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
  • F16F15/1204—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
  • F16F15/1206—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 planetary 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
  • F16H—GEARING
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
  • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
  • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
• • 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
  • F16H—GEARING
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
  • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
  • F16H2045/0268—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means the damper comprising a gearing
• • 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
  • F16H—GEARING
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type

Definitions

• the invention relates to a torsional vibration damper according to claim 1.
• a torque transmission device which can be used, for example, in a drive train of a vehicle in order to dampen or eliminate as far as possible rotational irregularities.
• the torque transmission device has an input to be driven for rotation about a rotation axis input area and an output range, wherein between the input area and the output area a first torque transmission path and parallel thereto a second torque transmission path and a coupling arrangement for superimposing the guided over the torque transmission paths torques is provided, wherein in the first Torque transmission path is provided a first phase shifter arrangement for generating a phase shift of rotational irregularities guided over the first torque transmission path with respect to rotational irregularities conducted over the second torque transmission path.
• a turbine wheel of a hydrodynamic converter is coupled to the output side of the torque transmission device.
• an improved torsional vibration damper can be provided in that the torque transmitting device at least two at least partially parallel torque transmission paths for transmitting torque between an input side and an output side and a translation device (s) for branching and / or summarizing by means of the torque transmission paths transmitted torque is formed has.
• the translation device as a circulation gear, wherein the translation device comprises at least one planet gear and at least a first gear part, wherein the first gear part has at least a first recess, wherein the first recess has a first toothing and the planet gear has a second toothing, wherein the planet gear at least partially in the recess arranged and the first toothing has a meshing engagement with the second toothing.
• the planet gear is rotatably mountable about a planetary gear axis, wherein the planet gear axis is arranged parallel to the axis of rotation, wherein the planet gear has a third toothing.
• the second toothing and the third toothing are arranged in a common plane of rotation. Additionally or alternatively, it is also conceivable that the second toothing is arranged radially outside the planetary gear axis and the third toothing radially inward to the planetary gear axis.
• the planet gear has a center of mass, wherein the center of gravity is arranged at a distance from the planet gear axis.
• the center of mass is arranged radially inward of the planetary gear axis. In this way, a gearing rattle can be avoided by a clever arrangement of the center of mass of the planetary gear.
• an effective radius of the third toothing is smaller than an effective radius of the second toothing.
• the second toothing is arranged spaced from the third toothing in the circumferential direction, wherein preferably between the second toothing and the third toothing in the circumferential direction an arc section is arranged, wherein in particular the arc section is concave.
• the planetary gear can be optimized in terms of component strength.
• the second toothing is arranged adjacent to the third toothing in the circumferential direction.
• the transmission device has a second transmission part, wherein the second transmission part is arranged axially adjacent to the first transmission part. is arranged, wherein the second gear part has a fourth toothing, wherein the fourth toothing meshes with the second or third toothing.
• the second gear part has a second recess, wherein preferably the second recess has the fourth toothing.
• the translation device is coupled to the input side, wherein one can be coupled to the output side
• Momentenkoppeleinnchtung is provided between the translation device and the torque coupling device.
• the two torque transmission paths are provided.
• a phase shifter arrangement is provided for generating a phase shift of rotational irregularities guided via the first torque transmission path with respect to rotational irregularities conducted via a second torque transmission path.
• the torque coupling device is designed to superimpose the torques transmitted via the torque transmission paths.
• the transmission device comprises a planet carrier, wherein the planet carrier is designed to support the planetary gear, wherein the planet carrier is coupled to the torque coupling device.
• a spring damper is provided between the torque coupling device and the output side, wherein the spring damper comprises a spring arrangement arranged between the torque coupling device and the output side, wherein the spring damper comprises a vibration system with the
• a friction device wherein the friction device has a first friction surface and a second friction surface.
• the first friction surface and / or the second friction surface is at least the planetary gear and / or the intermediate mass and / or the translation device and / or the
• Torque coupling means and / or the planet carrier coupled torque-torque wherein the first friction surface is in frictional engagement with the second friction surface, wherein the friction device is preferably designed to brace the first Wheelmomentüber- transmission path relative to the second torque transmission path.
• Figure 1 is a functional diagram of a torsional vibration damper
• FIG. 2 shows a half-longitudinal section of a constructive embodiment of the torsional vibration damper shown in FIG. 1 according to a first embodiment
• FIG. 3 shows a cross section along a sectional plane A-A shown in FIG. 2 through the torsional vibration damper shown in FIG. 2;
• FIG. 3 is a half-longitudinal section of a constructive embodiment of the torsional vibration damper shown in FIG. 1 according to a second embodiment
• FIG. 4 shows a cross section along a sectional plane B-B shown in FIG. 3 through the torsional vibration damper shown in FIG. 3;
• FIG. 5 is a half-longitudinal section of a constructive embodiment of the torsional vibration damper shown in FIG. 1 according to a third embodiment
• FIG. 6 shows a half-longitudinal section of a constructive embodiment of the torsional vibration damper shown in FIG. 1 according to a fourth embodiment
• FIG. 7 is a half-longitudinal section of a constructive embodiment of the torsional vibration damper shown in FIG. 1 according to a fifth embodiment.
• FIG. 8 shows a half-longitudinal section of a constructive embodiment of the torsional vibration damper according to a sixth embodiment shown in FIG.
• FIG. 1 shows a functional diagram of a torsional vibration damper 10.
• rotational masses 100 for example a hub, a flange, a carrier plate or a cast iron are symbolized by box-shaped elements.
• a particularly voluminous rotational mass 100 for example a turbine housing or a particularly massive rotational mass 100, can be represented by a relatively large box.
• a rotational mass 100 shown large can also be shown for illustrative reasons, for example, to be present at several engaging on the rotational mass 100 frictions or torque M clearly.
• a line-shaped connection in FIG. 1 represents a torque connection 30.
• the torsional vibration damper 10 has an input side 20 and an output side 25.
• the input side 20 can be connected in a torque-locking manner, for example, with a reciprocating motor of a motor vehicle.
• the output side 25 can be connected in a torque-locking manner, for example, to a transmission of the vehicle.
• the reciprocating engine provides a torque M for driving the vehicle, which has rotational irregularities.
• Torque M is introduced via the input side 20 in the torsional vibration damper 10.
• the torsional vibration damper 10 comprises a coupling device 50, a hydraulic torque converter 55, a spring damper 60, a transmission device 65 and a torque coupling device 70. Between the transmission device 65 and the torque coupling device 70, a first torque transmission path 75 and a second torque transmission path 80 are provided. The first torque transmission path 75 is arranged parallel to the second torque transmission path 80.
• the coupling device 50 is a torque transmitting device that is controllable to selectively transmit or disconnect torque M between its opposite ends.
• the coupling device 50 may be designed, for example, as a dry clutch, a multi-plate clutch or a wet clutch running in an oil bath.
• a hydraulically designed actuating device can be provided for actuating the coupling device 50.
• an electrical or a mechanical actuation of the coupling device 50 is conceivable.
• the converter 55 represents a torque transmission which can be produced in the hydrostatic interaction between an impeller 1 10 and a turbine wheel 1 15. A torque M transmitted by the converter 55 is dependent on a speed difference between the turbine wheel 15 and the impeller 1 10.
• the translation device 65 is designed as a planetary gear, in particular as a planetary gear.
• a spring arrangement 120 can be configured, for example, as a bow spring or compression spring. In this case, no difference between a bow spring and a compression spring is made in Figure 1.
• the spring arrangement 120 is designed to provide a vibration-damping transmission of torque M.
• the bow spring is an elastic element for power transmission, which is arranged to extend tangentially about an axis of rotation 15.
• the compression spring has a similar function as the bow spring. Deviating from this, the compression spring is usually helical and does not extend curved, but straight along a tangent to a perimeter of a circle segment about the axis of rotation 15.
• the spring assembly 120 may have one or more arrangements of the bow spring and / or the compression spring.
• the bow springs or compression springs can be interconnected in parallel and / or in series with each other.
• the output side 25 has a second rotational mass 100.2.
• the first rotational mass 100.1 is connected by means of the coupling device 50 with a third rotational mass 100.3.
• the first rotational mass 100. 1 is furthermore connected to the impeller 1 10 by means of a first torque connection 30.
• the third rotational mass 100.3 is connected in a torque-locking manner by means of a second torque connection 30.2 to the transmission device 65.
• the transmission device 65 is essentially rigidly connected on the output side via a third torque connection 30.3 to a fourth rotational mass 100.4.
• the fourth rotational mass 100.4 is connected to the torque coupling device 70 in the first torque transmission path 75 by means of a first spring arrangement 120.1.
• the fourth rotational mass 100.4 in conjunction with the first spring arrangement 120.1 and the fifth rotational mass 100.5, forms a phase shifter arrangement 130 in its tuning.
• the phase shifter assembly 130 forms a vibration system in which the fourth rotational mass 100.4 and the fifth rotational mass 100.5 against the first spring assembly 120.1 can oscillate against each other.
• the second torque transmission path 80 is the output side, the translation device 65 by means of a fourth torque connection 30.4 with the
• the spring damper 60 has a second spring arrangement 120.2, wherein the second spring arrangement 120.2 is arranged between the torque coupling device 70 and the second rotation mass 100.2 (output side 20).
• the spring damper 60 forms another oscillating system with the torque coupling device 70 and an output side 25 rotatable about the axis of rotation 15 with respect to the torque coupling device 120.2 with respect to the torque coupling device 70.
• the torque M is passed from the first rotational mass 100.1 to the third rotational mass 100.3 when the clutch device 50 is in the closed state, which in turn is transmitted via the second torque connection 30.2 transmits the torque M to the translation device 65.
• the transmission device 65 branches the torque M into the two torque transmission paths 75, 80 as a function of a ratio i, which the transmission device 65 has.
• the torque M is over the third torque connection 30.3 in the first torque transmission path 75 to the fourth rotational mass 100.4 and passed over the first spring arrangement 120.1 to the fifth rotational mass 100.5.
• the phase shifter assembly 130 is tuned such that the rotational inaccuracy loaded with the torque M is above a resonant frequency of the phase shifter assembly 130.
• This causes the rotational non-uniformity is transmitted out of phase, preferably with a phase offset of 180 °, from the fourth rotational mass 100.4 on the first spring assembly 120.1 to the fifth spring assembly 120.5.
• the rotational non-uniformity is transmitted to the fifth rotational mass 100.5 via the second torque transmission path 80 substantially without a phase offset.
• the fifth rotational mass 100.5 operates here as a torque coupling device 70 and superimposed over the two torque transmission paths 75, 80 superimposed rotational non-uniformity with each other.
• the phase offset of the rotational inaccuracy transmitted via the first torque transmission path 75 at least partially extinguishes the rotational nonuniformity transmitted via the second torque transmission path 80.
• the torque M is forwarded to the output side 25 via the second spring arrangement 120.2, if necessary with and with a portion of the rotational non-uniformity that has not been erased.
• FIG. 2 shows a half-longitudinal section through a constructive embodiment of the torsional vibration damper 10 shown in FIG. 1.
• the illustration of the first rotational mass 100.1 of the first torque connection 30.1 and of the converter 55 is dispensed with.
• the third rotational mass 100.3 in the embodiment comprises a disk carrier 200 of a wet friction clutch, not shown, and a disk 210.
• the disk carrier 200 comprises a disk carrier base 205 and a toothing 206 for the torque-locking connection of friction disks to the disk carrier 200.
• the disk carrier plate 205 extends essentially in the radial direction. Axially adjacent to the plate carrier base 205, the disc 210 is arranged.
• the disk 210 is connected in a torque-locking manner to the disk carrier base 205 via a first connection 215.
• the fourth rotational mass 100.4 comprises, axially adjacent to the disc 210, an intermediate mass 220 formed as a first gear part of the transmission device 65 on a side opposite the disc carrier base 205.
• the intermediate mass 220 has a first intermediate mass part 225 and a second intermediate mass part 230.
• the first intermediate mass part 225 extends axially in the direction of the disk carrier 200 radially on the outside of the disk carrier bottom 205.
• the second intermediate mass part 230 is connected torque-tight to the first intermediate mass part 225 via a second connection 235.
• the second intermediate mass part 230 has a recess (not shown), wherein the first spring arrangement 120.1 is arranged in the recess. In this case, an end face of the recess of the second intermediate mass part 230 is assigned to an end face of the first spring arrangement 120.1.
• the first spring arrangement 120.1 is formed in the embodiment with two bow springs 240, 245, wherein a first bow spring 240 is disposed radially inwardly of a second bow spring 245.
• a first bow spring 240 is disposed radially inwardly of a second bow spring 245.
• the fifth rotational mass 100.5 includes a side window 255.
• the side window 255 includes a first side window part 250. Radially outside, the first spring arrangement 120.1 is encompassed by the first side window part 250.
• the first side window part 250 is designed substantially cup-shaped and is axially in Figure 2 on the right side, so opposite to the first intermediate mass portion 225 past the first spring assembly 120.1.
• the side window 255 also has a second side window part 260, which is connected by means of a third connection 265 to the first side window part 250 in a torque-locking manner. Opposite in the circumferential direction to the second intermediate mass part 230 of a front side of the first spring assembly 120.1 is associated with a front side of the second side window part 260.
• the second spring arrangement 120.2 likewise comprises two sheet feeder countries, wherein one of the two bow springs is arranged radially inwardly of the other bow spring.
• the output side 25 or the second rotational mass 100.2 comprises an output part 270 and a hub 275. Axially between the first side window part 250 and the second side window part 260, the output part 270 is provided.
• the output part 270 extends substantially in the radial direction and is radially inwardly connected to the hub 275 torque-locking.
• the hub 275 is designed as a hollow shaft and has on the inside a shaft-hub connection (not shown) 280 to a transmission input shaft 285 of the transmission.
• On the hub 275 is rotatable, but secured in the axial direction of the disk carrier 200, the second intermediate mass part 225 and the second side window part 250 rotatably supported.
• the translation device 65 is arranged.
• the transmission device 65 is designed as a planetary gear and advantageously comprises in the circumferential direction a plurality of planetary gears 290.
• the planetary gear 290 is rotatably mounted about a Planetenrad- axis 295 on a planet carrier 300 of the translation device 65 by means of a bearing 345.
• the planetary gear axis 295 is equidistant from the rotational axis 15 with respect to the circumferentially disposed planetary gears 290.
• the Planetenradachse 295 is arranged parallel to the axis of rotation 15.
• the planet carrier 300 is connected in a torque-locking manner to the second side window part 260 and is thus part of the fifth rotational mass 100.5.
• the planet carrier 300 and the second side window part 260 form the second torque transmission path 80.
• the first side window 265 forms the torque coupling device 70 from FIG.
• the planet carrier 300 is rotatably mounted on the hub 275 on the hub 275 in the circumferential direction.
• the planet carrier 300 is mounted directly on the hub 275.
• a rolling and / or sliding bearing for supporting the planet carrier 300 may additionally be provided on the hub 275.
• the second intermediate mass part 230 (see FIG. 3) has a first recess 305 radially inwardly of the second connection 235.
• the first recess 305 has, in the embodiment, a recess contour 310 which is substantially part-annular. Radially on the inside, the first recess 305 has a first toothing 315, so that the first toothing 315 is formed sun-like.
• the planetary gear 290 passes through the first recess 305.
• the planet gear 290 has a second toothing 320, which is arranged corresponding to the first toothing 315 radially inward of the planetary gear axis 295.
• the second toothing 320 has a meshing engagement with the first toothing 315.
• Radially on the outside of the planetary gear 295, the planetary gear 290 has a third toothing 325.
• the second toothing 320 in this case has an effective radius r 2 , based on the Planetenradachse 295, which is greater than a Wirkradius r 3 of the third gear 325.
• the second gear 320 and the third gear 325 are in a common plane of rotation relative to the Planetenradachse 295 and also arranged with respect to the axis of rotation 15.
• the second toothing 320 and the third toothing 325 are spaced from one another.
• an arc section 330 is provided in the circumferential direction between the second toothing 320 and the third toothing 325.
• the arcuate portion 330 is concave and connects the second toothing 320 with the third toothing 325.
• the second toothing 320 is arranged adjacent to the third toothing 325. Due to the configuration of the planetary gear 290 with two different effective radii of the teeth 320, 325, the planetary gear 290 has a center of gravity 335 which, relative to the planetary gear 295, is arranged radially inward of the planetary gear 295. In a rest position, the center of mass 335 is arranged in a plane spanned by the axis of rotation 15 and the planetary gear axis 295.
• the disc 210 is formed as a ring gear and has on an inner circumferential surface a fourth toothing 340, which corresponds to the third toothing 325 of Planetary gear 290 is formed.
• the fourth toothing 340 has a combing engagement with the third toothing 325.
• a torque M possibly loaded with a torsional vibration introduced into the disk carrier 200 via the disk carrier 200, which acts as a third rotational mass 100.3, the disk carrier 200 passes the torque M into the disk 210 via the first connection 215.
• the disk 210 introduces the torque M via the fourth gear 340 in the third gear 325 a. Due to the different effective radii r 2 , r 3 of the two gears 320, 325 of the planetary gear 290, the introduced via the third gear 325 torque M is translated to the second gear 320.
• the second toothing 320 introduces the torque M via the first toothing 315 a first portion of the torque in the intermediate mass 220.
• the planetary gear 290 initiates a second portion of the torque M translated into the planetary carrier 300.
• the planetary gear 290 thus acts as Momentenverzweigungseinnchtung and splits the torque to be transmitted M on the two torque transmission paths 75, 80.
• the torque M is forwarded by the first toothing 315 via the intermediate mass 220 to the first spring arrangement 120.1.
• the first spring arrangement 120.1 forms, in conjunction with the intermediate mass 220 and the side window 255, the phase shifter arrangement 130 from FIG.
• the torsional vibration is transmitted through the first torque transmission path 75 through the tuning of the spring arrangement 120.1 to the intermediate mass 220 and the side window 255 out of phase into the side window 255.
• the torque M is superimposed on the two torque transmission paths 75, 80.
• the superimposed torque M is coupled via the side window 255 in the second spring arrangement 120.2 frontally.
• the superimposed torque M is forwarded from the second spring arrangement 120.2 at a second end via the output part 270 into the hub 275.
• the torsional vibration damper 10 can be made particularly slim in the axial direction. the. Furthermore, the orientation of the center of gravity 335 away from the planetary gear axis 295 has a positive effect on vibration isolation of the torsional vibration damper 10. In particular, by means of a change in position of the center of mass 335 by the above-described design measures in the design of the planetary gear 290, for example by a thickening or thinning of the planetary gear 290 between the two gears 320, 325, the vibration isolation of the torsional vibration damper 10 are modified in a simple manner.
• a centrifugal force acting on the planetary gear 290 in the operation of the torsional vibration damper 10 in the design of the planetary gear 290 with regard to the position of the center of mass 335 must be taken into account.
• the position of the center of gravity 335 and the centrifugal force acting on the planetary gear 290 can be coordinated so that a biasing force is achieved on the planetary gear 290, so that a gear play between the first and second teeth 315, 320 and / or the third and fourth toothing 325, 340 is compensated by a continuous contact contact of the teeth 315, 320, 325, 340, so that a gearing rattling can be avoided.
• the planetary gear 290 can, for example, be machined from the solid, in particular milled. Alternatively, it is conceivable that the planetary gear 290 is forged (finished) lowered. It is also conceivable that the planetary gear 290 is punched from a sheet. It is also conceivable that the planetary gear 290 has multi-part layers in the axial direction, which are connected to one another in a positive and / or non-positive manner, for example.
• the planetary gear 290 is supported by means of the bearing 345.
• the bearing 345 may be formed as a rolling bearing, as shown in Figure 3.
• the bearing 345 is designed as a sliding bearing.
• planetary gears 290 are distributed circumferentially at regular intervals in recesses 305 arranged regularly corresponding to the planetary gears 290.
• the first recess 305 and the corresponding planet gears 290 are arranged at irregular intervals.
• FIG. 4 shows a semi-longitudinal section through a torsional vibration damper 10 according to a second embodiment.
• FIG. 5 shows a cross section along a sectional plane B-B shown in FIG. 4 through the torsional vibration damper 10 shown in FIG. 4.
• the torsional vibration damper 10 is similar to the torsional vibration damper 10 shown in FIGS.
• the torque flow between the plate carrier 200 and the output side 25 is identical.
• the disk carrier bottom 205 is designed to be shortened radially inwards.
• the disk 210 which is arranged on the disk support base 205 and designed as a second gear part has a second cutout 400.
• the second recess 400 has a second recess contour 405, which is similar to the first recess contour 310 of the first recess 305.
• the second recess 400 has the fourth toothing 340.
• the fourth toothing 340 engages in the second toothing 320 of the planetary gear 290 and is therefore arranged radially in relation to the planetary gear axis 295 to the planetary gear axis 295.
• the cutout contours 405, 310 are arranged spaced apart radially from the outside of the planetary gear 290, so that the second toothing 320 has no contact contact radially outside the cutout contours 405, 310 of the two cutouts 305, 400. For this reason, the second toothing 320 of the planetary gear 290 could also be dispensed with in a particularly cost-effective embodiment.
• the torque transmission takes place on the planetary gear 290 exclusively via the third toothing 325.
• the disk carrier 200 can be arranged particularly close to the intermediate mass 220 in the axial direction.
• FIG. 6 shows a semi-longitudinal section through a torsional vibration damper 10 according to a third embodiment.
• the torsional vibration damper 10 is substantially identical to the torsional vibration damper 10 shown in FIGS. 4 and 5.
• the fourth toothing 340 is related to the pia Netenradachse 295 arranged radially outside to the planetary gear 295 and to the planet carrier 300.
• the fourth toothing 340 has a meshing engagement with the third toothing 325 of the planetary gear 290.
• the fourth toothing 340 is thus formed corresponding to the third toothing 325.
• FIGS. 1 shows a semi-longitudinal section through a torsional vibration damper 10 according to a third embodiment.
• the torsional vibration damper 10 is substantially identical to the torsional vibration damper 10 shown in FIGS. 4 and 5.
• the fourth toothing 340 is related to the pia Netenradachse 295 arranged radially outside to the planetary gear 295 and to
• the first toothing 315 is still arranged radially inward of the planetary gear axis 295 and the planetary gear 290 and has a meshing engagement with the second toothing 320 of the planetary gear 290.
• Figure 7 shows a semi-longitudinal section through a torsional vibration damper 10 according to a fourth embodiment.
• the torsional vibration damper 10 is formed substantially identical to the torsional vibration dampers 10 shown in FIGS. 4 to 6.
• the first toothing 315 and the fourth toothing 340 are arranged on the inner circumferential surfaces of the recesses 305, 400, radially with respect to the planetary gear axis 295, on the outside of the planetary gear axis 295.
• the first toothing 315 also has a meshing engagement with the third toothing 325.
• the cutout contours 405, 310 are arranged radially on the inside on a peripheral surface of the recesses 305, 400, which is oriented radially outwards, and are arranged at a distance from the second toothing 320.
• Figure 8 shows a semi-longitudinal section through a torsional vibration damper 10 according to a fifth embodiment.
• the torsional vibration damper 10 is substantially identical to the torsional vibration dampers 10 shown in FIGS. 2 to 7, and is in particular a combination of the torsional vibration damper 10 shown in FIGS. 4 and 5 and 7.
• the disk 210 is identical to that in FIGS. 4 and 5 formed disc 210 so that the fourth gear 340 is arranged radially inwardly to the planetary gear 295 and the planetary gear 290 arranged.
• the second recess 400 with its recess contour 405 is arranged at a distance from the third toothing 325.
• the intermediate mass 220 is identical to the intermediate mass 220 shown in FIG. 7, so that the first toothing 315 is radially outward of the Planetenradachse 295 is arranged and has a meshing engagement with the third toothing 325 of the planetary gear 290.
• the transmission ratio of the transmission device 65 and thus the distribution of the torques M on the two torque transmission paths 75, 80 can be determined in a simple manner.
• a friction device 500 can be provided.
• the friction device 500 has a first friction surface 505 and a second friction surface 510.
• the first friction surface 505 is arranged in the embodiment on the disc 210 frontally.
• the second friction surface 510 is arranged on the front side on the first intermediate mass part 225 on a side facing the plate carrier 200 end face.
• the friction surfaces 505, 510 are pressed against each other by means of a tensioning device (not shown), so that the friction surfaces 505, 510 have a frictional engagement and a torque transmission can take place via this friction engagement.
• the friction device 500 By transmitting the torque M via the two torque transmission paths 75, 80, the friction device 500 causes a tension of the intermediate mass 220 to the plate carrier 200, a tension of the planetary gear 290 relative to the plate carrier 200 and the intermediate mass 220 and a strain and thus a strain of the first Torque transmission path 75 relative to the second torque transmission path 80, so that a teeth clearance is compensated and the teeth 315, 320, 325, 340 abut each other in the operation of the torsional vibration damper 10 in order to avoid gearing rattling.
• first friction surface 505 and / or the second friction surface 510 can be coupled with at least the planetary gear 290 and / or the intermediate mass 220 and / or the translation device 65 and / or the torque coupling device 70 and / or the planet carrier 300 in a torque-locking manner ,
• the tension for example, a bearing clearance of the bearing 345 of the planetary gear 290 balanced.
• the vibration behavior and / or the damping behavior of the torsional vibration damper 10 can be influenced by the friction device 500.
• a tensioning device is particularly suitable a plate spring or a compression spring.
• other embodiments of the bracing device are also conceivable, for example, annular elements, in particular compensating rings, would be possible in this case.
• the bracing device can be arranged, for example, axially between the intermediate mass 220 and the first side window 250.
• the friction surfaces 505, 510 are annular in the embodiment. Of course, it is also conceivable that the friction surfaces 505, 510 differently, for example, on a peripheral side, are arranged. Furthermore, it is conceivable that the friction device 500 is supplemented by components suitable for the friction device 500, such as a friction lining, plastic parts and coatings.
• the friction device 500 is arranged on other components of the torsional vibration damper 10.
• the friction device 500 is arranged on other components of the torsional vibration damper 10.
• Friction device 500 on the planet gear 290, the planet carrier 300, the hub 275 or the side window 255 is arranged.
• gears 315, 320, 325, 340 are also arranged at a different position. Furthermore, it is also conceivable for the disk 210, the intermediate mass 220 and / or the side window 255 to accommodate additional functions.

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

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Citations (4)

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• 2014
  • 2014-07-02 DE DE102014212825.0A patent/DE102014212825A1/de not_active Withdrawn
• 2015
  • 2015-06-24 WO PCT/DE2015/200390 patent/WO2016000708A1/de active Application Filing
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