WO2019120373A1 - Plateau de friction exerçant une pression axiale avec un partenaire de friction - Google Patents

Plateau de friction exerçant une pression axiale avec un partenaire de friction Download PDF

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Publication number
WO2019120373A1
WO2019120373A1 PCT/DE2018/100960 DE2018100960W WO2019120373A1 WO 2019120373 A1 WO2019120373 A1 WO 2019120373A1 DE 2018100960 W DE2018100960 W DE 2018100960W WO 2019120373 A1 WO2019120373 A1 WO 2019120373A1
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WO
WIPO (PCT)
Prior art keywords
friction
radius
rotation
groove
friction plate
Prior art date
Application number
PCT/DE2018/100960
Other languages
German (de)
English (en)
Inventor
Ivo Agner
Original Assignee
Schaeffler Technologies AG & Co. KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2019120373A1 publication Critical patent/WO2019120373A1/fr

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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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/385—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs double clutches, i.e. comprising two friction disc mounted on one driven shaft
    • 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
    • F16D2021/0615—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate the central input plate is supported by bearings in-between the two 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
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/22—Vibration damping

Definitions

  • the invention relates to a friction plate for axial compression with a friction partner for the frictional transmission of torque about an axis of rotation, wherein the friction surface has a plurality of grooves, wherein the grooves extend in the circumferential direction and each have a groove width, and
  • Circumferential direction has a continuous course over at least 90 °, wherein the elevation curve extends axially out of the friction surface and is pointed in the axial direction, wherein the elevation curve has a radius of curvature to the axis of rotation, wherein the elevation curve in its course in
  • Circulation direction has a change in radius, wherein the elevation curve has a maximum point with a maximum radius and a minimum point with a
  • the friction plate is mainly characterized in that the radius of curvature has a change in radius such that the maximum radius is greater by at least 1.5 times the groove width than the minimum radius.
  • Friction clutch known as a disc brake.
  • Friction clutch is a solvable
  • Torque transmission for example, a crankshaft
  • the friction pair formed for this purpose comprises at least one friction plate and at least one friction partner, for example a friction disk or one or more brake pads.
  • the friction plate is the harder friction surface, which is the softer
  • the friction surface of Gussanpressplatten of friction clutches is preferably made by means of the cutting method turning. Here, the friction surface is machined over the entire surface width used for the frictional engagement. Using a conventional indexable insert results in a
  • Friction surface with rounded Rillentälern and (nearly) pointed elevations which line up in the radial direction, that are immediately adjacent to each other.
  • the elevations are pointedly dependent on the shape of the indexable insert, so for example, the rounding radius, also the distance, ie the relative position of the valleys to each other and the material behavior.
  • the material behavior affects the shape of the survey in the way that if the material is very tough, for example, burr-like peaks are formed, and that if the material is very brittle, uneven fracture edges can be formed.
  • Fig. 2 and in Fig. 3 are exemplary illustrated some form of writing such grooves, in which case the
  • a groove width is 0.3 mm [three tenths of a millimeter] and a groove depth is 20 pm [twenty microns], for example, so a groove depth to groove width ratio is more likely to be 1:10 to settle to 1:50.
  • the distance between the resulting contours of the grooves is determined by the
  • Feed (/) set The feed is here the amount of radial movement of the indexable insert per revolution of the workpiece.
  • the feeds range in ranges up to 0.6 mm [six tenths of a millimeter] and the resulting depth of the groove valleys in ranges up to 40 pm [forty microns].
  • the groove resulting from the turning process therefore has a spiral shape which depends on the direction of rotation of the
  • FIG. 4 shows a clearly exaggerated representation of such (ideal, ie mathematical) spiral shape.
  • the friction surface of the friction plate described above works in the friction partner in the form of circumferential grooves. This creates concentric, ie non-spiral, surface structures in the friction lining.
  • a third order of the ripple of the friction surface and small offsets between pressure plate and center of rotation coupling, which can produce large rotation angle ranges with almost invariable radii not only in a CNC spiral, but also in a mathematically ideal spiral are causes for circumferential grooves in the lining already during the running-in process , This is shown in FIG.
  • Friction disc with the friction plate In, for example, mobile applications,
  • friction plate-side shaft for example, the transmission shaft in a friction clutch, with axial vibrations and tilting vibrations of the friction plate due to this
  • the Rupf is a jerky
  • abrasion particles which are not tribologically effective can collect in the valleys of the valleys and, at higher surface pressures, can be removed from the grooves by means of the resulting friction with the counter friction surface
  • Circumferential direction can be transported or wiped.
  • a rough friction surface offers the possibility of collecting abrasive particles in the groove valleys, so that they can not become tribologically effective and ensure good damping behavior of the frictional contact.
  • the invention relates to a friction plate for axial compression with a friction partner for frictionally transmitting a torque about an axis of rotation, wherein the friction plate has at least one friction surface with a radial surface width in a plane perpendicular to the axis of rotation, and
  • the friction surface has a plurality of grooves with a groove valley and two groove mountain flanks each adjacent to a further groove of the plurality of grooves, the grooves extending in the circumferential direction and one each
  • Circumferential direction has a continuous course over at least 90 °, wherein the elevation curve extends axially out of the friction surface and is pointed in the axial direction, wherein the elevation curve has a radius of curvature to the axis of rotation, wherein the elevation curve in its course in
  • Circulation direction has a change in radius, wherein the elevation curve has a maximum point with a maximum radius and a minimum point with a
  • Torque for example, in a friction clutch or a disc brake, set up.
  • the friction plate forms, for example, the
  • Pressure plate the counter plate or, in a double clutch, a central web.
  • the brake disk axially loaded on one or both sides by means of a brake pad.
  • the friction plate is a cast component or a
  • the grooves are produced by (for example surface-turning) rotation in the friction side, so that macroscopically, or in the middle, a flat friction surface is produced, to which the rotation axis is normally aligned. It should be noted here that always meaningful from technically achievable or cost pressure
  • the grooves are produced by extrusion. Especially with such
  • the shape of the grooves is arbitrary, preferably in terms of
  • the grooves cover a large part of the surface width of the friction surface over the circumference, preferably, the entire friction surface is provided with grooves.
  • the grooves should be suitable for absorbing abrasion particles but, on the other hand, should not have a tendency to be buried in the counter friction surface.
  • the grooves each have, for example
  • rounded Rillental on which, for example, steadily, in each case a left and right edge of a groove with an inclined surface with axial portion are executed and adjacent to an adjacent groove flank of an adjacent groove.
  • the groove flanks merge into one another at an acute angle, as is known from the prior art.
  • narrow lands are formed with a flat surface of radial extent are. This is achieved, for example, when the axial feed of an indexable insert leads to a groove width which is less than half of the radial feed (over one complete revolution).
  • a low abrasion performance is hereby achieved by means of a survey curve, which in the direction of rotation has a continuous course over at least 90 °, preferably at least 180 °, particularly preferably over a complete circulation, ie 360 °.
  • Continuously means in this context that the survey curve is performed without abrupt jumps in the radial direction, preferably in the direction of rotation is steadily formed.
  • the elevation curve rises axially out of the friction surface, that is in the direction of the groove flanks.
  • Survey curve is pointed in the axial direction. This means that the tip forms a (continuous) ridge in the direction of rotation, in which the flanks to the right and to the left of the ridge in each case by more than 30 ° from the friction plane to the
  • Return plate material preferably by more than 45 °.
  • the burrs are dependent on the selected material and / or the cutting speed of the
  • Indexable insert or other process parameters for example, irregular, for example, such as a summit chain and or more parallel ridges, ie local maxima, formed with some very steep partial edges.
  • the elevation curve superimposes the grooves and thus forms a separate curve on the friction surface.
  • the elevation curve has a radius of curvature with respect to the axis of rotation, which has a change in radius in the course of the elevation curve in the direction of rotation. It is thus at least one maximum point with a maximum radius and at least one minimum point with a minimum radius over the course of
  • This change in radius is formed in such a way that the maximum radius is greater than the minimum radius by at least 1.5 times the groove width. At 1, 5 times the groove width, an installation tolerance is already taken into account, so that it is ensured that the survey curve is the location of the
  • the radius change should correspond to a complete revolution, ie 360 °, not more than 20 times the groove width. After that, no advantageous effects are achieved with respect to the prevention of the formation of circumferential grooves.
  • the friction plate is the elevation curve of the, preferably unsteady, transition from a groove mountain edge to the adjacent Rillenberg flank formed, preferably a plurality of radially parallel grooves with radially outwardly increasing radius of curvature, preferably concentric with the axis of rotation and / or preferred with the same groove width is formed.
  • the elevation curve is formed by at least two adjacent grooves.
  • the elevation curve is formed by all groove flanks.
  • the elevation curve is formed as pointed, as described in the introduction conventionally generated in the introduction of grooves in a turning process under conventional feed. Deviating from this, however, the radius change of the grooves is greater than this in such conventional adjacent grooves is the case. Although this is achievable by reducing the number of revolutions of the grooves, but this leads to an undesirable blunting of the survey. How nevertheless a large radius change can be achieved is shown in the following description.
  • a plurality of parallel grooves are formed, which run adjacent in the circumferential direction. That is, adjacent grooves are not part of a single continuous curve, but are multiple curves with their own starting point and end point.
  • such grooves are rotated with an indexable insert having a plurality of adjacent cutting edges, so that the feed corresponds to a multiple of a groove, namely the number of grooves, which are formed with a cut.
  • Such grooves are concentric, so executable with the axis of rotation as the center, or with an eccentric arrangement of the center.
  • the groove width and / or groove depth is preferably constant over the entire surface width.
  • the friction surface is inexpensive to produce, for example by means of a rotation process, and the damping behavior is approximately equal over the entire surface width.
  • the radius of curvature of the at least one elevation curve increases in the direction of rotation, preferably constant.
  • a spiral is formed, preferably one
  • Radial change in the course can lead to a retention of abrasion particles.
  • the DC component is reduced in the course and thus already leads to a lower feed to a reduced inclination
  • a spiral is combined with an eccentricity, so that the center of the spiral is arranged offset to the axis of rotation.
  • the grooves are for example unbalanced clamped in a lathe chuck, but the turning itself is, except for a rotation start and / or a rotation end, as previously known executed.
  • the eccentricity should be, for example, a groove width, preferably three times to six times a groove width.
  • the at least one elevation curve extends over at least one complete revolution, preferably several revolutions.
  • Such a survey curve is similar to the meeting of two immediately adjacent groove flanks of conventional grooves or in the form of a spiral (almost) the same.
  • these elevation curves are formed by two, several or all groove flanks, and particularly preferably with an eccentricity to the axis of rotation.
  • the at least one elevation curve on an elliptical shape or waveform wherein preferably a uniform ellipse is formed with its center on the axis of rotation.
  • the elevation curve preferably formed by the groove flanks immediately adjacent grooves, differently than described above as a closed curve, ie as a ring formed.
  • a closed curve ie as a ring formed.
  • an elliptical shape can be used which has at least a minimum radius at two
  • Minimal points and at least one maximum radius at two maximum points are formed as a ring with a waveform.
  • the shaping can be controlled by means of a CNC-controlled lathe.
  • the friction plate is formed on the friction surface at least one radially outwardly facing dirt groove, which has an axial depth that in a compressed with a friction partner state of abrasion and at least in the dissolved state a removal of recorded abrasive particles radially outward is possible, wherein the dirt groove is preferably oriented away from radially inward to radially outward from the direction of rotation and / or preferably over the entire radial
  • the dirt groove is deeper than the grooves, so that even at high contact pressures and / or in at least one state, for example, when the friction plate in a separate state abraded against the friction partners, a removal of transported in the dirt groove wear particles is guaranteed.
  • the depth of the dirt groove is 0.1 mm [one tenth of a millimeter] to 1.5 mm, for example, at a width of about 10 mm [ten millimeters] 1.2 mm.
  • the width of a dirt groove for example, 2 mm to 15 mm, on the one hand, a quick production allows and on the other hand the largest possible effective friction surface (for example, with the grooves) remains.
  • the dirt groove is preferably formed steeper than the elevation curve. As a result, a faster removal of abrasive particles from the dirt groove is facilitated, while the grooves remove the abrasion particles only slowly, so that the wear particles on the one hand not tribologically effective but on the other hand enough
  • Abrasion particles remain in the grooves, so that the desired damping effect is ensured against a Rupf the friction pairing.
  • the friction plate comprises a measuring groove, which is wider and / or deeper than a survey curve, wherein preferably the measuring groove is arranged radially outside of the friction surface.
  • Measuring means are not reliably detectable, for example, because the measuring head is too large and / or the radial attachment surface (ie, the axial extent of the
  • Survey curve for example, a groove flank
  • a measuring groove which allows a conclusion about the change in radius.
  • the measuring groove is sufficiently wide or deep to be reliable
  • the same shape is depicted with a measuring groove.
  • a circular ring ie with a constant radius, is formed, of which the position of the center, so the eccentricity, for example by means of a three-point measurement, can be detected.
  • the pitch of the spiral itself is sufficiently known as a manufacturing parameter or due to the shape, so that if so desired
  • the measuring groove is preferably introduced radially outside the surface width of the friction surface in the friction plate.
  • the measuring groove is inserted in interrupted segments on radially inwardly or radially outwardly extending flanges, for example for a leaf spring in a friction clutch or for fixing the brake disc to a wheel hub.
  • a marking is provided which indicates the position of the maximum point and / or an eccentricity so that the friction plate can be mounted in the correct angular position.
  • the invention relates to a friction pair arrangement having an axis of rotation for the frictional transmission of a torque as a result of an axial compression of the friction pair arrangement, comprising at least the following components:
  • the friction partner is a friction disc and the friction pair arrangement comprises a first friction plate having a first friction surface with a first elevation curve with a first radius change and a second friction surface with a second friction surface with a second elevation curve with a second radius change and the friction disc two corresponding counter friction surfaces the two friction surfaces are formed identically according to an embodiment according to the above description, wherein the direction of rotation of the first radius change of the direction of rotation of the second radius change is arranged in opposite directions.
  • the friction pair arrangement proposed here is for transmitting a
  • Torque set up around the axis of rotation The axis of rotation is congruent with the axis of rotation of the friction plate.
  • the counter friction surface of the friction partner is softer than the friction surface of the friction plate, so that in a frictional engagement abrasive particles are mainly formed by the friction surface.
  • the counter friction surface is formed by a friction lining, which is preferably exchangeable.
  • the friction surface has at least one elevation curve according to an embodiment as described above, so that formation of circumferential grooves is avoided or at least greatly reduced.
  • the radii changes are two
  • Friction surfaces for example in a friction clutch, with friction plates as
  • Friction partner aligned with each other so that a radial force resulting from the change in radius is canceled by the other friction surface. This is particularly effective when the friction disc is disposed between two friction plates, with their resulting from the respective change in radius
  • the friction plate is designed for such applications already for a desired high heat capacity for receiving and dissipating the heat input in a slipping engagement and hung that the radial forces of a conventional design are already sufficiently counteracted.
  • the invention relates to a dual clutch for a drive train of a motor vehicle, comprising at least the following
  • Friction disc of the second Reibparaniser is permanently connected to transmit torque
  • a central web has a first friction surface and a third
  • the dual clutch is designed to release a torque from one
  • Output shaft reached which has an axially displaceable, usually with the drive shaft rotation-resistant, pressure plate, which is pressed against at least one corresponding friction disc.
  • a counter plate is provided, which forms an axial abutment for the contact force, so that the friction disc does not have to be stored against axial forces and / or stiffened.
  • Central ridge formed, which is arranged centrally between the friction packs and accordingly has two friction surfaces, which axially
  • intermediate plates are provided, which are arranged to be axially displaceable similar to the pressure plate, but are arranged between two friction plates, that is, as a central web has two axially oppositely directed friction surfaces.
  • Counter plates, the central web and / or the intermediate plate is a friction plate.
  • the friction disk preferably has two friction linings to the two antagonists of the respective friction pack, which form the respective counter friction surface.
  • those are from the radius changes
  • Central web or the intermediate disc has such an orientation of the change in radius that the resulting radial forces on the pressure plate that of the other pressure plate is diametrically opposed.
  • Motor vehicle proposed which comprises a drive unit with a drive shaft and a dual clutch according to the above description, wherein the drive shaft for torque transmission by means of the double clutch is detachably connectable to at least one consumer.
  • the powertrain is configured to be one of a power plant, for
  • Example of an energy conversion machine preferably one
  • An exemplary consumer is at least one drive wheel of a motor vehicle and / or an electric generator for providing electrical energy.
  • a recording of an inertial energy introduced, for example, by a drive wheel can also be implemented.
  • the at least one drive wheel then forms the drive unit, wherein its inertial energy by means of
  • Double clutch on an electric generator for recuperation, so for the electrical storage of braking energy, with a suitably equipped drive train is transferable. Furthermore, in a preferred embodiment, a plurality of drive units are provided, which by means of
  • Double clutch in series or connected in parallel or decoupled from each other are operable, or their torque is releasably available for use available.
  • Examples are hybrid electric drives Drive engine and internal combustion engine, but also multi-cylinder engines in which individual cylinders (groups) are switchable.
  • the double clutch proposed here allows an extended life of the friction pair, preferably at least the friction linings, at the same time a low Rupfanberichtkeit at least one of the friction packs.
  • a motor vehicle which has at least one drive wheel which can be driven by means of a drive train according to the above description.
  • the drive train described above has a double clutch, which allows an extension of the life of the friction surface and / or the counter friction surface of a friction pair, while at the same time the Rupfan mecanickeit is low. This allows maintenance intervals to be extended.
  • Passenger cars are assigned to a vehicle class according to, for example, size, price, weight and power, and this definition is subject to constant change according to the needs of the market.
  • cars of the class small cars and microcars are classified according to European classification of the class of Subcompact Car and in the British market they correspond to the class Supermini or the class City Car.
  • Examples of the micro car class are a Volkswagen up! or a Renault Twingo.
  • Examples of the small car class are an Alfa Romeo Mito, Volkswagen Polo, Ford Fiesta or Renault Clio.
  • Fig. 1 Top view of a friction plate with eccentric spiral and dirt groove
  • FIG. 3 shows a sectional view of a friction pair arrangement with buried circumferential grooves
  • Fig. 6 Top view of a friction plate with ellipse
  • Fig. 7 sectional view of a double clutch with opposite
  • Fig. 11 a drive train in a motor vehicle with dual clutch.
  • the first friction plate 1 is mounted here in an axially movable by means of leaf springs 58 on flanges 59 on a co-rotating lid 57 and is for example a pressure plate.
  • the axis of rotation 3 is the torque transmission axis to which the components are aligned and balanced.
  • the first friction plate 1 has a first one
  • Friction surface 4 in which a survey curve 15, here formed as a spiral over several complete revolutions 30, is introduced in exaggerated representation.
  • the spiral of the elevation curve 15 has a minimum point 24 with a
  • Gradient radius 18 which is formed in a first direction of rotation 12 continuously, and preferably continuously.
  • the center of the elevation curve 15 is arranged with an eccentricity 60 to the axis of rotation 3, so that there is a spiral shape overlying first change in radius 19, the maximum point 21 with its maximum radius 23 because of the spiral shape (also exaggerated here) as shown slightly counterclockwise twisted next to the direction of eccentricity 60 is formed.
  • the minimum point 24 is with his
  • Minimal radius 26 (here also shown exaggerated) as shown twisted slightly counterclockwise next to the opposite direction of the eccentricity 60 formed.
  • the eccentricity 60 referred to as a change in radius 19, wherein the change in radius 19 is composed of the increase in radius due to the spiral shape of the elevation curve 15 and the eccentricity 60.
  • the change in radius 19 is composed of the increase in radius due to the spiral shape of the elevation curve 15 and the eccentricity 60.
  • here are optional and independent of the shape of the elevation curve 19 and type of
  • Friction plate 1 three grooves 33 created which are inclined away from a direction of rotation 36 at about 45 ° to a radial direction outwardly inclined. These allow a targeted removal of abrasion particles 35, so that they do not accumulate in the grooves (see FIGS. 2 and 3) and thus can not become tribologically effective.
  • Fig. 2 is a fragmentary friction pair 38, comprising a
  • a friction surface 4 is formed, which forms on average a plane perpendicular to the axial direction 17 9 for the frictional contact with the counter friction surface 42 of the friction disc 40.
  • This friction surface 4 has a plurality of immediately adjacent grooves 10, in each of which abrasion particles 35 are received.
  • each groove 10, which are all optionally identical here, has a groove valley 11 with a groove width 14, which in the illustration above is a first one
  • Two immediately adjacent groove flanks form an acute transition 27, which according to one embodiment, the elevation curve 15 with a
  • Radial change 19 (see, for example, Fig. 1) chosen too low, so that at the acute transitions 27 recirculating grooves 73 have formed, which in
  • FIGS. 4 and 5 show in comparison two elevation curves 15, each with a continuous continuous course 16 in the direction of circulation 12 and over a complete revolution 30 (exaggerated), once as an ideal (mathematical) spiral 61 (FIGS. 4) and once formed as a CNC spiral 62 ( Figure 5). Is the
  • Gradient radius 18 is placed on a center of both axes of rotation 2 (see, for example, Fig. 1), so the minimum point 24 with a minimum radius 26 on
  • Fig. 6 is a first friction plate 1 with a frictional surface width 8 in
  • the elevation curve 15 is formed here as an ellipse 31 (shown exaggeratedly), the center 32 of which is optionally arranged here on the axis of rotation 3. This results along the course 16 in the circumferential direction 12 over a complete circulation 30, a rotationally symmetric change in radius 19 with a first minimum point 24 and a second
  • a double clutch 46 is shown with a co-rotating lid 57 in section, wherein a torque about the rotation axis 3 by means of a first Reibcontractan extract 38, or a first Reibvers, of a
  • Input shaft 49 to a first output shaft 50 and by means of a second
  • Input shaft 49 on a second output shaft 63 releasably, namely frictionally engaged, transferable.
  • a vibration damper 64 is shown here, for example, a dual mass flywheel. The first
  • Reibparan onion 38 includes a first friction plate 1, here a pressure plate, a central web 51 (axially rigid counter-plate) and axially disposed therebetween first friction disc 40, which are axially compressible by means of a first actuator unit 65.
  • the second Reibparan onion 39 includes a second friction plate 2, here a pressure plate, the central web 51 and an axially disposed therebetween second friction disc 41, which are axially compressible by means of a second actuator unit 66.
  • the central web 51 has in the illustration on the left, ie belonging to the first Reibparan angel 38, a first friction surface 4, which is frictionally engageable with the first Gegenreib composition 42 of the first friction disc 40 in contact.
  • the first friction plate 1 has a second friction surface 5, which is frictionally engageable with the second counter-friction surface 43 of the first friction disc 40 in contact. Furthermore, the central web 51 in the representation on the right, ie belonging to the second friction pair 39, a third friction surface 6, which is frictionally engageable with the third Jacobreib composition 44 of the second friction plate 41 in contact.
  • the second friction plate 2 has a fourth friction surface 7, which is frictionally engageable with the fourth Jacobreib composition 45 of the second friction plate 41 in contact.
  • the first direction of rotation 12 of the elevation curve 15 of the first friction plate 1 and the second direction of rotation 13 of the elevation curve 15 of the central web 51 are opposite to each other.
  • a first circumferential direction 12 that is, inversely to the first friction surface 4 of the central web 51, and at the fourth friction surface 7, a second circumferential direction 13 is formed.
  • no elevation curve is formed here.
  • a friction plate 1 is shown in a same view as in Fig. 1 and in Fig. 6, so that reference is made to the description there.
  • Friction plate 1 has an elevation curve 15 formed as a CNC spiral 62, which is arranged with an eccentricity 60 to the rotation axis 3, so that here simplified as identical to the eccentricity 60 shown, a change in radius 19 along the course 16 in the direction of rotation 12 results , Because the grooves 10 (see FIG. 2) are relatively small, for a simpler measurement of the angular position of the eccentricity 60 a measuring groove 37 is provided in the flanges 59, ie radially outside the friction-effective surface width 8, with a preferably constant measuring groove radius 67, ie one circular measuring groove 37, formed.
  • FIG. 9 and 10 show, in section, two embodiments of a measuring groove 37, which has a measuring groove width 69 such that a measuring head 68 can be easily placed therein (coarse) and a sufficient measuring groove depth 70 that the measuring head bears radially can be brought.
  • the wall of the measuring groove 37 is in the embodiment of FIG. 9 parallel to the rotation axis 3 (see FIG. 8) and in the embodiment of FIG. 10 inclined to the rotation axis 3 (see FIG. 8) formed such that an open Measuring groove 37 for
  • a drive train 47 comprising a drive unit 71, shown here as a three-cylinder internal combustion engine, a drive shaft 72, a dual clutch 46 and a releasably torque transmitting connected left drive wheel 52 and right drive wheel 53, shown schematically.
  • the drive train 47 comprising a drive unit 71, shown here as a three-cylinder internal combustion engine, a drive shaft 72, a dual clutch 46 and a releasably torque transmitting connected left drive wheel 52 and right drive wheel 53, shown schematically.
  • Drive shaft 72 forms directly the input shaft 49 of the double clutch 46, for example, as shown in Fig. 7.
  • the drive train 47 is here in one
  • Motor vehicle 48 is arranged, wherein the drive unit 71 with his
  • Motor axis 56 is arranged transversely to the longitudinal axis 55 in front of the driver's cab 54.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un plateau de friction (1, 2) exerçant une pression axiale avec un partenaire de friction (40, 41) pour la transmission par friction d'un couple autour d'un axe de rotation (3), la surface de friction (4, 5, 6, 7) présentant une pluralité de rainures (10), les rainures (10) s'étendant en direction circonférentielle (12, 13) et présentant chacune une largeur (14) de rainure, et la surface de friction (4, 5, 6, 7) présentant au moins un profil de came (15) présentant un tracé (16) continu en direction circonférentielle (12, 13) sur au moins 90°. Le profil de came (15) est en saillie axialement vers l'extérieur à partir de la surface de friction (4, 5, 6, 7) et est réalisé en pointe en direction axiale (17), le profil de came (15) présente un rayon (18) de son tracé par rapport à l'axe de rotation (3), le profil de came (15) présente une variation (19, 20) du rayon de son tracé (16) en direction circonférentielle (12, 13), et le profil de came (15) présente un point maximal (21, 22) présentant un rayon maximal (23) et un point minimal (24, 25) présentant un rayon minimal (26). Le plateau de friction (1, 2) est principalement caractérisé en ce que le rayon (18) du tracé présente une variation (19, 20) de rayon de telle manière que le rayon maximal (23) est plus grand que le rayon minimal (26) d'au moins 1,5 fois la largeur (14) de la rainure. Le plateau de friction de l'invention, présentant un profil de came en pointe, permet d'obtenir une bonne caractéristique d'amortissement tout en évitant la formation de rainures périphériques.
PCT/DE2018/100960 2017-12-20 2018-11-27 Plateau de friction exerçant une pression axiale avec un partenaire de friction WO2019120373A1 (fr)

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DE102017130711 2017-12-20
DE102017130711.7 2017-12-20
DE102018100803.1 2018-01-16
DE102018100803.1A DE102018100803A1 (de) 2017-12-20 2018-01-16 Reibplatte zum axialen Verpressen mit einem Reibpartner

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018124686B3 (de) 2018-10-08 2020-01-16 Schaeffler Technologies AG & Co. KG Drehmomentübertragungseinrichtung mit einer Anpressanordnung zum Verpressen eines Reibelements
DE102021116936B3 (de) 2021-06-30 2022-11-03 Schaeffler Technologies AG & Co. KG Reibplatte mit einer zweistufig aufgebrachten Oberflächengestaltung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6121425A (ja) * 1984-07-06 1986-01-30 Toyota Motor Corp クラツチフエ−シング
DE19848583A1 (de) * 1998-10-21 2000-04-27 Mannesmann Sachs Ag Anpreßplatte
EP2835561A1 (fr) * 2013-08-08 2015-02-11 Aisin Seiki Kabushiki Kaisha Appareil d'absorption de fluctuation de couple
DE102015206887A1 (de) * 2014-05-12 2015-11-12 Schaeffler Technologies AG & Co. KG Kupplung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6121425A (ja) * 1984-07-06 1986-01-30 Toyota Motor Corp クラツチフエ−シング
DE19848583A1 (de) * 1998-10-21 2000-04-27 Mannesmann Sachs Ag Anpreßplatte
EP2835561A1 (fr) * 2013-08-08 2015-02-11 Aisin Seiki Kabushiki Kaisha Appareil d'absorption de fluctuation de couple
DE102015206887A1 (de) * 2014-05-12 2015-11-12 Schaeffler Technologies AG & Co. KG Kupplung

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