WO2019192644A1 - Pendule centrifuge et système d'entraînement comprenant un tel pendule centrifuge - Google Patents

Pendule centrifuge et système d'entraînement comprenant un tel pendule centrifuge Download PDF

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Publication number
WO2019192644A1
WO2019192644A1 PCT/DE2019/100208 DE2019100208W WO2019192644A1 WO 2019192644 A1 WO2019192644 A1 WO 2019192644A1 DE 2019100208 W DE2019100208 W DE 2019100208W WO 2019192644 A1 WO2019192644 A1 WO 2019192644A1
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WO
WIPO (PCT)
Prior art keywords
pendulum
flange
centrifugal pendulum
coupling
mass
Prior art date
Application number
PCT/DE2019/100208
Other languages
German (de)
English (en)
Inventor
Christian Dinger
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
Priority to DE112019001770.5T priority Critical patent/DE112019001770A5/de
Priority to CN201980017149.1A priority patent/CN111819372B/zh
Publication of WO2019192644A1 publication Critical patent/WO2019192644A1/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
    • 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
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range
    • 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
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/1464—Masses connected to driveline by a kinematic mechanism or gear system
    • F16F15/1471—Masses connected to driveline by a kinematic mechanism or gear system with a kinematic mechanism, i.e. linkages, levers

Definitions

  • the invention relates to a torque transmission device according to patent claim 1 and a drive system according to claim 10.
  • the torque transmission device couples the drive motor with a transmission device.
  • the drive motor is designed as a reciprocating piston engine and has a cylinder deactivation, so that in a first operating state the drive motor provides a torque by supplying all the cylinders with fuel. In cylinder deactivation operation, only part of the cylinders are supplied with fuel, so that the available torque through the drive motor is lower.
  • an improved centrifugal pendulum can be provided by rotatably supporting the centrifugal pendulum about a first axis of rotation, wherein the centrifugal pendulum has a first centrifugal pendulum unit and a second centrifugal pendulum unit and a connecting flange, wherein the connecting flange with a torque transmitting device can be coupled to a drive system, wherein the first centrifugal pendulum unit comprises a pendulum mass and a first slotted guide, wherein the pendulum mass is coupled by means of the first Kulis senment with the connecting flange and the first slotted guide is formed at a initiation of rotational nonuniformity in the connection flange to guide the pendulum mass along a first aerial tramway.
  • the second centrifugal pendulum unit has at least one partially ring-shaped flywheel unit. mass, a coupling rocker arm, a second slotted guide and a coupling device, wherein the coupling device is arranged and configured in the circumferential direction offset from the first and second slotted guide, to support the coupling rocker rotatable about a second axis of rotation extending parallel to the first axis of rotation.
  • the second slotted guide couples the coupling rocker with the flywheel and is designed to guide the coupling rocker along the introduction of rotational nonuniformity in the connection flange along a second pendulum track.
  • the centrifugal force pendulum is suitable in particular for drive systems with a drive engine with cylinder deactivation, since the first centrifugal pendulum unit thereby responds to a first excitation order of the drive motor in a first operating state in which all the cylinders of the drive engine are activated , is tunable.
  • the second centrifugal pendulum unit may be tuned to a second exciter order of the drive motor in a second operating state, for example in which a part of the cylinder is deactivated and thus the cylinder deactivation is activated. This avoids that in the second operating state, the pendulum mass of the first coupling device can oscillate in opposite directions to a rotation uniformity along the first pendulum mass. However, this is avoided by the second centrifugal pendulum unit, so that a reliable eradication of rotational irregularities is ensured even in the second operating state, in particular by the second centrifugal pendulum unit.
  • the first centrifugal pendulum unit has a first tuning order and the second centrifugal pendulum unit has a second tuning order, wherein the first tuning order and the second tuning order are substantially identical, or wherein the first tuning order is different from the second tuning order , wherein preferably the first voting order is greater than the second voting order.
  • the coupling rocker and the pendulum mass are offset in the circumferential direction, preferably arranged on a common circular path about the first axis of rotation. Additionally or alternatively, the coupling rocker is arranged in a radial direction offset from the pendulum mass. Preferably, the head The rocker arm is arranged radially on the inside or radially outside of the pendulum mass. In addition or as an alternative, the coupling rocker and the pendulum mass are arranged overlapping in the radial direction.
  • At least sections Wese the flywheel is arranged in the radial direction between the coupling rocker and the pendulum mass. Additionally or alternatively, the flywheel is arranged radially outside the coupling rocker and / or the pendulum mass. Additionally alternatively
  • the flywheel is arranged radially on the inside to the coupling rocker and / or the pendulum mass.
  • the connecting flange has a first recess and a web which at least partially delimits the first recess in the circumferential direction, the coupling rocker being arranged at least in sections in the first recess.
  • the coupling device connects the coupling rocker with the web.
  • connection flange has a first flange part and a second flange part.
  • the first flange is at least partially arranged axially offset from the second flange and rotatably connected to the second flange.
  • the coupling rocker and / or the flywheel and / or the pendulum mass is arranged axially between the first flange part and the second flange part.
  • the flywheel has a further recess, wherein preferably the further recess is open radially outwards.
  • the further recess is arranged offset in the circumferential direction to the coupling rocker.
  • the pendulum mass is arranged.
  • the connecting flange has a bearing section extending in the axial direction, wherein the bearing section extends radially inwardly. is arranged tig to the flywheel, wherein the flywheel is rotatably mounted about the first axis of rotation relative to the connecting flange radially outwardly on the bearing portion.
  • the pendulum mass has at least one pendulum mass part and at least one additional pendulum mass part, the pendulum mass being coupled to the connecting flange by means of the first slotted guide, where the pendulum mass part is connected in the additional pendulum mass part.
  • a drive system for a motor vehicle has a drive motor and a centrifugal pendulum, wherein the centrifugal pendulum as described above is formed, wherein the drive motor is designed as a piston engine and has at least two cylinders, wherein in a first operating state of the drive motor both cylinders are activated and supplied with fuel, wherein in a second operating state of the drive motor one of the two cylinders deactivated and the fuel supply to the deactivated cylinder is interrupted, wherein in the first operating state of the drive motor, a first exciter order and in the second operating state of the drive motor for the first exciter order different second excitation order, wherein the first order of votes is substantially equal to the first excitation order and the second order of coordination is substantially equal to the second order of excitement.
  • Figure 1 is a schematic representation of a drive system for a
  • FIG. 2 shows a cross section through a centrifugal pendulum 135 according to a first
  • FIG. 3 shows a sectional view along a first shown in FIG.
  • FIG. 4 shows a sectional view along a second one shown in FIG
  • Figure 5 shows a cross section through a centrifugal pendulum according to a second
  • FIG. 6 shows a sectional view along a sectional plane C-C shown in FIG. 5 through the centrifugal force pendulum shown in FIG. 5;
  • FIG. 7 shows a cross section through a centrifugal pendulum according to a third
  • FIG. 8 shows a sectional view along a sectional plane D-D shown in FIG. 7 through the centrifugal force pendulum shown in FIG. 7;
  • FIG. 9 shows a sectional view along a sectional plane E-E shown in FIG. 7 through the centrifugal force pendulum shown in FIG. 7;
  • FIG. 10 shows a cross section through a centrifugal pendulum according to a fourth
  • Figure 1 1 is a sectional view taken along a section plane F-F shown in Figure 10 by the centrifugal pendulum shown in Figure 10;
  • FIG. 12 shows a sectional view along the sectional plane F-F shown in FIG. 10 through a centrifugal pendulum according to a fourth embodiment
  • FIG. 13 shows a sectional view along the sectional plane F-F shown in FIG. 10 through a centrifugal pendulum according to a fifth embodiment
  • FIG. 14 shows a sectional view along the sectional plane FF shown in FIG. 10 through a centrifugal pendulum according to a sixth embodiment
  • Figure 15 is a sectional view taken along the section plane FF shown in Figure 10 by a centrifugal pendulum according to a seventh embodiment.
  • FIG. 16 shows a sectional view along the sectional plane F-F shown in FIG.
  • Figure 17 is a sectional view taken along the sectional plane F-F shown in Figure 10 by a centrifugal pendulum according to a tenth embodiment
  • FIG. 18 shows a development of the coupling rocker shown in FIG. 8;
  • FIG. 19 shows a development of the first centrifugal pendulum unit shown in FIG. 9; FIG. and
  • FIG. 20 is a development of the first centrifugal pendulum unit shown in FIG.
  • FIG. 1 shows a schematic representation of a drive system 10 for a motor vehicle.
  • FIG. 1 is designed in the manner of a circuit diagram.
  • differently sized rotational masses are represented symbolically in FIG. 1 by means of boxes.
  • a substantially stiff torque transmission is represented symbolically by straight lines.
  • Wavy lines represent spring devices.
  • Semicircular symbols represent pump or turbine wheels.
  • the drive system 10 comprises a torque transmission device 15 and a drive motor 20.
  • the drive motor 20 is designed as a reciprocating piston engine.
  • the drive motor 20 comprises a first cylinder 25 and at least one second cylinder 30.
  • the two cylinders 25, 30 are connected to a fuel supply 35.
  • a piston 40 is provided in each case, which is in each case coupled via a connecting rod 45 with a crankshaft 50.
  • the crankshaft 50 is coupled with an output side of the drive motor 20 torque-locking.
  • the piston 40 makes a linear alternating movement in the cylinder 25, 30 during operation of the drive motor 20.
  • the drive motor 20 has a first operating state and a second operating state.
  • the cylinders 25, 30 are coupled to the fuel supply 35, so that fuel is conveyed from the fuel supply 35 into the cylinders 25, 30 at regular intervals in order to store the fuel together with atmospheric oxygen in the cylinder 25, 30 to burn.
  • the piston 40 of the corresponding cylinder 25, 30 is displaced downward in FIG. 1 and a torque is provided on the crankshaft 50.
  • the drive motor 20 has a first excitation order m.
  • the excitation order n corresponds to half of the cylinder (BZ?) Of the drive motor 20 in operation.
  • the second operating state at least one of the two cylinders 25, 30 is disconnected from the fuel supply 35, and thus the corresponding cylinder 25, 30 is switched off.
  • the second operating state is selected in particular when the drive motor 20 has to provide only a low power.
  • the torque transmission device 15 comprises an input side 55, an output side 60, a series damper 65, a clutch 70 and a hydrodynamic converter 75.
  • the clutch 70 is switchable and, in the closed state, connects the input side 55 to the output side 60 of the torque transmission device 15 in a torsionally torque-locking manner.
  • the clutch 70 is formed as a lock-up clutch.
  • the hydrodynamic converter 75 comprises an impeller 80 and a turbine wheel 85.
  • the impeller 80 is connected to the input side 55 and the turbine 85 is connected to the output side 60 in a torque-locking manner.
  • the turbine wheel 85 comprises a coupling flange 110 and a turbine wheel part 86.
  • a liquid is provided in the converter 75. In the open state of the clutch 70, the converter 75 connects the input side 55 to the output side 60 for torque transmission.
  • the series damper 65 comprises a first spring device 90, an intermediate flange 95, a second spring device 100 and an input flange 105.
  • the input flange 105 is connected to a clutch output side of the clutch 70.
  • the coupling flange 110 is rotationally connected to the turbine wheel 85 of the converter 75.
  • the first spring device 90 is arranged between the input flange 105 and the intermediate flange 95.
  • a first end 115 of the first spring device 90 is coupled to the input flange 105 and a second end 120 of the first spring device is coupled to the intermediate flange 95.
  • the intermediate flange 95 is coupled on the output side to a first end 125 of the second spring device 100.
  • a second end 130 of the second spring device 100 is coupled to the coupling flange 110.
  • the torque transmission device 15 comprises a centrifugal pendulum 135 with a first centrifugal pendulum unit 140 and a second centrifugal pendulum unit 145.
  • the centrifugal pendulum 135 is arranged, for example, on the intermediate flange 95.
  • the centrifugal pendulum 135 may also be coupled to the turbine wheel 85, the coupling flange 110 or the input flange 105.
  • the torque transmitting device 15 may be formed differently.
  • the series damper 65 or instead of the series damper 65, a simple (torsional) damper is provided.
  • the hydrodynamic converter 75 can be dispensed with.
  • FIG. 2 shows a cross section through a centrifugal pendulum 135 according to a first embodiment.
  • the centrifugal pendulum 135 has a connection flange 150 in addition to the first centrifugal pendulum unit 140 and the second centrifugal pendulum unit 145.
  • the connection flange 150 is non-rotatably connected in the embodiment with the intermediate flange 95.
  • the connection of the connecting flange 150 with the intermediate flange 95 can take place, for example, radially on the inside of the connecting flange 150.
  • a respective first centrifugal pendulum unit 140 and a second centrifugal pendulum unit 145 are alternately provided in the circumferential direction.
  • the centrifugal pendulum pendulum 135 has two first centrifugal pendulum units 140 arranged opposite one another in the radial direction and two second centrifugal pendulum units 145.
  • the centrifugal pendulum 135 is rotatably mounted about a first axis of rotation 155.
  • the first centrifugal pendulum unit 140 has a pendulum mass 160 and a first slide guide 165.
  • the first pendulum mass 160 is coupled to the connecting flange 150 by means of the first slide guide 165.
  • the first slide guide 165 when introducing rotational nonuniformity from the drive motor 20 into the connection flange 150, guides the pendulum mass 160 along a first pendulum track 170.
  • the first pendulum track 170 together with a mass of the pendulum mass 160, determines a first tuning order of the first centrifugal pendulum unit 140 It is of particular advantage if the first tuning order of the first centrifugal pendulum unit 140 matches the first excitation pattern of the drive motor 20. In other words, the first voting order essentially corresponds to the first ordering order. In other words, the first centrifugal pendulum unit 140 is tuned in its first coordination order to the first excitation order of the drive motor 20 in the first operating state.
  • the second centrifugal pendulum unit 145 which is formed as Isoradialpendel, has a second tuning order. It is particularly advantageous if the second tuning order substantially corresponds to the second excitation order r2 of the drive motor 20, so that even in the second operating state, rotational nonuniformities in the torque of the drive motor 20 can be reliably canceled out.
  • the second centrifugal pendulum unit 145 is suitable for rotational irregularities with a low excitation order n, for example 1, 0 or 1, 5, so that in the second operating state, the rotational nonuniformities can thereby be removed particularly well.
  • the first centrifugal pendulum unit 140 is particularly suitable for exciter orders n for eradication with higher tuning orders, in particular exciter orders n, which are larger than the second exciter order r ⁇ 2.
  • the combination of the first centrifugal pendulum unit 140 with the second centrifugal pendulum unit 145 is characterized in that at low excitation orders n, for example, 1, 0 or 1, 5, the first centrifugal pendulum unit 140 tends to antiphase swinging, however, in a coupling with the first centrifugal pendulum unit 140 with the second centrifugal pendulum unit 145 this can be avoided.
  • the first slide guide 165 has, for example, a plurality of exemplary two first slides 166 in FIG. 2, which are arranged in the first pendulum mass 160.
  • the first slide guide 166 is kidney-shaped and has a first center of curvature, which is arranged radially outside the first slide 166. Shown in broken lines in FIG. 2, the first slide guide 165 also has a second slide 167, which is arranged in the connecting flange 150.
  • the number of the first scenes 166 and the second scenes 167 is identical.
  • the second link 167 has, for example, a kidney-shaped configuration and has a second center of curvature, wherein the second center of curvature is arranged radially inwards to the second link 167.
  • the first slide guide 165 has a first guide roller 168, wherein the first guide roller 168 engages through the first slide 166 and the second slide 167.
  • the first guide roller 168 is in operation of the centrifugal pendulum 135 at the first link 166 and the second link 167 and performs the first pendulum mass 160 upon initiation of nonuniformity, preferably the torsional vibration in the connecting flange 150, along the first pendulum track 170th
  • the second centrifugal pendulum unit 145 has a flywheel mass 175 formed at least partially in the form of a ring, a coupling rocker arm 180, a second slide guide 185 and a coupling device 190.
  • the connecting flange 150 has a first recess 195 on.
  • the first recess 195 is exemplarily opened radially outwards and is larger than a movement space which the coupling rocker 180 requires.
  • the coupling rocker 180 is arranged.
  • the first recess 195 extends on a circular path around the first axis of rotation 155. In the circumferential direction, the first recess 195 is bounded in each case by a web 200, wherein the first centrifugal pendulum unit 140 is arranged on the web 200.
  • the second link 167 is preferably arranged in the web 200.
  • the web 200 has on one side a bulge 205, which projects into the first recess 195.
  • the coupling device 190 is arranged and connects the coupling rocker 180 at one end to the web 200.
  • the coupling rocker 180 extends essentially on a first circular path 191 about the first axis of rotation 155.
  • the pendulum mass 160 is also arranged on the first circular path 191.
  • the coupling device 190 may be formed as a rotary joint.
  • the coupling device 190 rotatably connects the coupling rocker 180 about a second rotation axis 210. Relative to the second rotation axis 210, the coupling device 190 guides the coupling rocker 180 on a second circular path configured as a second pendulum track 215 about the second rotation axis 210.
  • the second rotation axis 210 is disposed radially outwardly toward the first axis of rotation 155.
  • the first rotation axis 155 and the second rotation axis 210 are parallel.
  • FIG. 3 shows a sectional view along a first cutting plane A-A shown in FIG. 2 through the centrifugal force pendulum 135 shown in FIG.
  • the second link guide 185 has a third link 220 arranged in the flywheel 175, a fourth link 225 arranged in the coupling link 180 and a second guide roller 230.
  • the third gate 220 is kidney-shaped and has a curvature about a third center of curvature, wherein the third center of curvature is arranged radially inwardly to the third gate 220 (the third gate 220 is shown in broken lines in FIG. 2).
  • the fourth link 225 is kidney-shaped and has a curvature with a fourth center of curvature, wherein the fourth center of curvature radially outwardly to the fourth Setting 225 is arranged.
  • the third link 220 and the fourth link 225 are penetrated by the second guide roller 230, wherein the second guide roller 230 abuts against the third link 220 and the fourth link 225 during operation of the centrifugal force pens 135 and upon initiation of rotational nonuniformity in the connecting flange 150 rolls on the third and fourth scenery 220, 225.
  • the second link guide 185 guides the coupling rocker 180 along the second pendulum track 215, wherein the second pendulum track 215 runs on the second circular track about the second axis of rotation 210 in relation to the bridge 200.
  • the flywheel 175 When guided along the second pendulum track 215, the flywheel 175 performs a pendulum motion in the circumferential direction on the first circular path 191 and thus moves coaxially with the first axis of rotation 155.
  • the flywheel 175 has a first one
  • the connecting means 245 couples the first flywheel mass part 235 to the second flywheel mass part 240 and thereby passes through a second cutout 250 in the connecting flange 150.
  • the first flywheel mass part 235 and the second flywheel mass part 240 are in the axial direction with respect to FIG first axis of rotation 155 offset from one another and arranged on both sides of the connecting flange 150.
  • the first flywheel mass part 235 is formed radially shorter on the inside than the second flywheel mass part 240.
  • the second flywheel mass part 240 has a first bearing surface 255.
  • the first bearing surface 255 is formed cylindrically with respect to the first axis of rotation 155.
  • the connection flange 150 has a ring-shaped radial section 260 and a bearing section 265, the radial section 260 extending in the radial direction in a plane of rotation perpendicular to the first axis of rotation 155.
  • Axially on a second flywheel mass part 240 side facing the bearing portion 265 is attached to the radial portion 260.
  • the bearing portion 265 extends perpendicular to the radial portion 260 in the axial direction.
  • Radially on the outside, the bearing section 265 has a second bearing surface 270. On the second bearing surface 270, the first bearing surface 255 is applied, so that thereby the flywheel 175 is rotatably mounted about the first axis of rotation 155 on the bearing portion 265.
  • FIG. 4 shows a sectional view along a second cutting plane BB shown in FIG. 2 through the centrifugal force pendulum 135 shown in FIG.
  • the flywheel 175 has a third recess 275 radially on the outside.
  • the third recess 275 is open radially outward.
  • the pendulum mass 160 is arranged in the third recess 275.
  • the first centrifugal pendulum unit 140 is formed as a conventional outboard centrifugal pendulum.
  • the first pendulum mass 160 has a first pendulum mass part 280 and a second pendulum mass part 285, which are connected to each other in the axial direction.
  • the first pendulum mass part 280 and the second pendulum mass part 285 are arranged on both sides of the connecting flange 150.
  • the first centrifugal pendulum unit 140 would be designed as internally formed centrifugal pendulum, for example, the flange 150 has two flange portions which are axially offset from each other in sections, wherein in the area where the flange of the flange 150 offset are arranged to each other, the pendulum mass 160 is arranged.
  • Figure 5 shows a cross section through a centrifugal pendulum 135 according to a second embodiment.
  • the centrifugal force pendulum 135 is essentially identical to the centrifugal pendulum 135 shown in FIGS. 2 to 4. In the following, only the deviations of the centrifugal force pendulum 135 shown in FIG. 5 from the centrifugal pendulum 135 shown in FIGS. 2 to 4 will be discussed.
  • the first centrifugal pendulum unit 140 is disposed radially outward of the second centrifugal pendulum unit 145.
  • the coupling rocker 180 and the first pendulum mass 160 are arranged overlapping.
  • a radial overlap is understood to mean that in the case of a projection of two components, for example 5, the coupling rocker 180 and the first pendulum mass 160 in a cylindrical projection plane, which runs around the first axis of rotation 155, overlap in the radial direction the two components in the projection plane.
  • the first pendulum mass 160 is arranged in the circumferential direction on one side nearer to the web 200 on which the coupling rocker 180 arranged radially on the inside to the first pendulum mass 160 is connected to the web 200 via the coupling device 190.
  • first centrifugal pendulum units 140 are arranged on the first circular path 191, which are arranged offset from one another in the circumferential direction.
  • the first centrifugal pendulum units 140 are each formed identical to each other.
  • four first centrifugal pendulum units 140 are provided by way of example.
  • the number of first centrifugal pendulum units 140 shown in FIG. 5 is exemplary. In particular, it would also be conceivable that three, five or six first centrifugal pendulum units 140 are provided.
  • a second centrifugal force pinning unit 145 is provided for each first centrifugal pendulum unit 140 radially on the inside of the first centrifugal pendulum unit 140, the second centrifugal pendulum units 145 being offset in the circumferential direction.
  • the first centrifugal pendulum unit 140 is arranged radially outwardly and radially overlapping each to a second centrifugal pendulum unit 145.
  • the connection flange 150 has a first section 290 arranged radially on the inside and a second section 296 arranged radially on the outside.
  • the second section 296 and the first section 290 are designed to extend in a ring around the first axis of rotation 155.
  • the second section 295 is connected radially to the first section 290 via the web 200 (preferably a plurality of circumferentially offset webs 200).
  • the first recesses 195 are arranged, which in the embodiment are closed radially on the outside by the second section 295.
  • the first recesses 195 are in the embodiment substantially part-annular passage openings.
  • FIG. 6 shows a sectional view along a sectional plane CC shown in FIG. 5 through the centrifugal force pendulum 135 shown in FIG.
  • the flywheel mass 175 is shorter in the radial direction than shown in FIGS. 3 and 4.
  • the first centrifugal pendulum unit 140 is arranged radially on the outside of the flywheel mass 175 so that the third recess 275 can be omitted radially on the outside.
  • the flywheel 175 extends radially outwardly web-shaped.
  • the first centrifugal pendulum unit 140 and the flywheel mass 175 are formed substantially equally wide in the axial direction, so that a particularly slim design of the centrifugal force pendulum 135 can be provided in the axial direction.
  • first flywheel mass part 235 and / or the second flywheel mass part 235 is slimmer in the axial direction than the first first pendulum mass part 280 arranged radially outside the first flywheel mass part 235 and / or radially outside the second flywheel mass part 240 second pendulum mass part 285.
  • This embodiment ensures that in the axial direction between the first flywheel mass part 235 and the second flywheel mass part 240 there is enough space for a coupling rocker 180 that is particularly wide in the axial direction.
  • the coupling rocker 180 can be made wider in the axial direction than the radial section 260 of the connecting flange 150.
  • Figure 7 shows a cross section through a centrifugal pendulum 135 according to a third embodiment.
  • the flange 150 and the flywheel 175 are reversed.
  • the flywheel mass 175 of FIG. 7 is essentially identical to the connection flange 150 described in FIGS. 2 and 4.
  • the connecting flange 150 shown in FIG. 7 is designed in accordance with the flywheel mass 175 described in FIGS. 2 to 4.
  • the web 200 is narrow in the circumferential direction in relation to the web 200 shown in FIGS. 2 to 4.
  • the web 200 is arranged substantially in the circumferential direction between the coupling rocker 180 and the pendulum mass 160.
  • the coupling rocker 180 and the pendulum mass 160 alternate in the circumferential direction.
  • the first recess 195 and the third recess 175 merge directly into one another.
  • a recess 291 between the two recesses 175, 195 in the circumferential direction centrally may be provided, wherein the indentation 291 in the radial direction has a smaller depth than the web 200 has a radial extent - points.
  • the indentation 291 is arranged substantially in the circumferential direction between the coupling rocker 180 and the first pendulum mass 160.
  • FIG. 8 shows a sectional view along a sectional plane D-D shown in FIG. 7 through the centrifugal force pendulum 135 shown in FIG.
  • connection flange 150 is formed in two parts, so that the connection flange 150 has a first flange part 295 and a second flange part 300, wherein the second flange part 300 is wider in the radial direction on the inside than the first flange part 295.
  • the first and second Flange portion 295, 300 are formed disc-shaped with respect to the first axis of rotation 155 and each extending substantially in planes of rotation perpendicular to the first axis of rotation 155.
  • Radially inside of the second flange portion 300 of the bearing portion 265 is arranged, which extends in the axial direction in the direction of the first flange portion 295.
  • the first flange part 295 and the second flange part 300 are rotatably connected to each other.
  • Radially outside the bearing section 265, the flywheel mass 175 is rotatably mounted on the bearing section 265.
  • the flywheel 175 is annular and integrally formed.
  • the flywheel mass 175 is arranged in the axial direction between the first flange part 295 and the second flange part 300.
  • the third slide 220 are provided for each flange part 295, 300, respectively.
  • the third backdrop 220 is in the axial direction opposite in both flange 295, 300 arranged.
  • On the provision of the third gate 220 in the flywheel 175 is omitted in the embodiment.
  • the third slide 220 and the fourth slide 225 are penetrated by the second guide roller 230.
  • FIG. 9 shows a sectional view along a sectional plane E-E shown in FIG. 7 through the centrifugal force pendulum 135 shown in FIG.
  • the first centrifugal pendulum unit 140 is formed as an internal centrifugal pendulum 135 in the embodiment.
  • the first pendulum mass 160 is integrally formed of the same material and arranged between the first flange portion 295 and the second flange portion 300 in the axial direction.
  • the first slide guide 165 has in each case two second slides 167, which are formed opposite one another in the axial direction and identical to one another, and which are passed through by the first guide roller 168 in each case.
  • FIG. 10 shows a cross section through a centrifugal pendulum 135 according to a fourth embodiment.
  • the centrifugal force pendulum 135 is essentially a combination of the centrifugal pendulum 135 explained in FIGS. 5 and 6 and the centrifugal pendulum 135 explained in FIGS. 7 to 9.
  • the connecting flange 150 and the flywheel 175 are interchanged.
  • the flywheel mass 175 of FIG. 10 is essentially identical to the connection flange 150 described in FIGS. 5 and 6.
  • the connection flange 150 shown in FIG. 10 is designed according to the flywheel 175 described in FIGS. 5 and 6.
  • the first section 290 is made slimmer in the radial direction with respect to the embodiment of the centrifugal force pendulum 135 shown in FIG. 5, so that the flywheel mass 175 has a lower mass moment of inertia.
  • FIG. 11 shows a sectional view along a sectional plane F - F shown in FIG. 10 through the centrifugal force pendulum 135 shown in FIG.
  • the first section 290 is arranged radially inward to the coupling rocker 180 and has radially on the inside the first bearing surface 255, with which the ring section 206 is mounted on the second bearing surface 270 of the bearing section 265 of the connecting flange 150.
  • the coupling rocker 180 is made wider in the axial direction than the flywheel 175. Furthermore, the coupling rocker 180 is designed in several parts.
  • an element 310 can be arranged radially on the inside of the coupling rocker shown in FIGS. 7 to 9 on the coupling rocker 180, the element 310 being connected to the coupling rocker 180. By the element 310, a mass of the coupling rocker 180 can be increased.
  • FIG. 12 shows a sectional view along the sectional plane F-F shown in FIG. 10 through a centrifugal pendulum 135 according to a fifth embodiment.
  • the centrifugal pendulum 135 is formed substantially identical to the centrifugal pendulum 135 shown in Figures 10 and 11. Deviating from this, the coupling rocker 180 is formed in one piece and of the same material. Further, by way of example, the axial extent of the pendulum mass 160 and the coupling rocker 180 is identical.
  • FIG. 13 shows a sectional view along the sectional plane F-F shown in FIG. 10 through a centrifugal pendulum 135 according to a sixth embodiment.
  • the centrifugal pendulum 135 is formed substantially identical to the centrifugal pendulum 135 shown in FIG. Deviating from this, the first portion 290 of the flywheel 175 is arranged radially outside the coupling rocker 180. Thus, the first portion 290 is in the radial direction between the pendulum mass 160 and the coupling rocker 180.
  • the web 200 (not shown in Figure 13) extends radially from outside to inside.
  • the first recess 195 is also arranged radially on the inside and radially inwardly toward the flywheel 175.
  • FIG. 14 shows a sectional view along the sectional plane FF shown in FIG. 10 through a centrifugal pendulum 135 according to a seventh embodiment.
  • the centrifugal pendulum 135 is formed substantially identical to the centrifugal pendulum 135 shown in FIG. Deviating from this, the coupling rocker 180 is arranged radially outside the first section 290. Furthermore, the web 200 extends in the radial direction from the first portion 290 to the outside. Radially inside to the first section, the first centrifugal pendulum unit 140 is arranged with the pendulum mass 160.
  • FIG. 15 shows a sectional view along the sectional plane F-F shown in FIG. 10 through a centrifugal pendulum 135 according to an eighth embodiment.
  • the centrifugal force pendulum 135 is substantially identical to the centrifugal pendulum 135 explained in FIG.
  • the centrifugal force pendulum 135 shown in FIG. 15 is essentially a combination of the centrifugal force pendulum 135 explained in FIGS. 13 and 14.
  • the first section 290 of the flywheel 175 is arranged radially outward of the coupling rocker 180.
  • the web 200 thus extends from radially outward to radially inward direction.
  • the coupling rocker 180 is arranged in the radial direction between the pendulum mass 160 and the ring portion 206.
  • FIG. 16 shows a sectional view along the sectional plane F-F shown in FIG. 10 through a centrifugal pendulum 135 according to a ninth embodiment.
  • the second flange part 300 is wider in the radial direction than the first flange part 295. In this case, the second flange part 300 projects radially beyond the first flange part 295 and does not end radially, as shown in FIGS. 10 to 15 same fleas with the first flange 295th
  • the first centrifugal pendulum unit 140 is designed in the manner of an external centrifugal force pennel.
  • the design of the first centrifugal pendulum unit 140 corresponds to the embodiment explained in Figure 4, but deviating to the second Gate 167 is disposed in the second flange 300.
  • the two pendulum mass parts 280, 285 are thus arranged on both sides in the axial direction of the second flange part 300.
  • the coupling rocker 180 is, as shown in FIGS. 7 to 15, arranged between the first flange part 295 and the second flange part 300.
  • the first section 290 is arranged radially inward to the coupling rocker 180 and, as explained in FIG. 11, is mounted on the bearing section 265 with the first bearing surface 255.
  • FIG. 17 shows a sectional view along the sectional plane F-F shown in FIG. 10 through a centrifugal pendulum 135 according to a tenth embodiment.
  • the centrifugal pendulum 135 is formed substantially identical to the centrifugal pendulum 135 explained in FIG. Deviating from this, the first flange part 295 is dispensed with and only the second flange part 300 is provided which extends in a plane of rotation perpendicular to the first axis of rotation 155. On the second flange 300, the bearing portion 265 is arranged.
  • the first centrifugal pendulum unit 140 is designed as explained in FIG. 16 and arranged radially outside the coupling rocker 180. In the embodiment, the coupling rocker 180 is designed in two parts similar to the first centrifugal pendulum unit 140.
  • the coupling rocker 180 has a first coupling rocker part 315 and a second coupling rocker part 320, wherein the first coupling rocker part 315 and the second coupling rocker part 320 are arranged on both sides of the second flange part 300.
  • the fourth link 225 is provided in each case, which is penetrated by the second guide roller 230 to guide the coupling rocker 180 along the second pendulum track 215 about the second axis of rotation 210.
  • the flywheel mass 175 is arranged.
  • the flywheel mass 175 is connected to the first coupling rocker part 315 via the coupling device 190.
  • the first coupling oscillating part 315 is rotatably connected to the second coupling oscillating part 320. This can be done for example by means of connecting bolts.
  • FIG. 18 shows a development of the coupling rocker 180 shown in FIG.
  • a first additional coupling rocker part 325 and a second additional coupling rocker part 330 are provided, wherein the first additional coupling rocker part 325 and the second auxiliary coupling rocker part 330 are arranged on opposite sides of the coupling rocker 180 in each case in the axial direction.
  • the first additional coupling rocker part 325 and the second additional coupling rocker part 330 are designed identically to one another and shorter in the radial direction than the coupling rocker 180.
  • the additional coupling rocker part 325, 330 does not protrude beyond the flange part 295, 300 arranged radially in each case on the inside , As a result, a centrifugal force pendulum 135 that is particularly compact in the axial direction can be provided. Furthermore, a mass of the coupling rocker shown in FIG. 18 is increased relative to the coupling rocker 180 shown in FIG.
  • first portion 290 of the flywheel 175 is disposed radially inwardly of the coupling rocker 180 axially between the first flange portion 295 and the second flange 300.
  • the second flange part 300 extends in the radial direction radially inward beyond the first flange part 295. Furthermore, the bearing section 265 on the second flange part 300 has been dispensed with.
  • FIG. 19 shows a development of the first centrifugal pendulum unit 140 shown in FIG.
  • a pendulum mass part 335, 340 is provided on both sides of the pendulum mass 160 shown in FIG. 9, the pendulum mass 160 being arranged in the axial direction between the first auxiliary pendulum mass part 335 and the second additional pendulum mass part 340.
  • the first additional pendulum mass part 335 and the second auxiliary pendulum mass part 340 are designed such that the first relievepelt- mass part 335 does not protrude over the first flange 295 and the second 1925pendel- mass part 340 via the second flange 300 in the axial direction.
  • FIG. 20 shows a development of the first centrifugal pendulum unit 140 shown in FIG.
  • first pendulum mass part 280 and the second pendulum mass part 285 are wider in the radial direction than shown in FIG.
  • first auxiliary pendulum mass part 335 is arranged axially between the first pendulum mass part 280 and the second pendulum mass part 285.
  • first relievependelmas- sentens part 335 is radially outside the connection flange 150 and connects the first pendulum mass portion 280 with the second pendulum mass portion 285. Also characterized mass of the pendulum mass 160 can be increased.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Transmission Devices (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

L'invention concerne un pendule centrifuge qui peut être monté de manière rotative autour d'un premier axe de rotation, le pendule centrifuge comprenant une première unité de pendule centrifuge et une seconde unité de pendule centrifuge et une bride de raccordement, la bride de raccordement étant bloquée en couple à un dispositif de transmission de couple d'un système d'entraînement. La première unité de pendule centrifuge comporte une masse pendulaire et un premier guide de liaison, la masse pendulaire étant couplée à la bride de raccordement au moyen du premier guidage à coulisse, et le premier guidage à coulisse étant conçu pour guider la masse pendulaire le long d'une première voie de pendule lorsqu'une uniformité de rotation est introduite dans la bride de raccordement, la seconde unité de pendule centrifuge comprenant une masse centrifuge au moins partiellement annulaire, une bielle oscillante d'accouplement, un second guidage à coulisse et un dispositif de couplage. Le dispositif de couplage est disposé de manière décalée dans la direction circonférentielle par rapport aux premier et second guidage à coulisse et est conçu pour monter la bielle oscillante d'accouplement de manière rotative autour d'un second axe de rotation s'étendant parallèlement au premier axe de rotation, le second guidage à coulisse couplant la bielle oscillante d'accouplement à la masse du volant et étant conçu pour guider la bielle oscillante d'accouplement selon un second trajet pendulaire lorsque l'uniformité en rotation est amorcée dans la bride de raccordement.
PCT/DE2019/100208 2018-04-03 2019-03-08 Pendule centrifuge et système d'entraînement comprenant un tel pendule centrifuge WO2019192644A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112019001770.5T DE112019001770A5 (de) 2018-04-03 2019-03-08 Fliehkraftpendel und Antriebssystem mit solch einem Fliehkraftpendel
CN201980017149.1A CN111819372B (zh) 2018-04-03 2019-03-08 离心摆和具有这种离心摆的驱动系统

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018107812.9A DE102018107812A1 (de) 2018-04-03 2018-04-03 Fliehkraftpendel und Antriebssystem mit solch einem Fliehkraftpendel
DE102018107812.9 2018-04-03

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WO2019192644A1 true WO2019192644A1 (fr) 2019-10-10

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PCT/DE2019/100208 WO2019192644A1 (fr) 2018-04-03 2019-03-08 Pendule centrifuge et système d'entraînement comprenant un tel pendule centrifuge

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CN (1) CN111819372B (fr)
DE (2) DE102018107812A1 (fr)
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WO2017057681A1 (fr) * 2015-09-30 2017-04-06 アイシン・エィ・ダブリュ株式会社 Dispositif d'amortissement de vibrations
EP3284969A1 (fr) * 2015-07-17 2018-02-21 Aisin Aw Co., Ltd. Dispositif d'amortissement de vibration

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JP5460849B2 (ja) * 2009-03-16 2014-04-02 シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト 遠心力振り子
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EP3284969A1 (fr) * 2015-07-17 2018-02-21 Aisin Aw Co., Ltd. Dispositif d'amortissement de vibration
WO2017057681A1 (fr) * 2015-09-30 2017-04-06 アイシン・エィ・ダブリュ株式会社 Dispositif d'amortissement de vibrations

Also Published As

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CN111819372B (zh) 2022-08-16
DE102018107812A1 (de) 2019-10-10
DE112019001770A5 (de) 2020-12-17
CN111819372A (zh) 2020-10-23

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