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
  • F16D13/583—Diaphragm-springs, e.g. Belleville
  • F16D13/585—Arrangements or details relating to the mounting or support of the diaphragm on the clutch on the clutch cover or the pressure plate
• • 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
  • F16D13/75—Features relating to adjustment, e.g. slack adjusters
  • F16D13/757—Features relating to adjustment, e.g. slack adjusters the adjusting device being located on or inside the clutch cover, e.g. acting on the diaphragm or on the pressure plate

Definitions

• the invention relates to a friction clutch with a counter-pressure plate and a
• Clutch pressure plate with a housing attached to the counter-pressure plate, a rotatably and axially connected to the housing pressure plate and a biased between the housing and pressure plate, at an operating point of the friction clutch pressure plate and counter-pressure plate with the interposition of friction linings of a clutch disc with a predetermined contact force spanning disc spring, which upon actuation can be actuated in the opening direction by means of an actuation system acting on the plate spring tongues along an actuation path with a force characteristic curve with a force maximum and subsequent minimum force.
• Such friction clutches are sufficient in particular in drive trains of motor vehicles, for example from DE 39 20 188 A1, known.
• a plate spring is used to provide a contact force at the operating point of the friction clutch to clamp an axially displaceable, but rotationally fixed in a housing pressure plate with the interposition of friction linings of a clutch disc against a platen and thus to generate a frictional engagement between friction linings on the one hand and pressure plate and platen on the other ,
• the contact force is responsible in conjunction with other parameters for the maximum transmittable via the friction clutch torque.
• the plate spring has radially inner plate spring tongues, which are acted upon by an actuating system such as release axially along an actuation path, so that reduced by means of the operating force to be applied, the contact pressure at the operating point and thus the frictional closure successively lifted, the friction clutch is thus opened.
• an actuating system such as release axially along an actuation path
• the object of the invention is the development of a friction clutch with over a
• the proposed friction clutch includes a reaction plate which may be formed as a single flywheel or as a secondary flywheel of a dual mass flywheel.
• a reaction plate which may be formed as a single flywheel or as a secondary flywheel of a dual mass flywheel.
• two friction clutches can be combined to form a double clutch, wherein the counter-pressure plates of both friction clutches can be formed from a common disk part.
• a clutch pressure plate is preferably fastened by means of the housing, for example screwed or riveted.
• the clutch disc includes a non-rotatably and axially connected to the housing, for example by means of distributed over the circumference of leaf springs or plate spring assemblies pressure plate.
• the plate spring points radially inward extended plate spring tongues and forms a two-armed lever, which is supported by means of a radially arranged within a support region of the plate spring on the pressure plate lever point on the housing.
• the plate spring reduces the contact pressure on the pressure plate until it finally lifts under the action of the leaf springs of the friction linings and opens the friction clutch.
• the actuating system brings a release force, which corresponds to the sum of the plate spring force, the pad spring force and the leaf spring force taking into account the leverage ratios.
• a Kraftken line of the plate spring with a force maximum and subsequent force minimum compensate in such a way that the plate spring is assigned at least one force minimum at least partially compensating in the direction of the contact force servo spring.
• the maximum force of the plate spring can be limited to the contact pressure, so that the plate spring can be designed for smaller forces.
• the falling maximum force is compensated by the at least one servo spring, so that overall a balanced common characteristic can be formed.
• This disc spring and at least one servo spring work with the formation of synergy effects in the same direction of action, namely against the pressure plate so that no opposing distortion of plate spring and at least one servo spring must be made and thus the strength of the friction clutch can be designed without consideration of such counter forces.
• the relevant energy storage - plate spring and at least one synchronizing spring - form with their characteristics the common force forming the contact force.
• the friction clutch can preferably have a pitch equal to zero over a wear range between new and worn friction linings at the operating point, a contact pressure force with a substantially constant pitch. Accordingly, over a wide range plate spring and the at least one synchronous spring over an operating range of the friction clutch between the closed and fully opened friction clutch having a common characteristic with substantially constant pitch. Depending on the gradient, the characteristic is falling, rising or horizontal.
• the disc springs in a set for example by a stop, transport locks and the like transport position of the coupling tion pressure plate when compared with the operating point smaller actuating travel at the maximum force of the plate spring against the pressure plate and the at least one servo spring to be biased substantially force-free.
• a slight bias can only serve to avoid noise, such as rattling serve.
• the plate spring tongues are formed when the friction linings wear as a result of the displacing pressure plate, as a result of a preferably horizontal or slightly rising or falling characteristic, the contact pressure remains substantially the same.
• the proposed friction clutch remains space-neutral with respect to friction clutches without the proposed servo spring. This means that, in particular, an axial increase of the installation space of the proposed friction clutch caused by the installation of the at least one servo spring can be avoided. Furthermore, in contrast to friction clutches having a force maximum over the wear range having characteristic widened, so that the wear area can be widened along the actuation path or can be designed with greater certainty. Furthermore, due to a flat common characteristic tolerance deviations can be minimized.
• the proposed friction clutch is formed with a single servo spring, which as a complementary to the plate spring formed radially outside a support area on the housing on the plate spring axially supporting and engaging with plate spring tongues in the interspaces of the diaphragm spring tongues of the plate spring and the operating system in the same way as the plate spring acted upon Servotellerfeder is provided with a maximum force in the range of the minimum force of the plate spring.
• the usual number of plate spring tongues for example twelve, for example, reduced to six, so that sufficiently large recesses can be provided, in which the plate spring tongues of the servo disc spring can engage.
• the plate spring tongues of the plate spring and the servo disc spring can be actuated simultaneously and uniformly.
• the proposed friction clutch may be provided with at least one servo spring, which is formed from at least one radially outwardly of a support region of the diaphragm spring on the housing between the housing and the pressure plate facing away from the plate spring, axially effective energy storage.
• the characteristic of this at least one energy storage device may be linear, progressive, degressive or formed in the form of a plate spring with a force maximum. This may be a single annular energy store or multiple energy stores arranged around the circumference.
• the at least one axially effective energy store can be formed from at least one plate spring distributed between the circumference, the housing accommodated in a displaceably limited manner and supported on the pressure plate, and the housing supporting the housing.
• the bolts are biased by the at least one disc spring against the housing against a stop, wherein the bolt in the support region of the plate spring forms a dependent on the displacement of the pressure plate and thus dependent on the actuation and wear axial force on the pressure plate.
• a plurality of distributed over the circumference and held by rivets on the housing energy storage can be provided, for example, as unilaterally accommodated on the housing and applied to the plate spring leaf springs or as compression springs such as helical compression springs and the like.
• FIG. 1 shows a partial view of a friction clutch with plate spring and servo spring in longitudinal section through centering pin of the plate spring
• FIG. 2 shows a longitudinal section through part of the clutch pressure plate of the friction clutch of FIG. 1 along the servo disc spring
• FIG. 3 shows a longitudinal section through a part of the clutch pressure plate of the friction clutch of FIG. 1 along the disc spring
• Figure 4 shows a longitudinal section through a part of one of the clutch pressure plates of
• Figure 5 is a longitudinal section through part of one of the clutch pressure plate of
• FIG. 8 shows a diagram of a force behavior of a conventional friction clutch compared with a force behavior of a friction clutch with a common, horizontal characteristic curve formed from a plate spring and a servo disc spring, FIG.
• FIG. 9 shows a diagram of a force behavior of a friction clutch with a slightly rising characteristic curve formed from a disk spring and a servo disk spring
• FIG. 10 shows a diagram of a force behavior of a friction clutch with a characteristic curve formed from a disk spring and servo disk springs with a linear characteristic curve.
• FIG. 1 shows a part of a longitudinal section of the friction clutch 1 arranged around the axis of rotation d with the clutch pressure plate 2, the counterpressure plate 3, which is merely indicated and connected to a shaft such as a transmission input shaft in a radially rotationally connected manner, optionally having a torsional vibration damper and / or a centrifugal pendulum pendulum Clutch disk 4 with the friction linings 6 arranged opposite one another with interposition of the lining suspension 5.
• FIGS. 1 to 3 taken together, show a part of the longitudinal sections through the clutch pressure plate 2 along different cutting lines.
• the housing 7 is in this case firmly connected to the counter-pressure plate and takes, for example by means of distributed over the circumference of the housing attached leaf springs or leaf spring assemblies rotatably and axially displaceable on the pressure plate 8.
• the pressure plate 8 is acted upon by a predetermined radius at the support region 10 axially from the plate spring 9.
• the plate spring 9 is supported to provide a contact force of the pressure plate 8 by means of the wire ring 1 1 on the folded wall portion 12 of the housing 7 from.
• the characteristic of the diaphragm spring shows at axial Displacement, for example via an actuation path such as Ausgurweg the friction clutch 1, which causes the axial displacement of the pressure plate 8, a maximum, so that in conventional friction clutches in due to axial wear of the friction linings 6 at the operating point relocating pressure plate changes the maximum contact force and thus a maximum Moment on the friction linings can be transmitted by appropriate contact pressure of the pressure plate only with a correspondingly strong design of the plate spring 9.
• the friction clutch 1 which adjoins the maximum force of the plate spring 9 force minimum by means of the servo spring 13 in the form of complementary to the plate spring 9 servo disc spring 14, wherein a desired common characteristic curve of plate spring 9 and servo disc spring 14, for example, substantially horizontal, slightly rising or can be given sloping.
• the servo disc spring 14 is placed on the plate spring 9, is supported at the operating point on the wire ring 1 1 and is axially biased by the wire ring 15 against the plate spring 9.
• the maximum force of the servo disc spring 14 is placed in the force minimum of the plate spring 9, so that overall a balanced common characteristic can be achieved.
• the contact pressure of the plate spring 9 and the servo disc spring 14 at the operating point to form the friction engagement between pressure plate 8 and counter-pressure plate 3 on the one hand and the friction linings 6 on the other hand with closed friction clutch 1 is constant, so that over a wear area of the friction linings 6 in contrast to one with a Force maximum provided characteristic of a plate spring, a constant contact force, for example, slightly above a maximum contact force for transmitting the maximum torque to be transmitted can be provided without over-pressing must be provided in certain phases of wear.
• plate spring 9 and the servo disc spring 14 each distributed over the circumference radially inwardly directed plate spring tongues 16, 17 are provided.
• the plate spring tongues 16, 17 are mutually rotated in the circumferential direction so that they are in gaps between the plate spring tongues of the other spring - plate spring 9 and Servotellerfeder 14 - are positioned.
• plate spring 9 and servo disc spring 14 at axial displacement of the plate spring tongues 16, 17 in the direction counterpressure plate 3 by means of a pressure ring of an actuating system, for example, automatically or actuated by means of a pedal.
• plate spring 9 and servo disc spring 14 are supported on the abutment 18, which is formed by the wire ring 19 and the centering pin 20 accommodated in the wall part 12 of the housing 7 for centering disc spring 9 and servo disc spring 14 and release the frictional engagement. grip the pressure plate 8 on the friction linings 6 by the support portion 10 of the plate spring 9 follows under the action of the leaf springs.
• the disengagement force for the actuating system results in accordance with the uniform common characteristic of plate spring 9 and Servotellerfe- 14 on the actuation path, taking into account the effective leverage of the plate spring 9 and servo disc spring 14 in a similar manner as the contact force on the wear area. It is understood that in order to design the common characteristic of disc spring 9 and servo disc spring 14, the pad spring force and the leaf spring force are taken into account in order to achieve a desired uniform overall characteristic.
• FIG. 6 shows the sensor plate spring 14 of Figures 1 to 3 with the plate spring tongues 17 and provided therebetween gaps 21.
• Figure 7 shows the plate spring 9 of Figures 1 to 3 with the plate spring tongues 16 and interposed gaps 22.
• the friction clutch 1 of Figure 1 disc spring 9 and servo disc spring 14 are positioned against each other so that the plate spring tongues 16 are positioned in the gaps 21 and the plate spring tongues 17 in the gaps 22, so that an axial displacement of the plate spring tongues 16, 17 by means of an actuation system without contact can be done.
• FIG. 4 shows a longitudinal section of a clutch pressure plate 2 a changed with respect to the clutch pressure plate 2 of FIGS. 1 to 3, which can be provided in the friction clutch 1 of FIG. 1 instead of the clutch pressure plate 2.
• a plurality of circumferentially distributed servo springs 13a in the form of cup springs 14a are effectively disposed between the cup spring 9a and the wall part 12a of the casing 7a.
• the plate spring 9a and the plate springs 14a form a common uniform characteristic over the actuation path of the friction clutch 1.
• the plate springs 14a are supported on the wall part and are limitedly supported on the pin 23a.
• the bolts 23a are received in the wall portion 12a axially displaceable and wegbe friendship means of the retaining rings 24a.
• the plate springs 14a are biased to avoid noise only slightly opposite to the plate spring 9a. If the pressing force of the plate spring 9a decreases during the transition from the maximum force to the minimum force, the bias of the plate springs 14a increases relative to the plate spring 9a.
• the pressure plate 8a is displaced in the direction of the wall part 12a, so that the bolts 23a are axially displaced against the action of the plate springs 14a relative to the wall part 12a, so that the force minimum of the plate spring 9a advantageously by the in this Range set maximum force of the plate springs 14a is balanced.
• the disc springs 14a may be formed by a single annular plate spring which is received on the wall part 12a by at least one, preferably at least three, circumferentially distributed, axially displaceable pin 23a.
• FIG. 5 shows an alternative to the clutch pressure plate 2a of FIG. 4 in the form of the clutch pressure plate 2b in longitudinal section.
• the servo springs 13a are replaced by the servo springs 13b, which in the exemplary embodiment shown are designed as a pre-bent leaf springs 14b arranged between the disk spring 9b and the wall part 12b of the housing 7b.
• the servo springs 13b For captively receiving the distributed over the circumference arranged leaf springs 14b these are received by means of the rivet 25b on the wall portion 12b.
• the path compensation between pressure plate 8b and wall portion 12b upon actuation of the friction clutch or over the wear region of the friction linings is effected by a sufficient intrinsic elasticity of the leaf springs 14b.
• the characteristic of the leaf springs can be substantially linear, progressive or degressive and takes place in such a way that at least partially the force minimum of the disc spring 9b is compensated and thereby results in a substantially balanced common characteristic.
• the leaf springs 14b may be partially or completely replaced by compression springs such as helical compression springs in other embodiments. Furthermore, the leaf springs 14b can be combined over a part or the entire circumference to a plurality or a single leaf spring.
• FIG. 8 shows the diagram 26 with the contact force F via the actuation path s.
• the dashed curve 27 shows the behavior of a plate spring of a conventional friction clutch.
• the plate spring To keep over a wear range B (k), the contact force F of the plate spring over the maximum contact force F (a, max) and to ensure a sufficient transmission of the maximum torque on the friction clutch, the plate spring must be Ü oversized, thus to the Beginning and end points of the wear area B (k) the contact force F of the diaphragm spring is sufficient. In between, at least in the region of the force maximum F (k, max), a high, undesired overpressing takes place.
• the force maximum F (s, max) of the servo springs 13, 13a and the force minimum F (n, min) of the plate spring 9, 9a essentially coincide that indicated by the arrows by summation of the path-related force components, the common characteristic (29) is formed over a wide path range of the actuation path, at least over the wear area B (k) expandable wear area B (n) substantially horizontally above the maximum contact pressure F (a, max) is.
• the characteristic curves 30 of the padding suspension at the extreme points of the wear region B (n) are furthermore shown which, like the leaf spring characteristic curves (not shown), are advantageously taken into account in the optimization of the common characteristic curve 29.
• FIG. 9 shows the diagram 31 of the contact force F via the actuating travel s.
• This is provided by appropriate design of the characteristics 32, 33 of the plate spring and at least one servo spring over the actuating travel s and the wear area B (n) a slightly increasing common characteristic curve 34.
• Such or similar common characteristics 34 may be provided in particular in trucks. For example, this can be compensated for a decreasing over a slow life coefficient of friction, which in contrast to the horizontal maximum contact force shown in Figure 9 F (a, max) may require increasing contact forces. In this way, the maximum torque to be transmitted over life of the friction clutch or the clutch disc with the friction linings are transmitted with increasing maximum contact forces.
• the diagram 35 of Figure 10 shows the behavior of the friction clutch of Figure 1 in conjunction with the clutch pressure plate 2b of Figure 5.
• the characteristic curve 36 of the plate spring 9b is compensated by means of the linear characteristic 37 of the servo springs 13b.
• a sufficiently balanced and uniform common characteristic curve 38 within the wear region B (n) with contact forces F over the maximum contact force F (a, max) is produced.

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

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• 2014
  • 2014-02-24 WO PCT/DE2014/200077 patent/WO2014131415A2/de active Application Filing
  • 2014-02-24 CN CN201480011181.6A patent/CN105074249B/zh not_active Expired - Fee Related
  • 2014-02-24 DE DE102014203198.2A patent/DE102014203198A1/de not_active Withdrawn
  • 2014-02-24 DE DE112014001052.9T patent/DE112014001052A5/de not_active Withdrawn

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