembly of FIG. 4 at
- FIG. 1 shows an embodiment of a dry dual clutch 1 with two of a (not shown in detail) drive unit driven friction clutches K1 and K2 with a common clutch housing and a fixedly connected to this clutch housing central plate 3 with two contact surfaces and two each one of the contact surfaces facing axially displaceable printing plates 4, 5.
- the present dual clutch is arranged in a drive train of a vehicle between the drive and a dual-clutch transmission, wherein the dual-clutch transmission comprises the input shafts 8, 9, which are arranged coaxially and nested in the present case.
- the engine-side partial clutch K1 and the transmission-side partial clutch K2 are both closed in the normal state ("normally closed"), wherein the pneumatic or hydraulic actuator is provided to press the respective pressure plates 4, 5 of the partial clutches to the central plate 3 for power transmission between the drive and transmission input shafts. 8 , 9 via the clutch disks 6, 7.
- the central plate 3 is connected to a flywheel 2 via screw connections (not shown here).
- a pilot bearing 10 is arranged on the flywheel 2.
- a torsional vibration damper DMF
- a flex-plate could be used.
- the clutch cover 11 is screwed via a plurality of screw connection 12, 13 to the central plate.
- Each of the screw connection comprises a spacer 12 and a screw 13th
- the clutch cover 11 is fixedly connected to the actuator for the dry dual clutch, in particular, compressed air is available as actuation energy.
- the actuating device comprises two rolling diaphragm cylinders which are arranged on opposite sides of the clutch cover 11.
- the rolling diaphragm cylinder arranged from the clutch cover in the direction of the central plate is in operative connection with the transmission-side partial clutch K2.
- rolling diaphragm cylinder is in operative connection with the engine-side part clutch K1.
- Both rolling diaphragm cylinders comprise a rolling diaphragm 21, 22, which together with the clutch cover 11 form a pressure chamber for the respective cylinder.
- the clutch cover 11 is presently formed from two flat sheets 11A and 11C, between which a plurality of intermediate elements 11B are arranged.
- the sheets and intermediate elements are clamped together via the screw 23 and 24. Due to the sheets 11 A, 11 C and the intermediate elements 11 B resulting supply channels for the pressure medium.
- These supply channels supply the pressure chambers with pressure medium (in particular compressed air).
- pressure medium in particular compressed air.
- Fig. 1 the supply channel for the pressure chamber of the rolling diaphragm cylinder of the transmission-side part clutch and in Fig. 3, the supply channel for the rolling diaphragm cylinder of the engine-side part clutch shown.
- the supply channels are supplied via a rotary inlet, which has a connected to a compressed air connection and not rotating with the clutch inner part 15 and a co-rotating with the clutch outer part 14.
- the inner part 15 comprises supply channels with which a pressure medium volume flow is conducted via the supply channels formed in the rotary inlet to the outer part 14 and via the outer part 14 into the supply channels in the clutch cover.
- a fixed bearing 16 and a floating bearing 17 are arranged between inner part 15 and outer part 14. Between the fixed bearing 16 and floating bearing 17 are sleeves 19, 20, spacers 21 and sealing collars 18A, 18B, 18C arranged, which form the feed channels within the rotary inlet.
- the tubular outer part 14 of the rotary inlet also forms an inner wall of the rolling diaphragm cylinder against which the rolling diaphragm rests.
- a radially outer wall is formed by cylindrical components 33, which are arranged on opposite sides of the clutch cover of the partial clutch K2.
- the pistons of the rolling diaphragm cylinders are constituted by the transmission members 26A, 26B and 25A and 25B. These transmission elements each have an inner part 26B, 25B formed in the direction of the respective rolling diaphragm, which together with the outer roller part of the rotary inlet and the cylindrical components 33 each form a rolling gap for the rolling diaphragm.
- the respective outer part 26A, 25A is correspondingly in operative connection with the pressure plates 4, 5 of the associated partial clutches. In this case, the outer part 26A is directly in operative connection with the pressure plate (that is due to it).
- the outer panel 25A is connected to a tie rod which is connected to the pressure plate 4.
- the present teaching is thus characterized by co-rotating cylinder and co-rotating transmission elements ("piston”), which are supplied via a rotary inlet with pressure medium (in particular compressed air).
- pressure medium in particular compressed air
- compressed air has a density of less than 670 as oil.
- the two rolling diaphragm cylinders in the present case designed as engagement cylinders
- the two rolling diaphragm cylinders also have a low leakage and a low friction hysteresis. Therefore, a simple pressure control is possible.
- the power flow is presently closed without the use of a support bearing.
- the required contact force is generated directly in the cylinders.
- the present teaching accordingly discloses a dry clutch in which it is possible to dispense with a support bearing, which would have to absorb actuating forces, due to the use of co-rotating cylinders and pistons, which are supplied with compressed air and directly generate the contact pressure.
- the compressed air is supplied via a present two-channel rotary induction system.
- Fig. 1 the air supply for the actuation of the partial clutch K2 is shown.
- Fig. 2 the air supply for the actuation of the partial clutch K1 is shown.
- the outlets of both supply channels in the rotary inlet are combined at the level of the clutch cover to be passed from there into the two separate supply channels for the cylinder.
- the individual channels inside the rotary union are sealed by means of sealing collars, the interior of which is filled with grease to lubricate the sealing point.
- the gaskets are axially compressed with sleeves, shims and bearings and rotate with the clutch cover and corresponding to the complete actuator and the remaining parts of the clutch at engine speed.
- the decoupling of the stationary inner part to the co-rotating outer part takes place with the fixed bearing and the floating bearing.
- the bearings also take over the axial guidance of the outer part and are grease lubricated. They also protect the sealing sleeves against external influences, such.
- the rolling diaphragm forms the pressure chambers and are sealed via the system on the clutch cover.
- the inner and outer roller gap of the rolling diaphragm is supported in each case radially with the cylindrical component or the outer part of the rotary inlet against the applied internal pressure. In the present case, the rolling membranes are divided into two parts for assembly reasons.
- the transmission device (the piston) of the transmission-side part of the clutch is shown in the extended state, ie upon application of a compressive force in which the getriebesei- term clutch is closed.
- the piston is also shown in its retracted state, which is generated via the action of the leaf springs in conjunction with a pressure reduction in the pressure chamber (see the dashed lines in Fig. 3). Limiting the return stroke, so the Lsymmetricweg, on the cylindrical components 33, which form the stop for the return stroke.
- the piston stroke may be 8.5 mm in total.
- the piston stroke can be divided into 5 mm wear reserve + 0.8 mm air gap + 0.8 mm pad suspension + 1, 0 mm deflection + 0.9 tolerances.
- the rolling path of the rolling diaphragm on the piston is reduced when actuated to half of the piston stroke.
- the couplings are designed as "normally open”.
- the force to ventilate the leaf springs which are arranged between pressure plates and central plate.
- the complete actuator is screwed to the central plate.
- the movable pressure plates are riveted here by leaf springs.
- the clutch discs are inserted between the central plate and pressure plates. Consequently, a complete pre-assembly of central plate, pressure plates, clutch plates and actuator can be formed. This pre-assembly can be taken on the central plate and z. B. can be lifted into a truck, resulting in a very simple way of mounting.
- the clutch discs can be radially centered over the crankshaft before installation with a centering mandrel. This centered position can be fixed by applying an air pressure, z. B. by means of a simple check valve which holds the pressure in the pressure chambers.
- a pressure line is not needed and would only interfere with the application of the gearbox to the engine.
- the check valve can be removed after the gearbox assembly.
- the transmission elements (“piston") are formed to increase their rigidity as set out of two individual sheets, but could also be integrally formed.
- the central inner support of the actuator is realized via the clutch cover, wherein the plates of the clutch cover represent quasi the rear wall of the respective actuating cylinder, and wherein the plates are clamped together via a screw and the air duct is integrated in the sheets.
- the pre-assembly is shown in FIG. 4.
- Fig. 5 an arrangement is shown in which the dual clutch is mounted with the rotary input via two bearings on the outer, designed as a hollow shaft transmission input shaft.
- the clutch is also connected to the flywheel via a gimbal, which is flexible and torsionally stiff.
- Advantage of this variant is that not the total weight of the double clutch on the crankshaft loads.
- Fig. 6 is a schematic representation of the pre-assembly of FIG. 4 is shown when mounted on a flywheel, which is connected to a drive shaft.
- the complete pre-assembly can be screwed directly to the flywheel (or alternatively: on a Torsionsschwingungs- damper) via several screws without, as in accordance with the embodiment of FIG. 5 to arrange a gimbal between them.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112009001564T DE112009001564A5 (en) | 2008-07-14 | 2009-06-29 | dry clutch |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008033033 | 2008-07-14 | ||
DE102008033033.7 | 2008-07-14 | ||
DE102009011000.3 | 2009-03-02 | ||
DE102009011000 | 2009-03-02 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2010006576A1 true WO2010006576A1 (en) | 2010-01-21 |
Family
ID=41051734
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2009/000899 WO2010006576A1 (en) | 2008-07-14 | 2009-06-29 | Dry-running clutch |
Country Status (2)
Country | Link |
---|---|
DE (2) | DE102009030977A1 (en) |
WO (1) | WO2010006576A1 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2310707A1 (en) * | 2008-07-14 | 2011-04-20 | Schaeffler Technologies AG & Co. KG | Dual clutch |
WO2011076170A1 (en) * | 2009-12-22 | 2011-06-30 | Schaeffler Technologies Gmbh & Co. Kg | Method for adjusting a clearance of clutch devices |
WO2013085604A1 (en) * | 2011-12-08 | 2013-06-13 | Econugenics, Inc. | Reduction of galectin-3 levels by plasmapheresis |
CN104847807A (en) * | 2014-07-08 | 2015-08-19 | 北汽福田汽车股份有限公司 | Clutch device |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017211274A1 (en) * | 2017-07-03 | 2019-01-03 | Zf Friedrichshafen Ag | Powertrain for a motor vehicle |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2636585A (en) * | 1946-08-30 | 1953-04-28 | William T Livermore | Automatic fluid pressure transmission |
US3584717A (en) * | 1969-07-31 | 1971-06-15 | Montalvo And Co Inc | Mounting for brake or clutch |
DE19750249A1 (en) * | 1997-11-13 | 1999-05-20 | Mannesmann Sachs Ag | Pneumatically operated commercial vehicle clutch |
-
2009
- 2009-06-29 DE DE102009030977A patent/DE102009030977A1/en not_active Withdrawn
- 2009-06-29 WO PCT/DE2009/000899 patent/WO2010006576A1/en active Application Filing
- 2009-06-29 DE DE112009001564T patent/DE112009001564A5/en not_active Withdrawn
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2636585A (en) * | 1946-08-30 | 1953-04-28 | William T Livermore | Automatic fluid pressure transmission |
US3584717A (en) * | 1969-07-31 | 1971-06-15 | Montalvo And Co Inc | Mounting for brake or clutch |
DE19750249A1 (en) * | 1997-11-13 | 1999-05-20 | Mannesmann Sachs Ag | Pneumatically operated commercial vehicle clutch |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2310707A1 (en) * | 2008-07-14 | 2011-04-20 | Schaeffler Technologies AG & Co. KG | Dual clutch |
EP2310707B1 (en) * | 2008-07-14 | 2012-12-05 | Schaeffler Technologies AG & Co. KG | Dual clutch |
WO2011076170A1 (en) * | 2009-12-22 | 2011-06-30 | Schaeffler Technologies Gmbh & Co. Kg | Method for adjusting a clearance of clutch devices |
WO2013085604A1 (en) * | 2011-12-08 | 2013-06-13 | Econugenics, Inc. | Reduction of galectin-3 levels by plasmapheresis |
AU2012348311B2 (en) * | 2011-12-08 | 2014-06-12 | Eliaz Therapeutics, Inc. | Reduction of galectin-3 levels by plasmapheresis |
CN104847807A (en) * | 2014-07-08 | 2015-08-19 | 北汽福田汽车股份有限公司 | Clutch device |
CN104847807B (en) * | 2014-07-08 | 2017-09-12 | 北汽福田汽车股份有限公司 | Arrangement of clutch |
Also Published As
Publication number | Publication date |
---|---|
DE102009030977A1 (en) | 2010-03-11 |
DE112009001564A5 (en) | 2011-03-31 |
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