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
  • F16D25/08—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
  • F16D25/083—Actuators therefor

Definitions

• the present invention relates to a device for actuating a clutch, in particular a clutch in the drive train of a motor vehicle between a drive motor and a transmission.
• Object of the present invention is therefore to provide a Monausgurer, in which the wear load of the seals is reduced.
• a device for actuating a clutch in particular a clutch in the drive train of a motor vehicle between a drive motor and a gearbox, which comprises a pneumatic or hydraulic piston / cylinder assembly which is cantilevered relative to a transmission means operatively connected to a release bearing
• cantilever is meant here that the release bearing operatively connected means can only transmit compressive forces and relative to the release bearing or the release bearing operatively connected means - apart from frictional forces - can transmit no rotational forces and can not transmit tensile forces.
• the pneumatic or hydraulic piston / cylinder arrangement is thus preferably rotatable relative to the transmission means.
• the pneumatic or hydraulic piston / cylinder arrangement preferably abuts against the transmission means when moving in the direction of the transmission means and establishes a positive connection. When the movement is opposite to the direction of the transmission means beyond a relieved position, it loses positive engagement.
• the transmission means is a sliding sleeve, which is mounted with a sliding bearing on a guide sleeve.
• the sliding bearing is preferably a sliding bearing, which has, for example, plastic rings or the like as bearing surfaces.
• a pressure disk is preferably arranged, against which the pneumatic or hydraulic piston / cylinder arrangement presses when pressurized.
• the piston of the pneumatic or hydraulic piston / cylinder assembly is mounted fixed to the housing and the cylinder occurs in its axial movement with the transmission means in operative connection.
• the piston is preferably made substantially of a plastic or a plastic composite material.
• the piston preferably comprises an inner and an outer seal which seal a pressure space enclosed between the piston and the cylinder from the environment.
• the seals are preferably lip seals.
• the device is preferably attached to a differential flange made of a plastic or a plastic composite material on a clutch bell or a gear or motor housing.
• the sliding sleeve is preferably supported with a biasing spring on a housing-fixed spring counter bearing, wherein the biasing spring transmits a torque between the sliding sleeve and spring counter bearing and thus has the function of a rotation.
• the piston / cylinder arrangement preferably comprises means for limiting the axial play relative to the sliding sleeve, wherein the means for limiting the axial play is preferably a tongue arranged on the movable cylinder, which surrounds the pressure disk.
• the means for limiting the axial clearance may be a nose arranged on the movable cylinder, which engages in a recess of the sliding sleeve.
• the recess may preferably be formed as a circumferential shoulder.
• an outer sliding surface of the piston / cylinder arrangement is arranged offset in the axial direction with respect to an inner sliding surface of the piston / cylinder arrangement.
• the outer sliding surface relative to the inner sliding surface in the direction of an actuated by the piston / cylinder assembly clutch, which is in particular a dry clutch is arranged offset.
• the outer seal is arranged offset in the direction of the clutch actuated by the piston / cylinder arrangement with respect to the inner seal.
• the biasing spring is preferably disposed between the ring pot and the Gottausscherkolben.
• the ring pot and / or the central release piston comprise a circumferential bulge for receiving the biasing spring.
• the sliding sleeve preferably comprises a nose between the release bearing and the ring pot is arranged.
• the nose serves both the power transmission between release bearing and ring pot and the leadership or rotation of the sliding sleeve.
• the staggered arrangement of the outer relative to the inner sliding surface a reduction of the axial space of the Gottausgurers is achieved.
• the inner region of the central release that is, the region which is formed essentially by the inner sliding surface and the surrounding components, can thus be arranged offset relatively far in the direction of the transmission. This is especially possible if this area is not used by any other modules of the transmission.
• the Monausscher has a modular design that uses a mechanical module and a pneumatic or hydraulic module, which are separated from each other.
• the mechanical module essentially corresponds to known mechanical clutch actuations with release lever. It consists of a sliding sleeve, which carries the release bearing, and a guide sleeve.
• a preload spring which ensures the contact pressure of the release bearing on the disc spring and also includes a rotation, which is necessary so that the radial centering can work on the release bearing.
• the function of a stop ring is integrated into the guide sleeve by a bead.
• the pneumatic module contains the slave cylinder.
• the advantage here is the always centric force application of the slave cylinder on the piston.
• the slave cylinder consists essentially of a housing which carries the two lip seals, and a piston.
• the piston has no fixed connection to the sliding sleeve.
• This floating arrangement has the advantage that all oscillating movements on the release bearing, z. B. because of tongue strike, axial play and deflection of the crankshaft and the like, are disconnected from the seal, as long as the system is depressurized.
• the non-pressurized state is always given when no clutch actuation takes place, which is the case in the majority of the driving operation of a motor vehicle.
• the front piston stop which is only transport safety device, was integrated into the guide sleeve.
• the outer and the piston enclosing Gottitzerzylinder reduces the space requirement.
• the Gottitzerzylinder is preferably made of sheet metal, here are one-piece but also multi-part solutions conceivable.
• For the hydraulic module come next to a housing made of aluminum and cost-effective solutions made of plastic or plastic composite materials such as glass fiber or carbon fiber reinforced plastics in question.
• a lubricant This is preferably applied as a viscous film.
• the lubricant preferably contains a siloxane, wherein the lubricant preferably contains a weight fraction of 55 to 90% of polydimethylsiloxane.
• the lubricant polytetrafluoroethylene (PTFE), wherein the lubricant preferably contains a weight fraction of 5 to 45% of polytetrafluoroethylene. It is preferably provided that the lubricant contains particles of polytetrafluoroethylene having a particle size of 1 to 20 microns.
• the lubricant preferably has a viscosity greater than 1000 mm 2 / s, in particular a viscosity between 10,000 and 100,000 mm 2 / s, and particularly preferably a viscosity of 30,000 mm 2 / s.
• the lubricant preferably has a density greater than 1 g / cm 3 .
• At least one of the seals is made of ethylene-propylene-diene rubber (EPDM) or hydrogenated nitrile rubber (HNBR) with a hardness of 70 to 82 Shore.
• EPDM ethylene-propylene-diene rubber
• HNBR hydrogenated nitrile rubber
• the surfaces of the cylinder (10), to which the lubricant is applied, preferably have a roughness Rz of 1 to 4 .mu.m, wherein the surfaces of the cylinder, to which the lubricant is applied, preferably have a support ratio between 20 and 90%.
• the high viscosity of the lubricant improves the adhesion and thus the adhesion to the surface.
• the lubricant is also a sealing medium due to the high viscosity.
• the lubricant does not dissolve in the water or oil contained in the compressed air.
• the lubricant is also temperature-stable in the operating range from - 40 0 C to over 200 0 C, especially at high operating temperatures, it does not cause the lubricant to resin.
• the lubricant also serves as an assembly aid (mounting medium). In contrast to painting, incomplete wetting of the surface with the lubricant does not lead to any sealing problems or increased wear, since the seal distributes and incorporates the lubricant on the running surface during operation by means of axial and rotational movements. Due to the light-white color of the lubricant, this is in contrast to the application areas, so that an automatic camera inspection during assembly is easily possible.
• Fig. 2 is a section through a second embodiment of a central release according to the invention.
• Fig. 1 shows a section through a first embodiment of a central release 1 according to the invention as a device for actuating a clutch.
• the end position is shown at fully compressed Gottausschreiber 1
• the end position is shown at fully actuated Gottausschreiber 1.
• the Monausschreiber 1 comprises a sliding sleeve 2 as a transmission means, which cooperates with a release bearing 3, which acts on a plate spring 4.
• the sliding sleeve 2 is arranged along a guide sleeve 5 axially displaceable along an axis of rotation R.
• the guide sleeve 5 merges into a substantially radially extending flange 7, on which also a preload spring 6 arranged between guide sleeve 5 and flange 7 is supported.
• a Gottausscherkolben 9 is attached, which forms together with a ring pot 10 as a cylinder piston / cylinder assembly 21 which can be acted upon via a compressed air connection 12 with compressed air.
• the ring pot 10 is cantilevered relative to the sliding sleeve 2, so it is not connected with this form-fitting or frictional connections.
• a flange 19 is arranged, which carries a thrust washer 11.
• the pressure plate 11 projects beyond the sliding sleeve 2 in the axial direction to the outside.
• the ring pot 10 presses with an inner pot 20 against the pressure plate 11.
• This is firmly connected to an outer ring 22 of the release bearing 3 and therefore axial forces (compressive forces) on the release bearing 3 and on this on the Transfer plate spring 4.
• the ring pot 10 can transmit only compressive forces on the pressure plate 11 via the inner pot 20, this corresponds to a transmission of forces in the direction of the arrow D in Fig. 1. In the opposite direction no tensile forces can be transmitted. If the ring pot 10 is therefore moved counter to the direction of the arrow D in FIG.
• the piston / cylinder assembly 21 includes the Monausschreiberkolben 9, which is fixedly connected to the flange 7.
• the central release piston 9 is thus arranged fixed to the housing.
• the ring pot 10, which is mounted so as to be able to fly, is mounted so as to be movable relative to it, that is, it is fixed to the housing neither in the axial direction nor in the circumferential direction or fixed to another part.
• the seal between Monausschreiberkolben 9 and the ring pot 10 relative to the environment is an outer seal 13 and an inner seal 14, which may be, for example, each double lip seals and annular over the entire circumference of Monausschreiberkolben 9 and ring pot 10 are arranged.
• the path of the sliding sleeve 2 is limited in the axial direction of the release bearing 3 by a flange 18.
• the bead has an outer radius which is greater than the inner radius of the sliding sleeve 2.
• the sliding sleeve 2 has disposed in annular grooves on a sliding ring 16.1 and a sliding ring 16.2, which cause a sliding bearing relative to the guide sleeve 5.
• the flange 7 is fastened by means of a differential flange 8 to a clutch bell or transmission housing, not shown.
• the guide sleeve 5 together with integrally formed flange 7 is preferably made of sheet metal, as well as the ring pot 10 is preferably made of sheet metal.
• the central release piston 9 may be made of plastic or a plastic composite material, the same applies to the differential flange 8, which may also be made of a plastic or a plastic composite material. Likewise, however, the differential flange 8 as well as the central release piston can also be made of a metal.
• the sliding sleeve 2 is preferably made of a metal, but may also be made of a plastic or a plastic composite material.
• the pressure disk 11 is preferably a metal disk.
• the ring pot 10 is cantilevered relative to the thrust washer 11, so it is neither positively or frictionally connected with her.
• the ring pot 10 is thus stored on the fly, so it can in the unloaded position of the central release 1, which is the position, in which the pressure chamber 24 is depressurized, are rotated with respect to the pressure plate 11 and the release bearing 3, wherein the contact between the hub 11 and ring pot 10 can be lost at unpressurized pressure chamber 24, so that an annular gap is formed.
• the pneumatic or hydraulic piston / piston / cylinder assembly 21 abuts on a movement in the direction of the transmission means 2 to this and provides a pressure-sensitive positive connection. In a movement opposite to the direction of the transmission means 2 via a relieved position addition, the piston / cylinder assembly 21 loses the positive connection with the sliding sleeve as a transmission means or with the pressure plate 11.
• the unloaded position is reached at unpressurized piston / cylinder assembly 21, thereby creating a Gap between ring pot 10 and thrust washer 11.
• the ring pot 10 can be moved axially relative to the central release piston 9, as well as this can be rotated relative to both the central release piston 9 and the pressure plate 11 in the circumferential direction. In this case, only the frictional forces between the components involved to overcome, in the fully relieved position of the central release 1, thus at approximately unpressurized pressure chamber 24, the connection between the pressure plate 11 and the ring pot 10 is lost, so that here even with a rotation of the Circumferential direction no frictional forces occur and in particular vibrations of the clutch can not be transmitted to the ring pot 10 via the plate spring 4, the release bearing 3 and the pressure plate 11. In this respect, the ring pot 10 and thus also the inner and outer seals 13, 14 are vibration-decoupled from the release bearing 3 in the unloaded position of the central release 1.
• the function of the piston / cylinder assembly 21 is completely separated from the actual power transmission to the release bearing 3.
• the sliding sleeve 2 assumes the function of power transmission to the release bearing 3 and the centering of the entire central release 1 relative to the release bearing 3.
• the piston / Cylinder assembly 21 is solely for the application of the axial force, so does not itself radial guiding functions within the device. This function is taken over by the sliding sleeve 2.
• the ring pot 10 comprises a tongue 25, which extends in the radial direction in the direction of the axis of rotation R and surrounds the pressure disk 11.
• the tongue 25 thus restricts the axial clearance, since the tongue 25 strikes the pressure disk 11 after overcoming an axial clearance X during a movement of the ring pot 10 away from the pressure disk 11.
• a nose 26 which is arranged on the inside of the ring pot 10 so that it engages in a circumferential shoulder 27 and abuts in this way after overcoming an axial clearance on the sliding sleeve 2.
• a circumferential shoulder 27 can here also a recess, e.g. be arranged in the form of an axially extending groove or the like.
• FIG. 2 shows a section through a second exemplary embodiment of a central release device 1 according to the invention.
• the components identical to FIG. 1 are identified identically in FIG. 2.
• the plate spring 4 is fixed with Belleville spring bolts 28 on a clutch cover 29.
• the remaining components of a dry clutch 30 known per se here are not shown in greater detail in FIG.
• the preload spring 6 between the sliding sleeve 2 and the flange 7 of the guide sleeve 5 is arranged.
• the second embodiment of the invention Gottausschreibers the preload spring 6 between the central release piston 9 and the ring pot 10 is arranged.
• Both the Primaausschreiberkolben 9 and the ring pot 10 in the embodiment of FIG. 2 are designed so that they extend as far as possible to the dry clutch 30 in a radially outer region A and in a radially inner region B as far as possible in the direction of not shown Gear extend.
• the radially inner region B is thus arranged as close as possible to the transmission.
• the central release piston 9 comprises an outer cylindrical piston part 31, which is connected via a disc-shaped flange 32 with an inner cylindrical piston part 33 of the Primaaus Wegerkolbens 9.
• a pot-like axial recess 34 for receiving the preload spring 6 is arranged on the inner piston part 33.
• a front edge 35 of the inner piston part 33 is thereby displaced relative to a front edge 36 of the radially outer piston part 31 by a length Z in the direction of the transmission.
• the ring pot 10 follows in its contour in the section of the representation of FIG. 2 essentially the contour of the central release piston 9 facing the dry clutch 30.
• the ring pot 10 comprises an outer sleeve-shaped region 37, which is substantially cylindrical, and an inner sleeve-shaped region 38 which is also cylindrical.
• the outer sleeve-shaped region 37 merges at its leading edge into a substantially radially extending region 39, which in turn merges into a substantially axially extending sleeve-shaped or conical-sleeve-shaped region 40. This merges into an in turn substantially radially extending region 41, which merges into the inner sleeve-shaped region 38 via an annular groove-shaped bulge 42 which extends in the direction of the dry clutch 30.
• the bulge 42 essentially serves to form a guide and receptacle for the preload spring 6.
• the outer seal 13 and the inner seal 14 are axially offset from one another, wherein the outer seal 13 is arranged closer to the dry clutch 30 than the inner seal 14.
• the two seals 13, 14 may also, for example, by a length measure in the order of the length Z be arranged relative to each other.
• the sliding sleeve 2 comprises a circumferential nose 43, which is arranged between the release bearing 3 and the outer ring 22 of the release bearing 3 and the ring pot 10. Between the inner ring 44 of the release bearing 3 and the sliding sleeve 2 remains a game, so that both are mutually rotatable.
• the outer sleeve-shaped region 37 is offset axially relative to the inner sleeve-shaped region 38, correspondingly the outer piston part 31 of the central release piston 9 is offset in the axial direction relative to the inner piston part 33 of the central release piston 9.
• the outer piston part 31 and the outer sleeve-shaped portion 37 relative to the inner piston part 33 and the inner sleeve-shaped portion 38 in the axial direction to the dry clutch 30 is arranged to be offset.
• the radially outer region 31 of the central release piston 9 forms a substantially cylindrical outer sliding surface 45 with the outer sleeve-shaped region 37.
• the radially inner region 33 of the central release piston 9 forms a substantially cylindrical inner sliding surface 46 with the inner sleeve-shaped region 38 of the ring pot 10.
• the outer sliding surface 45 is arranged axially offset relative to the inner sliding surface 46 in the direction of the dry clutch 30. Due to the staggered arrangement, it is possible to arrange the radially inner part of the central release in the direction of the transmission out. This is particularly possible if this space is not to be used by other components of the transmission. By this measure, the axial length of the combination engine dry clutch transmission can be reduced.
• Pneumatic slave cylinders are operated with compressed air, a drag repositioning of hydraulic fluid, which could be used as a lubricant, is therefore missing due to the system.
• the sealing surfaces therefore usually receive a Teflon coating, which is expensive and expensive to process.
• the lubricant is thus applied as a film on the surfaces in the area which is swept by the outer seal 13 and the inner seal 14.
• a siloxane having a very high solids content that matches the surface area of the inner and outer sliding surfaces 45, 46 is used.
• the lubricant contains substantially 55-90 weight percent polydimethylsiloxane, 5-45 weight percent polytetrafluoroethylene (PTFE) powder, wherein the particle size of the PTFE is between 1 and 20 microns.
• the lubricant has a density greater than 1 g / cm 3 .
• the siloxane also referred to as silicone oil
• the particle size of the lubricant and its viscosity harmonize particularly with a surface made of aluminum, which was produced by a machining process and subsequent hard anodization or anodizing, or a surface of a deep-drawn steel component, for example, was post-machined, and then optionally nitrided , wherein both surfaces previously shown surface roughness Rz in the range of 1-4 microns and a support share between 20 and 90%.
• the outer seal 13 and the inner seal 14 are lip seals of ethylene-propylene-diene rubber (EPDM) or hydrogenated nitrile rubber (HNBR), each having a hardness between 70 and 82 Shore.
• EPDM ethylene-propylene-diene rubber
• HNBR hydrogenated nitrile rubber
• the application of the lubricant is preferably carried out by spraying, since the lubricant has a fairly high viscosity during processing. For optimal adhesion, the surface must be dry and clean.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
• Mechanical Operated Clutches (AREA)

Priority Applications (4)

Applications Claiming Priority (4)

Publications (1)

Family

ID=38008236

Family Applications (1)

Country Status (5)

Cited By (6)

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Citations (5)

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• 2007
  • 2007-02-15 EP EP07702447A patent/EP1994297A1/de not_active Withdrawn
  • 2007-02-15 BR BRPI0708526A patent/BRPI0708526A8/pt not_active Application Discontinuation
  • 2007-02-15 WO PCT/DE2007/000294 patent/WO2007101419A1/de active Application Filing
  • 2007-02-15 DE DE112007000291.3T patent/DE112007000291B4/de not_active Expired - Fee Related
  • 2007-02-15 CN CN2007800081755A patent/CN101395397B/zh not_active Expired - Fee Related

Patent Citations (5)

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