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
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
  • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
  • F16F15/123—Wound springs
  • F16F15/1232—Wound springs characterised by the spring mounting
  • F16F15/12346—Set of springs, e.g. springs within springs
• • 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
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
  • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
  • F16F15/123—Wound springs
  • F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
  • F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
  • F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
  • F16F15/12373—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs the sets of springs being arranged at substantially the same radius

Definitions

• the invention relates to a clutch disc having a rotatable about an axis input part with radially outer friction linings and at least three circumferentially distributed window-shaped recesses and a relation to the input part at a limited angle about the rotational axis rotatable relative to the output part with a hub and arranged radially outside the hub , Distributed over the circumference, aligned with the recesses in the non-rotated state of the input part and output part cutouts, wherein in the recesses and cutouts each compression spring assemblies consisting of at least one between stops of the recesses and cutouts under bias built-in outer spring and housed in this, shorter inner spring are included.
• Generic clutch discs are known for example from DE 102 18 472 A1 and may have a multi-stage characteristic of the compression spring assemblies in that the outer springs under bias in input side and output side recesses or cutouts under bias, that is, are recorded without clearance angle and therefore upon rotation of input - And starting part against each other are acted upon immediately, while the accommodated in the outer spring inner spring is shorter than the outer spring and thus only at larger angles of rotation of corresponding Beauftschungs Suiteen such as circumferential boundaries of the cutouts or recesses is applied.
• the inner spring can be excited to oscillate, which can manifest itself in a pendulum of the end faces of the inner spring between the Beauftschungs Schemeen and leads to unwanted noise of the clutch disc.
• wear of the springs can occur by appropriate contact with each other.
• the object of the invention is the development of the prior art with increased spring capacity with low intrinsic friction of the compression spring assemblies.
• the object is solved by the subject matter of claim 1.
• the subordinate claims give advantageous embodiments again.
• the proposed clutch disc includes a rotatable about an axis of rotation
• each compression spring packs consisting of at least one incorporated between circumferential attacks of the recesses and cutouts under bias outer spring and accommodated in this, shorter inner spring, which are compressed at a rotation of the input and output part and in cooperation with a at least over a partial angle of the rotation effective friction device form a torsional vibration damper.
• the slopes of the turns of these are in the same direction, ie formed with the same sign.
• the inner spring is flared at its end forming the positive connection. In this case, an end turn of the inner spring can at least partially radially overlap an end turn of the radially directly adjacent outer spring and thus form the positive connection.
• the radially inner outer spring with a diameter that is constant over its length so as not to widen the installation space of the latter relative to the radially outer spring.
• the end turn of the immediately adjacent outer spring can be bevelled radially inward with a diameter which opens in the direction of the stop.
• an inner periphery of the outer outer spring may be formed with a constant diameter over its length.
• a radial gap can be set with a radial gap that remains constant over its length, so that, in particular under the influence of centrifugal force, friction can be reduced with friction hysteresis and wear occurring.
• Figure 1 is a partially sectioned partial view of a clutch disc with a view of a
• FIG. 2 shows a view of the partially cut-together compression spring packet of FIG. 1,
• Figure 3 is a view of the inner spring
• Figure 4 is a partially sectioned view of the inner spring radially immediately adjacent outer springs.
• FIG. 1 shows a section of the clutch disc 1 which is essential for the invention, as is otherwise known from its construction of the prior art, for example from the aforementioned DE 102 18 472 A1.
• the clutch disc 1 are distributed over the circumference preferably three or four cutouts 5 and recesses 6 mutually aligned in the output part 3 and this in the form of two disc parts 4 flanked on both sides input part 2 is introduced, in which the compression spring 7 are housed.
• the compression spring packs 7 act as energy storage, which store energy during compression and release again during decompression.
• the compression spring assemblies 7 are formed from the two outer springs 8, 9 and the inner spring 10.
• the two outer springs 8, 9 are preferably on the peripheral side stops 1 1, 12, 13, 14 of the recesses 6 and cutouts 5 or have little play on these and thus form a first damper stage at small angles of rotation of input and output part.
• the inner spring 10 is shorter than the outer spring formed 8 and 9 and is compressed by the cutouts 5 and recesses 6 only larger angles of rotation and then forms in cooperation with the outer springs 8, 9 a second damper stage with higher rigidity.
• a positive connection between the inner spring 10 and the outer spring 8 is set.
• the turns 21 of the inner spring 10 have gradients m3, which are aligned in the same direction as the pitch m2 of the outer spring 9.
• inner diameter Di and outer diameter D A are substantially constant along the axis of action.
• Figure 2 shows the compression spring assembly 7 with the outer springs 8, 9 and the inner spring 10.
• the Endwindungen 18 are flared at the front end and engage at least partially in the constant diameter in their turns 17th the outer spring 9 radially.
• the end turn 19 of the outer spring 9 to the stops 1 1, 13 ( Figure 1) widening gate 20, in which the last end turn 18 of the inner spring dips radially.
• FIG. 4 shows the outer spring 9 with a constant outside diameter D A and in the region of the end turns 19 on its inner circumference a conically widened area ⁇ , which is formed at the end by the gate 20.

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Citations (3)

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• 2013
  • 2013-10-17 DE DE112013005108.7T patent/DE112013005108A5/de not_active Ceased
  • 2013-10-17 EP EP13805252.7A patent/EP2912337A1/de not_active Ceased
  • 2013-10-17 WO PCT/DE2013/200233 patent/WO2014063699A1/de active Application Filing
  • 2013-10-17 CN CN201380055119.2A patent/CN104755798B/zh active Active
  • 2013-10-17 BR BR112015009082A patent/BR112015009082A2/pt not_active Application Discontinuation
  • 2013-10-17 DE DE102013221103.1A patent/DE102013221103A1/de not_active Withdrawn

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Non-Patent Citations (1)

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