WO2016131453A1 - Dispositif de transfert de couple et système d'entraînement - Google Patents

Dispositif de transfert de couple et système d'entraînement Download PDF

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Publication number
WO2016131453A1
WO2016131453A1 PCT/DE2016/200077 DE2016200077W WO2016131453A1 WO 2016131453 A1 WO2016131453 A1 WO 2016131453A1 DE 2016200077 W DE2016200077 W DE 2016200077W WO 2016131453 A1 WO2016131453 A1 WO 2016131453A1
Authority
WO
WIPO (PCT)
Prior art keywords
centrifugal pendulum
unit
spring
tilgerordnung
pendulum
Prior art date
Application number
PCT/DE2016/200077
Other languages
German (de)
English (en)
Inventor
Matthias Eckerle
Florian Baral
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 CN201680010395.0A priority Critical patent/CN107250602B/zh
Priority to DE112016000765.5T priority patent/DE112016000765A5/de
Publication of WO2016131453A1 publication Critical patent/WO2016131453A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
    • F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
    • F16F15/12373—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs the sets of springs being arranged at substantially the same radius
    • 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
    • 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
    • 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
    • F16H2045/0231—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 arranged in series
    • 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
    • F16H2045/0263—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 pendulum

Definitions

  • the invention relates to a torque transmission device according to claim 1 and a drive system according to claim 10.
  • the torque transmitting device couples the drive motor with a translation device.
  • the drive motor is designed as a reciprocating engine and has a cylinder deactivation, so that in a first operating state, the drive motor provides a torque by supplying all cylinders with fuel. In cylinder deactivation operation, only a portion of the cylinders are fueled so that the available torque through the drive motor is lower. It is an object of the invention to provide an improved torque transmitting device and an improved drive system.
  • an improved torque transmission device in that the torque transmission device is rotatable about an axis of rotation and an input side, an output side, a series damper and at least one centrifugal pendulum device and at least one turbine wheel of a hydrodynamic converter comprises.
  • the series damper comprises at least a first spring device, an intermediate flange and a second spring device.
  • the first spring device is coupled on the input side to the input side and on the output side to the intermediate flange.
  • the second spring device is coupled on the input side with the intermediate flange and on the output side with the turbine wheel.
  • the first centrifugal pendulum device is coupled to the intermediate flange.
  • a second centrifugal pendulum device is provided. see, wherein the second centrifugal pendulum device is coupled to the turbine wheel.
  • the first centrifugal pendulum device has a first centrifugal pendulum unit and a second centrifugal pendulum unit.
  • the first centrifugal pendulum unit comprises at least a first pendulum mass and the second centrifugal pendulum unit at least a second pendulum mass.
  • the first pendulum mass is coupled by means of a first guide unit with the intermediate flange and the second pendulum mass by means of a second guide unit with the intermediate flange.
  • the first centrifugal pendulum unit has at least one first absorber arrangement and the second centrifugal pendulum unit has at least one second absorber arrangement, wherein the first absorber arrangement is equal to or different from the second absorber arrangement.
  • the second centrifugal pendulum device has a third centrifugal pendulum unit and a fourth centrifugal pendulum unit, wherein the third centrifugal pendulum unit has at least a third pendulum mass and a third guide unit and the fourth centrifugal pendulum unit at least a fourth pendulum mass and a fourth guide unit.
  • the series damper comprises a coupling flange, which is connected in a torque-locking manner to the turbine wheel.
  • the third guide unit couples the third pendulum mass with the coupling flange and the fourth guide unit couples the fourth pendulum mass with the coupling flange.
  • the third centrifugal pendulum unit has at least one third absorber arrangement and the fourth centrifugal pendulum unit has at least one fourth absorber arrangement, wherein the third absorber arrangement is equal to or different from the fourth absorber arrangement.
  • the third orbital order and / or the fourth order of orifice is different from the first and / or second order of orts.
  • the first spring device comprises at least a first spring element and the second spring device comprises at least one second spring element.
  • the first spring element and / or the second spring element is designed as a bow spring or compression spring.
  • the first spring element has a first diameter and the second spring element has a second diameter. The first diameter is different from the second diameter.
  • first spring device and the second spring device are arranged at least partially radially at the same height.
  • the radial space can be made particularly compact.
  • first centrifugal pendulum unit and the second centrifugal pendulum unit are arranged at least partially radially at the same height and axially adjacent to each other.
  • an improved drive system can be provided by the drive system comprising a drive motor and a torque transmission device, which is designed as described above.
  • the drive motor is designed as a reciprocating engine and comprises at least two cylinders. In a first operating state, at least temporarily both cylinders are activated and at least partially fillable with a fuel. In a second operating state, the drive motor is switched off at least one of the cylinders and interrupted a fuel supply to the deactivated cylinder.
  • the Anthebsmotor on a first excitation order and in the second operating state of the drive motor to a second excitation order.
  • the first Tilger angel and / or the third Tilger angel is substantially equal to the first excitation order and the second and / or fourth Tilger angel substantially equal to the second excitation order.
  • Figure 1 is a schematic representation of a drive system according to a first embodiment
  • Figure 2 is a perspective view of a semi-longitudinal section through a structural design of a torque transmitting device of the drive system shown in Figure 1;
  • FIG. 3 shows a half-longitudinal section through the torque transmission device shown in FIG. 2;
  • FIGS. 4 and 5 are perspective views of the torque transmission device shown in FIGS. 2 and 3;
  • FIG. 6 is a schematic representation of a drive system according to a second embodiment.
  • FIG. 1 shows a schematic representation of a drive system 10 according to a first embodiment.
  • FIG. 1 is designed in the manner of a circuit diagram. In this case, 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 includes a torque transfer device 15 and a drive motor 20.
  • the drive motor 20 is designed as a reciprocating engine.
  • the drive motor 20 comprises a first cylinder 25 and at least one second cylinder 25. Linder 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 supplied from the fuel supply 35 into the cylinders 25, 30 at regular time intervals to burn the fuel together with atmospheric oxygen in the cylinder 25, 30 ,
  • 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 ni.
  • the excitation order n corresponds to half of the cylinders 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 lockup clutch 70 and a hydrodynamic converter 75.
  • the lockup 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 torque-locking manner.
  • the converter 75 comprises a pump impeller 80 and a turbine wheel 85.
  • the pump impeller 80 is torque-connected to the input side 55 and the turbine wheel 85 to the output side 60.
  • the turbine wheel 85 comprises a coupling flange 110 and a turbine wheel part 86. Furthermore, a liquid is provided in the converter 75. In the open state of the lock-up 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 lock-up clutch 70.
  • the coupling flange 1 10 is connected in a torque-locking manner to the turbine wheel 85 of the converter 75.
  • the first spring means 90 is arranged between the input flange 105 and the intermediate flange 95.
  • a first end 15 of the first spring device 90 is coupled to the input flange 105 and a second end 120 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 first centrifugal force pens 135 and a second centrifugal pendulum device 140.
  • the first centrifugal pendulum device 135 is arranged on the intermediate flange 95.
  • the second centrifugal pendulum device 140 is coupled to the turbine wheel 85.
  • FIG. 2 shows a perspective view of a semi-longitudinal section through the torque transmission device 15 shown in FIG. 1.
  • FIG. 3 shows a semi-longitudinal section through the torque transmission device 15 shown in FIG. 2.
  • FIGS. 4 and 5 show perspective views of the torque transmission device 15 shown in FIGS
  • the illustration of the lockup clutch 70 and of the hydrodynamic converter 75 in FIGS. 2 to 5 has been dispensed with.
  • the torque transmission device 15 can be mounted rotatably about a rotation axis 145.
  • the output side 60 of the torque transmission device 15 comprises a hub 150 arranged radially on the inside.
  • the hub 150 has a receptacle 155 on the radially inner side in order to provide a torque-locking connection to a transmission input shaft 160 of a transmission device.
  • Radially on the outside, the hub 150 is formed like a step.
  • the input flange 105 and on the right-hand side the coupling flange 110 are arranged.
  • the input flange 105 is formed in the embodiment by a plate carrier 161 of the lock-up clutch 70 and by a first holding device 165.
  • the first holding device 165 is rotatably mounted on the hub 150 radially inwardly.
  • the first spring device 90 comprises a plurality of circumferentially extending on a circular path spring elements 170, 171st In this case, a first spring element 170 spaced apart in the circumferential direction to a second spring element 171 is arranged.
  • the spring element 170, 171 is formed in the embodiment as a bow spring.
  • the spring element 170, 171 is designed as a compression spring, which is arranged in a straight line on a tangent to a circular path about the axis of rotation 145.
  • each spring element 170, 171 consist of a plurality of springs which are nested concentrically in one another and / or stacked in the circumferential direction.
  • Each spring element 170, 171 has in each case the ends 1 15, 120 of the first spring device 90 of FIG.
  • the first spring device 90 has a first diameter.
  • the first holding device 165 engages radially outside at least partially the spring elements 170, 171 and secures both an axial and a radial position of the first Fe. 90. Radial on the inside, the first holding device 165 is connected by means of a first connection 175 with the plate carrier 160 of the lock-up clutch 70 torque-locking.
  • the first holding device 165 has at least one first engagement element (not shown), which engages in the circumferential direction between the first spring element 170 and the second spring element 171. In this case, by way of example, the first engagement element is coupled to the first end 1 15 of the first spring device 90.
  • the intermediate flange 95 is disc-shaped and rotatably mounted on the hub 150.
  • the intermediate flange 95 has radially on the outside a second engagement element 180 and a third engagement element 185 (see FIG.
  • the third engagement element 185 is arranged offset in the circumferential direction to the second engagement element 180.
  • the second engagement element 180 extends substantially radially outward and engages between the first spring element 170 and the second spring element 171 of the first spring device 90 and couples the intermediate flange 95 with the first spring device 90.
  • the second engagement element 180 of the intermediate flange 95 is coupled to the second end 120 of the first spring device 90. If the lockup clutch 70 is opened and thus the first spring device 90 is unconfirmed, the first engagement element is also coupled to the second end 120 of the first spring device 90 and the second engagement element 180 is coupled to the first end 15 of the first spring device 90.
  • the first centrifugal pendulum device 135 Radially inside to the first spring means 90, the first centrifugal pendulum device 135 is arranged.
  • the first centrifugal pendulum device 135 has a first centrifugal pendulum unit 200 and a second centrifugal pendulum unit 201.
  • the first centrifugal pendulum unit 200 and the second centrifugal pendulum unit 201 are circumferentially spaced from each other.
  • the first centrifugal pendulum unit 200 has a first pendulum mass 205 and a first guide unit 210.
  • the first guide unit 210 is designed and coupled in the manner of a slotted guide When a rotary oscillation is introduced into the intermediate flange 95, the first guide unit 210 guides the first pendulum mass 205 along a first pendulum track 215.
  • the second centrifugal pendulum unit 201 comprises a second pendulum mass 220 and a second guide unit 225
  • Guide unit 225 couples the second pendulum mass 220 with the intermediate flange 95.
  • the second guide unit 225 is designed in the manner of a slotted guide. When introducing a torsional vibration into the intermediate flange 95, the second guide unit 225 guides the second follower mass 220 along a second pendulum track 230.
  • the first and second centrifugal pendulum units 200, 205 are formed in the manner of an external centrifugal pendulum.
  • the centrifugal pendulum unit 200, 205 is formed in the manner of an internal centrifugal pendulum.
  • the first centrifugal pendulum unit 200 has a first
  • the second centrifugal pendulum unit 201 has a second absorber arrangement as a function of a mass of the second pendulum mass 220 of an embodiment of the second pendulum track 230.
  • the first centrifugal pendulum unit 200 is formed identical to the second centrifugal pendulum unit 201, so that the first
  • Tilger inch and the second Tilger inch are identical. This has the consequence that upon initiation of torsional vibration in the intermediate flange 95, the first pendulum mass 205 and the second pendulum mass 220 oscillate synchronously along the pendulum tracks 215, 230. This allows the two pendulum masses 205, 220 are formed in the circumferential direction particularly wide, so that the mass of the two pendulum masses 205, 220 is particularly large. As a result, the first centrifugal pendulum unit 200 and the second centrifugal pendulum unit 200 can cancel out particularly high torsional vibrations.
  • the first and second Tilgerowski the first and second centrifugal pendulum unit 200, 201 corresponds substantially to the first excitation order of the drive motor 20 in the first operating state.
  • the coupling flange 110 comprises a second holding device 235, a first coupling disk 240 and a second coupling disk 245.
  • the second coupling disk 245 is connected to the hub 150 radially on the inside by means of an integral connection 250, preferably a welded connection.
  • the first coupling disc 240 is seated radially on the inside of the hub 150.
  • the first coupling disk 240 extends substantially in the radial direction. Radially on the outside, the second holding device 235 is connected to the first coupling disk 240 by means of a second positive connection 255, which is designed as a riveted connection.
  • the second coupling disc 245 is connected by means of a third positive connection 270 with the first coupling disc 240 torque-locking.
  • the third positive connection 270 may be formed as a riveted joint.
  • the second holding device 235 is open axially in the direction of the first holding device 165 and surrounds the second spring device 100 radially on the outside.
  • the first spring device 90 and the second spring device 100 are arranged essentially at the same radial height.
  • the second spring device 100 has a second diameter that is smaller than the first diameter.
  • the second spring device 100 comprises a third spring element 260 and a fourth spring element 265 arranged in the circumferential direction at a distance from the third spring element 260 (see FIG.
  • the third and fourth spring element 260, 265 are formed in the embodiment as a bow spring.
  • the third and / or fourth spring element 260, 265 is designed as a compression spring which is arranged in a straight line on a tangent to a circular path about the axis of rotation 145.
  • the second centrifugal pendulum device 140 is arranged axially adjacent to the first centrifugal pendulum device 135 radially at substantially the same height of the first centrifugal pendulum device 135.
  • the second centrifugal pendulum device 140 includes a third centrifugal pendulum unit 275 and a fourth centrifugal pendulum unit 280.
  • the third centrifugal pendulum unit 275 is disposed in a circumferential direction adjacent to the fourth centrifugal pendulum unit 280.
  • the third centrifugal pendulum unit 275 includes a third pendulum mass 285 and a third guide unit 290.
  • the third guide unit 290 couples the third pendulum mass 285 to the first coupler 240 and, upon initiation of torsional vibration in the first coupler 240, guides the third pendulum mass 285 along a third pendulum mass 295.
  • the fourth centrifugal pendulum unit 280 includes a fourth pendulum mass 300 and a fourth guide unit 305.
  • the fourth guide unit 305 couples the fourth pendulum mass 300 to the first coupler 240 and, upon initiation of torsional vibration in the first coupler 240, guides the fourth pendulum mass 300 along a fourth pendulum 310.
  • the third and fourth guide unit 290, 305 are designed in the manner of a slotted guide.
  • the third centrifugal pendulum unit 275 has a third Tilger Ich depending on a mass of the third pendulum mass 285 and the configuration of the third pendulum track 295.
  • the fourth centrifugal pendulum unit 280 depending on a mass of the fourth pendulum mass 300 and the configuration of the fourth pendulum track 310 on a fourth Tilger Mr.
  • the third and fourth tilting arrangements are identical to each other in the embodiment, so that the third and fourth pendulum masses 285, 300 oscillate in synchronism with each other along the third and fourth pendulum tracks 295, 310 upon initiation of torsional vibration in the first coupling disk 240.
  • the third and fourth Tilger inch different from the first and second Tilger inch and matched to the second excitation order of the drive motor 20 in the second operating state of the drive motor 20.
  • the third and fourth absorber order essentially corresponds to the second excitation order of the drive motor 20.
  • the third engagement element 185 engages between the third spring element 260 and the fourth spring element 265.
  • the third engagement element 185 is coupled to the first end 125 of the second spring device 100.
  • the second end 130 of the second spring device 100 is connected to the second holding device. device 235 (not shown).
  • the first coupling disk 240 has a fourth engagement element radially on the outside, wherein the fourth engagement element is coupled to the second end 130 of the second spring device 100.
  • FIG. 6 shows a schematic representation of a drive system 10 according to a second embodiment.
  • the drive system 10 is designed similarly to the drive system 10 described in FIGS. 1 to 5. Deviating from this, the first absorber arrangement of the first centrifugal pendulum unit 200 is different from the second absorber arrangement of the second centrifugal pendulum unit 201. It is particularly advantageous if the first Tilgerowski to the first excitation order of the drive motor 20 and the second Tilgerowski the second centrifugal pendulum unit 201 are tuned to the second excitation order of the drive motor 20. Further, unlike the drive system 10 described in Figs.
  • the third damper arrangement of the third centrifugal pendulum unit 275 is different from the fourth damper arrangement of the fourth centrifugal pendulum unit 280. It is advantageous if the third damper arrangement of the third centrifugal pendulum unit 275 is equal to the first damper order the first centrifugal pendulum unit 200 and the fourth absorber arrangement of the fourth centrifugal pendulum unit 280 equal to the second absorber order of the second
  • Centrifugal pendulum unit 201 is.
  • substantially the third absorber order of the third centrifugal pendulum unit 275 is equal to the first excitation order of the drive motor 20 in the first operating state.
  • the fourth absorber arrangement of the fourth centrifugal pendulum unit 280 is also equal to the second excitation order of the drive motor 20 in the second operating state.
  • the second absorber arrangement of the second centrifugal pendulum unit 201 can thereby be designed differently from the first absorber arrangement of the first centrifugal pendulum unit 200 in that the second pendulum mass 220 has a mass that is different from the first pendulum mass 205. Additionally or alternatively, the second
  • the second pendulum mass 220 leads on a different to the first pendulum track 215 second pendulum track 230. This causes, that upon initiation of the torsional vibration in the intermediate flange 95, the first pendulum mass 205 asynchronously oscillates to the second pendulum mass 220.
  • the fourth Tilger eleven the fourth centrifugal pendulum unit 280 can be designed differently from the third Tilger eleven the third centrifugal pendulum unit 275, characterized in that the fourth pendulum mass 300 has a different mass to the third pendulum mass 285. Additionally or alternatively, the fourth Tilger eleven thereby be different from the third Tilger eleven by the fourth guide unit 305, the fourth pendulum mass 300 leads on a fourth pendulum track 310 different from the third pendulum track 295. This causes the third pendulum mass 285 to oscillate asynchronously with the fourth pendulum mass 300 when the torsional vibration is introduced into the turbine wheel 85.
  • the drive system 10 described above has the advantage that can be reliably eradicated by the provision of two centrifugal pendulum devices 135, 140 in both operating states of the drive motor 20 with activated cylinder deactivation and deactivated cylinder deactivation torsional vibrations.
  • the series damper 65 provides further cancellation of torsional vibrations at a predefined frequency.

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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)

Abstract

L'invention concerne un dispositif de transfert de couple (15) et un système d'entraînement comprenant un dispositif de transfert de couple (15) de ce type, le dispositif de transfert de couple (15), qui peut tourner autour d'un axe de rotation (145), comprenant un côté d'entrée (55), un côté de sortie (60), un amortisseur série (65), au moins un premier dispositif à pendule à force centrifuge (135) et au moins une roue de turbine (85) d'un convertisseur hydrodynamique (75), l'amortisseur série (65) comprenant au moins un premier dispositif à ressort (90), une bride intermédiaire (95) et un deuxième dispositif à ressort (100), le premier dispositif à ressort (90) étant accouplé côté entrée au côté d'entrée (55) et côté sortie à la bride intermédiaire (95), le deuxième dispositif à ressort (100) étant accouplé côté entrée à la bride intermédiaire (95) et côté sortie à la roue de turbine (85), le premier dispositif à pendule à force centrifuge (135) étant accouplé à la bride intermédiaire (95), un deuxième dispositif à pendule à force centrifuge (140) étant présent, le deuxième dispositif à pendule à force centrifuge (140) étant accouplé à la roue de turbine (85).
PCT/DE2016/200077 2015-02-16 2016-02-08 Dispositif de transfert de couple et système d'entraînement WO2016131453A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201680010395.0A CN107250602B (zh) 2015-02-16 2016-02-08 扭矩传递装置和驱动***
DE112016000765.5T DE112016000765A5 (de) 2015-02-16 2016-02-08 Drehmomentübertragungseinrichtung und antriebssystem

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015202751.1A DE102015202751A1 (de) 2015-02-16 2015-02-16 Drehmomentübertragungseinrichtung und Antriebssystem
DE102015202751.1 2015-02-16

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Publication Number Publication Date
WO2016131453A1 true WO2016131453A1 (fr) 2016-08-25

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DE (2) DE102015202751A1 (fr)
WO (1) WO2016131453A1 (fr)

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Publication number Priority date Publication date Assignee Title
WO2018041294A2 (fr) * 2016-08-29 2018-03-08 Schaeffler Technologies AG & Co. KG Dispositif de transmission de couple et système d'entraînement
DE102019127216B4 (de) * 2019-10-10 2021-12-02 Schaeffler Technologies AG & Co. KG Drehmomentübertragungsvorrichtung
CN112833135B (zh) * 2021-02-04 2022-06-21 太原理工大学 一种机械旋转式非光滑局域共振声子晶体减振装置

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DE102015202751A1 (de) 2016-08-18

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