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
  • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
  • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
  • F16D3/12—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted for accumulation of energy to absorb shocks or vibration
• • 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
  • F16D13/60—Clutching elements
  • F16D13/64—Clutch-plates; Clutch-lamellae
  • F16D13/68—Attachments of plates or lamellae to their supports
• • 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
  • F16F15/1204—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 with a kinematic mechanism or gear system
• • 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
  • F16F15/1204—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 with a kinematic mechanism or gear system
  • F16F15/1205—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 with a kinematic mechanism or gear system with a kinematic mechanism, i.e. linkages, levers
• • 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
• • 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
• • 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
• • 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
  • F16F2230/00—Purpose; Design features
  • F16F2230/0052—Physically guiding or influencing
  • F16F2230/0064—Physically guiding or influencing using a cam
• • 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
  • F16F2232/00—Nature of movement
  • F16F2232/02—Rotary

Definitions

• the present invention relates to a torsional vibration damper, in particular for a clutch disc within a drive train of a motor vehicle, a corresponding clutch disc and a clutch, in particular for the drive train of a motor vehicle.
• Torsional vibration dampers are known in automotive engineering, for example from DE 10 2015 211 899 A1, in which an input part and a limited input part rotatable output part, which are coupled by intermediate elements and spring means, which are arranged so that the spring devices not in Circumferential direction are arranged.
• This type of torsional vibration damper has heretofore been known with two intermediate elements and two spring means which connect them. Due to the design with two spring elements only limited design options with regard to the performance parameters of the torsional vibration damper are given. In addition, arise in the design of such a torsional vibration damper conflicts, on the one hand the longest possible spring means (springs) are necessary to have as much potential energy available.
• the object of the present invention is to at least partially overcome the problems known from the prior art and, in particular, to provide a torsional vibration damper which has a simple structure and whose function is independent of manufacturing tolerances.
• This object is achieved with the features of independent claim 1.
• Further advantageous embodiments of the invention are specified in the dependent formulated claims.
• the individually listed in the dependent formulated claims features can be combined with each other in a technologically meaningful way and can define further embodiments of the invention.
• the features specified in the claims are specified and explained in more detail in the description, wherein further preferred embodiments of the invention are illustrated.
• the torsional vibration damper according to the invention in particular for a clutch disc within a drive train of a motor vehicle, having an input part arranged about a rotation axis and an output part rotatable relative to the input part about the rotation axis against the action of a spring device with a plurality of spring means, between the input part and the Output member arranged torque-transmitting intermediate elements, which are forcibly radially displaced by means of cam gears in a relative rotation of input part and output member and between the insects- th the spring means is arranged, with a number of intermediate elements is formed is formed, which corresponds to the number of spring means characterized that the number is at least three.
• a spring means is meant a means which is constructed from one or more springs. Under a spring while an element is understood, which is elastically deformable and thereby builds up a restoring force. Preference is given to compression springs, in which a compression of the compression spring causes a restoring force, the compression spring would like to extend again.
• a spring is constructed as a helical spring.
• the spring means preferably comprises a single spring or a spring assembly of at least two cooperating springs.
• Previously known torsional vibration damper with forced radial Verlage- tion of the intermediate elements are previously known only with two spring means and two intermediate elements. At each intermediate element both spring means are fastened, so that a rectangular arrangement results. In the present case with three or more intermediate elements and spring means results in a different geometric Arrangement. For example, with a number of three (intermediate elements and spring means), a triangular arrangement results which leaves more space for other components inside the torsional vibration damper than in the known arrangement.
• an embodiment with more spring means compared to the above-described embodiment with two spring means significantly more design freedom in the design of the torsional vibration damper, so that other power ranges of the torsional vibration damper are possible.
• Each spring device preferably comprises one or more helical compression springs.
• Intermediate element, input part and output part each have ramps in which rolling elements can roll. These roll on the one hand in ramps in the input part and intermediate element, while other rolling elements roll in ramps in the intermediate element and in the output part, so that transmission of moments from the input part via the intermediate element to the output part is possible. Due to the shapes of the ramps in the input part, intermediate element and output part, it is possible to define the rigidity of the damper system.
• the torsional vibration damper is designed so that the corresponding spring means are actuated straight along its axis. This reduces lateral loads on the spring and increases the durability of the connection of the spring means to the intermediate elements.
• each spring means on a direction of action and the effective direction of a spring means includes with the effective direction of each other spring means a different from zero first angle.
• the effective direction of the spring is defined in particular by the configuration of the corresponding spring (s).
• the term direction of action is the direction in which the spring means can apply or absorb forces.
• the longitudinal axis thereof represents the effective direction.
• Such an embodiment advantageously permits the displacement of the spring means radially outward.
• Such a configuration is preferred for an odd number of intermediate elements and spring means, that is to say, for example, for three or also five intermediate elements and spring means.
• close the effective directions of adjacent spring means at three intermediate elements and spring means preferably an angle of 60 °.
• each intermediate element has a relative direction of movement, in which it can be moved during operation, and each spring means has an effective direction, wherein each effective direction includes a second angle different from zero with each direction of relative movement.
• each spring means on a direction of action and the effective directions of all spring means are tangent to a circle with a circular radius, the center of which lies on the axis of rotation.
• Such a symmetrical design provides a relatively large degree of freedom in the design of a corresponding torsional vibration damper, in particular radially far outward arrangement of the spring means are possible.
• the torsional vibration damper can be designed so simply.
• all intermediate elements are identical.
• first and second spring means increases the possibilities in the design of the torsional vibration damper, since other damping characteristics and frequency spectra can be achieved.
• a clutch disc is proposed for a clutch, in particular in the drive train of a motor vehicle, which comprises a torsional vibration damper as described here, as well as a clutch which comprises a corresponding clutch disc.
• a clutch disc in particular, a lining ring is fastened radially on the outside of the input parts of the torsional vibration damper.
• a motor vehicle is proposed with such a coupling in an advantageous manner. The details and advantages disclosed for the torsional vibration damper can be applied and applied to the clutch disc, the clutch and the motor vehicle, and vice versa.
• Fig. 1 and 2 a known as known torsional vibration damper
• FIG. 3 shows a section of a first example of a torsional vibration damper
• Figures 6 and 7 the intermediate elements and spring means of the first example in the undeflected and deflected state.
• Fig. 10 u. 11 shows a second example of a torsional vibration damper in the undeflected and deflected state in the cutout
• torsional vibration damper 1 comprises an input part 2, intermediate elements 3, cam gear 4,
• the intermediate elements 3 each have, radially inward, a further ramp 14, which are in operative connection with ramps 15 arranged in the output part 10.
• the intermediate elements 3 are likewise guided via rolling elements 16 rolling freely between the correspondingly designed ramps 14, 15, so that their movement again results in a parallel deflection the spring means 9 means.
• the total torsion angle between the input part 2 and the output part 10 results from the sum of the angles of rotation which occur in the respective cam mechanism 4, 5 at a specific deflection of the spring means 9 ,
• the torsional moment on the input part 2 for the rotational movement is supported as a pure torsional moment on the output part 10.
• the unit consisting of intermediate elements 3 and spring means 9 is not subject to external momentary action, but defines the fleas of the transmitted moment via the fleas of the force from the parallel deflection of the spring means 9.
• the torsional vibration damper 1 in this example has compared to the example of Figures 1 and three intermediate elements 3, three input parts 2, three output parts 10 and a spring device 8 with three spring means 9.
• spring means 9 individual springs or spring packs can be formed from a plurality of springs.
• Each input part 2 is radi al outside with one connected to a pad ring 18 which is connected directly or indirectly with friction linings, not shown here, so that together with a pressure plate a friction clutch can be built.
• the output part 10 is opposite the corresponding input part 2 against the action of the spring device 8 with the two arranged on the corresponding intermediate piece 3 spring means 9 limited to the rotation axis d rotatable.
• FIGS. 4 and 5 show two views of a clutch disk 19 with three input parts 2 (only one input part 2 is shown in FIG. 5 for reasons of clarity), three output parts 10 and three intermediate parts 3 which are interconnected by three spring means 9 of a spring device 8 are connected.
• the torsional vibration damper 1 is shown in the undeflected state.
• the intermediate elements 3 are made identical, as well as the spring means. 9
• FIG. 6 shows a part of a torsional vibration damper 1 according to FIGS. 3 to 5 in the undeflected state
• FIG. 7 shows the same part of the torsional vibration damper 1 in the deflected state.
• the spring means 8 have a first length 11 in the undeflected state and a second length 12 in the deflected state which is smaller than the first length 11.
• the spring means (energy store) 9 are therefore compressed in the deflection by the intermediate elements 3.
• Each spring means 9 in each case has an effective direction 22.
• the direction of action 22 is displaced in parallel by the deflection of the intermediate elements 3 (compare FIGS. 6 and 7).
• the effective directions 22 are not aligned parallel to each other.
• Fig. 8 and 9 show schematically the directions of action 22 and applied forces in the example of Figures 3 to 7.
• Fig. 8 shows the undeflected case analogous to Fig. 6.
• the spring means 9 exert a spring force Fp in the direction of action 22 to the Zwi element 3.
• the spring forces Fp are in vectorial equilibrium with the rocker force Fy / / applied to the intermediate element 3. Increases the rocker force Fy ⁇ /, so the intermediate member 3 is pressed radially inwardly in the direction of the seesaw force F ⁇ j overall.
• the spring means 9 are compressed and the spring force Fp increases until the spring forces Fp are again in vectorial equilibrium with the rocking force F ⁇ j .
• the deflection of the spring means 9 is reduced from the first length 11 (see FIG. 8) to the second length 12 (see FIG. 9).
• FIG. 8 and 9 also show a first angle 23 between the directions of action 22 of two adjacent spring means 9, this is not equal to zero for all directions of action 22 of all spring means 9. Furthermore, FIG. 9 shows by way of example a second angle 24 between the effective direction 22 of a spring means 9 and a direction of relative movement 20 of an intermediate element 3.
• FIGS. 10 to 13 show two further examples of a torsional vibration damper 1 in which four intermediate elements 3 are formed with a spring device 8 with four spring elements 9. Each spring means 9 is connected to two adjacent intermediate elements 3 in the circumferential direction and connects them to one another.
• FIG. 10 and 11 show an example of a torsional vibration damper 1 in the non-deflected state, which is rotationally symmetrical.
• four identical spring means 9 are formed between the intermediate elements 3.
• all spring means 9 have a first length 11 in the non-deflected state.
• FIG. 11 shows an example of the torsional vibration damper 1 in the deflected state.
• the spring means 9 are compressed to a second length 12 by the movement of the intermediate elements 3 in the direction of relative movement 20.
• FIGS. 12 and 13 show a further example of a non-rotationally symmetrical torsional vibration damper 1 with four non-identical intermediate elements 3 and spring means 9.
• two opposite first spring means 29 and two opposite second spring means 30 are formed, which are in their length in the undeflected state and possibly differ in their spring constant.
• the intervening intermediate elements 3 in the circumferential direction are formed correspondingly adapted, so that all intermediate elements 3 have a common outer circumference 21.
• the first 29 and second spring means 30 and the corresponding ramps of the intermediate elements 3 are formed so that in this example, a radially inwardly directed displacement of the intermediate elements 3 takes place in the deflected state.
• first 29 and second spring means 30 a torsional vibration damper 1 can be generated, which allows a further flexibilization of the use of the interior space between the intermediate elements 3.
• a comparison of FIGS. 13 and 11 shows that the asymmetrical design of the torsional vibration damper 1 according to FIGS. 12 and 13 also results in a change in the relative directions of movement 20 of the intermediate elements 3.
• Each spring means 9 has an effective direction 22 which is defined by the orientation and design of the spring means 9.
• the spring means 9 are arranged so that they are tangential to a circle 25 having a circular radius 26 and the center 27 is located on the axis of rotation d.
• Fig. 15 shows very schematically a coupling 28 which summarizes a clutch disc 17 which comprises at least one torsion damper 1 as described herein.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Acoustics & Sound (AREA)
• Aviation & Aerospace Engineering (AREA)
• Mechanical Operated Clutches (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=66041077

Family Applications (1)

Country Status (6)

Families Citing this family (5)

Family Cites Families (8)

• 2018
  • 2018-04-05 DE DE102018107993.1A patent/DE102018107993A1/de not_active Withdrawn
• 2019
  • 2019-03-19 EP EP19715382.8A patent/EP3775610A1/de not_active Withdrawn
  • 2019-03-19 WO PCT/DE2019/100256 patent/WO2019192652A1/de active Application Filing
  • 2019-03-19 DE DE212019000243.9U patent/DE212019000243U1/de active Active
  • 2019-03-19 CN CN201990000519.6U patent/CN214367510U/zh active Active
  • 2019-03-19 KR KR1020207027567A patent/KR20200138230A/ko not_active Application Discontinuation
  • 2019-03-19 US US17/042,980 patent/US11454287B2/en active Active

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