WO2015124156A1 - Dispositif de transmission de couple - Google Patents

Dispositif de transmission de couple Download PDF

Info

Publication number
WO2015124156A1
WO2015124156A1 PCT/DE2015/200073 DE2015200073W WO2015124156A1 WO 2015124156 A1 WO2015124156 A1 WO 2015124156A1 DE 2015200073 W DE2015200073 W DE 2015200073W WO 2015124156 A1 WO2015124156 A1 WO 2015124156A1
Authority
WO
WIPO (PCT)
Prior art keywords
torque transmission
additional mass
torque
mass
turbine wheel
Prior art date
Application number
PCT/DE2015/200073
Other languages
German (de)
English (en)
Inventor
Stephan Maienschein
Mario Degler
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 DE112015000857.8T priority Critical patent/DE112015000857A5/de
Priority to EP15708718.0A priority patent/EP3108153A1/fr
Publication of WO2015124156A1 publication Critical patent/WO2015124156A1/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
    • F16F15/1204—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
    • 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 torque transmission device according to claim 1.
  • WO 201 1/147 633 discloses a torque transmission device which can be used, for example, in a drive train of a vehicle in order to damp or as far as possible eliminate rotational nonuniformities.
  • the torque transmission device has an input area to be driven for rotation about an axis of rotation 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 superposition of the torque transmission paths guided torques is provided, wherein in the first Torque transmission path is provided a first phase shifter arrangement for generating a phase shift of over the first torque transmission path guided torsional vibrations with respect to the second torque transmission path guided torsional vibrations.
  • a turbine wheel of a hydrodynamic converter is coupled to the output side of the torque transmission device.
  • an improved torque transmission device can be provided in that the torque transmission device for torque transmission between input side and an output side is rotatable about an axis of rotation, wherein a power split device is provided with a first torque transmission path and a second torque transmission path and a translation device, wherein the power split device is coupled to the input side and the output side and is configured to transmit the torque via the two torque transmission paths between the input side and the output side, wherein in the first torque transmission path, a phase shifter is provided for generating a phase shift of torsional vibrations guided via the first torque transmission path with respect to the second torque transmission path, wherein a hydrodynamic converter is provided with a turbine wheel, wherein the turbine wheel is coupled to the transmission device.
  • a mass of the phase shifter can be easily increased with already existing components, so that a resonance frequency of the phase shifter is particularly low, and thus the phase shifter can be operated particularly fast in a supercritical state during operation of the torque transmitting device.
  • the power split device has a
  • Branching device and a coupling device Between the branching device and the coupling device, the two torque transmission paths are arranged.
  • the translation device is part of the branching device or the coupling device or is arranged in the second torque transmission path.
  • the phase shifter forms a vibration system with a first rotational mass arranged on the input side of the phase shifter and a second rotational mass about the axis of rotation with respect to the first rotational mass, wherein the turbine wheel is at least partially part of the first rotational mass or the second rotational mass.
  • an additional mass is provided, wherein the additional mass is torque-connected to the turbine wheel.
  • the mass of the turbine wheel can be further increased.
  • the additional mass is at least partially annular and preferably arranged axially between the turbine wheel and the spring arrangement. This results in a particularly compact axial design of the torque transmission device.
  • the additional mass has a first portion and a second portion directly adjacent to the first portion, wherein the first portion extends substantially in the radial direction and the second portion extends substantially in the axial direction, the first portion being axially adjacent the spring arrangement of the phase shifter and the second section is arranged radially outwardly adjacent to the spring arrangement of the phase shifter.
  • the additional mass has a wall, wherein the wall is guided in a distribution section at least partially multi-layered, preferably double-layered.
  • a distribution section at least partially multi-layered, preferably double-layered.
  • the additional mass comprises a first additional mass part and a second additional mass part.
  • the first additional mass part is torque-locking manner with the turbine wheel and the second additional mass part torque-connected to the first additional mass part.
  • the second additional mass part can be connected in a simple manner indirectly to the turbine wheel.
  • the second additional mass part has a radially inner side arranged inner contour and the first additional mass part has a radially outer outer contour, wherein the inner contour is at least partially identical to the outer contour and the second additional mass part at least partially rests flat against the first additional mass part.
  • the additional mass radially outside half a maximum radial extent of the additional mass has at least 50 percent of a total volume of the additional mass, preferably at least 75 percent of the total volume of the additional mass.
  • Figure 1 is a schematic representation of a drive system with a torque transmission device according to a first embodiment; a schematic representation of the drive system shown in Figure 1 with a torque transmitting device according to a second embodiment.
  • Figure 3 is a schematic representation of the drive system shown in Figure 1 with a torque transmitting device according to a third embodiment.
  • FIG. 4 shows a half-longitudinal section through a structural design of the embodiment shown in FIG. 1
  • FIG. 7 shows a third variant of the half longitudinal section of the torque transmission device shown in FIG.
  • FIG. 1 shows a schematic representation of a drive system 10 with a torque transmission device 15.
  • rotational masses 100 are symbolized by a rectangular box.
  • the rotational mass 100 is larger the larger the box.
  • rotational masses 100 for example a hub, a flange, a carrier plate or a cast part with box-shaped elements are symbolized.
  • 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 represent a plurality of engaging in the rotational mass 100 frictions or torques clear.
  • a line-shaped connecting line represents a torque transmission 30.
  • the torque transmitting device 15 has an input side 20 and a
  • the input side 20 is connected via a first torque transmission 30.1 on the input side to a reciprocating motor 35.
  • the drive system 10 comprises, in addition to the reciprocating motor 35, a transmission 40, which is preferably designed as a semi-automatic, in particular as a fully automatic switching transmission.
  • the transmission 40 has a transmission input shaft 45.
  • the output side 25 is connected via the transmission input shaft 45 to the transmission 40.
  • the torque transmission device 15 comprises a clutch device 50, a hydrodynamic converter 55 and a power split device 60 with a branching device 65 and a coupling device 70. Between the branching device 65 and the 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 disposed in parallel with the second torque transmission path 80.
  • the coupling device 70 is formed in Figure 1 as a translation device 71.
  • the translation device 71 is designed as summing, in particular as a planetary gear.
  • the coupling device 70 may also be designed differently and, for example, a hydraulic and / or a lever mechanism for coupling the two torque transmission paths 75, 80 have.
  • the coupling device 50 is a torque transmitting device that is controllable to selectively transmit or disengage torque 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 disengaging unit may be provided.
  • an electrical operation 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 transmitted by the converter is dependent on a speed difference between the turbine wheel 1 15 and the impeller 1 10.
  • Speed reducer works.
  • the transmittable by means of the converter 55 torque decreases.
  • a spring arrangement 120 can be designed, for example, as a bow spring or as a compression spring or as a turbine spring. In this case, no difference is made in Figure 1 between a bow spring or a compression spring.
  • the bow spring is an elastic element for force transmission, which is arranged tangentially around an axis of rotation 125 (see FIG.
  • the compression spring has a similar operation as the bow spring.
  • the compression spring is usually helical and does not extend curved, but straight along a tangent to a circumference of a circle segment about the rotation axis 125.
  • the spring assembly 120 may comprise one or more arrangements of the bow spring, the compression spring and / or the turbine spring.
  • the bow springs, the compression spring or the turbine spring can be connected in parallel and / or in series with each other.
  • the input side 20 forms a first
  • the input side 20 is connected via a second torque transmission 30.2 with the impeller 1 10 of the converter 55.
  • the input side 20 is further connected to the coupling device 50.
  • the coupling device 50 is connected on the output side to the branching device 65.
  • the first torque transmission path 75 includes the spring assembly 120.
  • the spring arrangement 120 is connected to the turbine wheel 15 or the third rotational mass 100.3.
  • the phase shifter 135 is connected on the output side of the third rotational mass 100.3 via a third torque transmission 30.3 to the coupling device 70.
  • the second torque transmission path 80 has a fourth torque transmission 30.4, which is rigid.
  • the second torque transmission path 80 has a spring damper, so that the second torque transmission path 80 is more elastic than shown in FIG.
  • the second torque transmission path 80 has a rigidity of at least 600 Nm / °, preferably 800 Nm / °, in particular 1500 Nm / °, in particular 1800 Nm / °.
  • the coupling device 70 is connected on the output side via a fifth torque transmission 30.5 to the output side 25 or the fourth rotational mass of the output side 25.
  • the reciprocating motor 35 provides torque. Due to the configuration of the reciprocating piston engine 35, the reciprocating motor 35 generates, in addition to a constant torque, a torsional vibration with which the torque is superimposed. The torque with the torsional vibration is introduced via the first torque transmission 30. 1 into the input side 20 of the torque transmission device 15. When the clutch 50 is closed, the torsional vibration is transmitted to the branching device 65 together with the torque. The branching device 65 distributes the torque but also the rotational vibration on both the first and second torque transmission paths 75, 80.
  • the phase shifter 135 has a resonant frequency.
  • the resonance frequency is by way of example in a range from 400 to 700 Hz, preferably between 500 and 600 Hz. It should be noted that the resonant frequency is understood to be that resonant frequency which has the lowest frequency.
  • the phase shifter 135 forms a vibration system.
  • two rotational masses 100.1, 100.2, 100.3 can oscillate relative to each other against the action of the spring assembly 120.
  • the spring assembly 120 has a predetermined stiffness or spring rate.
  • the two mutually oscillating rotational masses 100.1, 100.2, 100.3 are essentially the input side of the phase shifter 135 by the branching device 65, the clutch, the input side 20 and the impeller 1 10 determined.
  • the other rotation mass is determined by the third rotation mass 100.3.
  • the third rotational mass 100.3 is significantly smaller than the input side ground.
  • phase shifter 135 When vibrational excitation with a frequency below the resonance frequency by the reciprocating motor 35 phase shifter 135 operates subcritical, which means that excitation and reaction substantially simultaneously, ie without mutual phase shift, occur. When the resonant frequency is exceeded, the phase shifter 135 changes to a supercritical state in which excitation and reaction are shifted relative to one another, which essentially means a phase jump of 180 ° of excitation and reaction.
  • torsional vibration components which are contained in the torque component to be transmitted via the first torque transmission path 75, when the excitation frequency of the torsional vibration is above the second resonance frequency of the phase shifter 135, are forwarded by a maximum of 180 ° out of phase in the direction of the coupling device 70.
  • phase shifter 135 the quality of the phase jump, that is to say the size of the phase shift produced by different conditions, will in particular also depend on the frictional effects occurring in the area of the phase shifter 135, while the position of the transition is defined by the resonant frequency of the phase shifter 135.
  • friction elements are provided in the first torque transmission path 75.
  • the fourth torque transmission 30.4 also has a (separate) resonant frequency, this is so high that the fourth torque transmission 30.4 operated by the torsional vibrations of the reciprocating motor 35 becomes subcritical. As a result, the torque components of the torsional vibration or of the torque to be transmitted via the second torque transmission path 80 have essentially no phase offset.
  • the coupling device 70 is configured to superimpose the torques transmitted through the first torque transmission path 75 and the second torque transmission path 80.
  • the translation device 71 has a translation i.
  • the torque transmission paths 75, 80 are over or reduced or obtained towards the fifth torque transmission 30.5. Due to the superimposition, the phase-shifted torsional vibrations are transmitted by transmitting over the first torque transmission path 75 and the non-phase-locked torsional vibrations, transmitted via the second torque transmission path 80, superimposed.
  • the torsional vibrations transmitted via the first torque transmission path 75 have a phase offset of ideally 180 °, so as to cancel the torsional vibrations transmitted via the second torque transmission path 80 in the coupler 70 by summing up so that on the output side the coupling device 70, a substantially constant torque of the damper input side 130 is provided.
  • FIG. 2 shows a schematic illustration of a torque transmission device according to a second embodiment.
  • the mode of operation of the torque transmission device 200 shown in FIG. 2 is essentially similar to the torque transmission device 15 shown in FIG. 1. Deviating from this, however, the components of the torque transmission device 200 are partially arranged or interconnected with one another.
  • the torque transmission device 200 has on the input side 20, the first rotational mass 100.1, which is connected via a second torque transmission 30.2 with the impeller 1 10 of the hydrodynamic converter 55.
  • the turbine wheel 15 and its rotational mass 100.3 are connected to the transmission device 71 via a third torque transmission 30.3.
  • the first rotational mass 100.1 is also connected to the coupling device 50.
  • the second rotational mass 100.2 is formed as a branching device 65, as also in FIG.
  • the first torque transmission path 75 and the second torque transmission path 80 are connected to the branching device 65, wherein the second torque transmission path 80 is rigidly connected to the transmission device 71 by means of the fourth torque transmission 30.4.
  • the spring assembly 120 is connected in the first torque transmission path 75 with the fourth rotational mass 100.4.
  • the translation device 71 is connected on the output side via the fifth torque transmission 30.5 with the fourth rotational mass 100.4.
  • the fourth rotational mass 100.4 thus serves in the embodiment both as an output side 25 and as a coupling device 70 of the power split device 60, in which the two torque transmission paths 75, 80 are superimposed.
  • the coupling device 50 is opened, the torque to be transmitted is transmitted from the input side 20 via the second torque transmission 30.2 to the impeller 1 10.
  • the impeller 1 10 transmits the torque further to the turbine wheel 1 15. From the turbine wheel 15 1, the torque is further transmitted via the third torque transmission 30.3 in the translation device 71. From there, depending on a ratio i of the transmission device 71, the torque flows via the fifth torque transmission 30.5 into the output side 25.
  • the torque transmission 30 also takes place via the second torque transmission path 80 into the second rotation mass 100.2 and from there via the spring arrangement 120 and the first one Transmission route 75 in the output side 25.
  • the embodiment has the advantage that in the open state of the clutch device 50 as a power split in the torque transmitting device 200 takes place and by the two torque transmission paths 75, 80 and in the open state of the clutch device 50 torsional vibrations can also be redeemed.
  • the torque transmission in the torque transmission device 200 essentially takes place via the clutch device 50 and no longer via the converter 55.
  • the torque transmission 30 takes place from the input side 20 via the clutch device 50 into the second rotational mass 100.2, which then functions as a branching device 65 serves. From the branching device 65 then go from the two torque transmission paths 75, 80 from.
  • the spring arrangement 120 is arranged, which is connected to the fourth rotational mass 100.4.
  • the spring arrangement 120 is part of the phase shifter 135.
  • the second rotation mass 100.2 together with the first rotation mass 100.1 in conjunction with the spring arrangement 120 and the fourth rotation mass 100.4 serves as the phase shifter 135.
  • the phase shifter 135 forms the oscillatory system as described above , wherein two rotational masses, in this case the first and second rotational masses 100.1, 100.2, on the input side of the spring arrangement 120 and the fourth rotational mass 100.4 on the output side of the spring arrangement 120 can oscillate relative to one another.
  • the translation device 71 is provided, which is connected on the input side via the fourth torque transmission 30.4 with the branching device 65. Furthermore, the translation device 71 is connected to the turbine wheel 15 via the third torque transmission 30.3. Furthermore, the second torque Transmission path 80, the fifth torque transmission 30.5 on the output side, the translation device 71 with the fourth rotational mass 100.4 connects.
  • a torsional vibration is introduced via the input side 20 into the torque transmission device 200, then the torsional vibration is transmitted via the coupling device 50 to the branching device 65.
  • the branching device 65 forwards the torsional vibration to the translation device 71 via the fourth torque transmission 30.4.
  • the torsional vibration is translated according to the translation of the fourth torque transmission 30.4 to the fifth torque transmission 30.5 and forwarded to the fourth rotational mass 100.4.
  • the translation device 71 which is designed as a planetary gear in the embodiment, which is connected to the input side 20 of the translation device 71 third rotational mass 100.3 or the turbine wheel 1 15 with its inertia.
  • the inertia of the third rotational mass 100.3 acts against the transmitted via the fourth torque transmission 30.4 torsional vibration.
  • the translation device 71 is set in its degrees of freedom in the dynamic case, so that the torsional vibration coming from the fourth torque transmission 30.4 can be translated to the fifth torque transmission 30.5 according to the translation i.
  • the provision of the turbine wheel 1 15 on the input side of the translation device 71 has the advantage that the turbine wheel 1 15 has a high rotational mass, which is therefore shown in Figure 2 with a large rectangular box.
  • a different embodiment of the torque transmission device 200 can be provided with respect to FIG. 1, as a result of which more degrees of freedom are available in the design of the torque transmission device 200, so that the torque transmission device 200 can be adapted particularly well to different applications.
  • FIG. 3 shows a schematic representation of a torque transmission device according to a third embodiment.
  • the torque transmission device 205 is designed similarly to the torque transmission device 200 shown in FIG. Deviating from this, however, the spring arrangement 120 is arranged between the third rotational mass 100.3 and the fourth rotational mass 100.4.
  • the third rotational mass 100.3 or the turbine wheel 1 15 in conjunction with the spring arrangement 120 and the fourth rotational mass 100.4 serves as a phase shifter 135th If a torsional vibration is introduced via the input side 20 into the torque transmission device 205, then the torsional vibration is transmitted from the first rotational mass 100.1 via the coupling device 50 to the second rotational mass 100.2.
  • the second rotational mass 100.2 no longer serves as a branching device 65.
  • the second rotational mass 100.2 is rigidly connected to the transmission device 71 via the fourth torque transmission 30.4 ,
  • the translation device 71 is used in the embodiment as a branching device 65.
  • the transmission device 71 divides the torque transmission between the translation device 71 and the output side 25 and the fourth rotational mass 100.4 in the two torque transmission paths 75, 80.
  • the first torque transmission path 75 has the third torque transmission 30.3, with which the transmission device 71 is connected to that in the turbine wheel 1 15 and the third rotational mass 100.3.
  • the third rotational mass 100.3 connects the third torque transmission 30.3 with the spring arrangement 120 on the input side.
  • the second torque transmission path 80 has exclusively the fifth torque transmission 30.5, with which the transmission device 71 is connected on the output side to the fourth rotational mass 100.4.
  • the operation of the torque transmission device 205 is similar to the embodiments shown in Figures 1 and 2.
  • the torsional vibration is coupled on the input side via the first rotational mass 100.1.
  • the second rotational mass 100.2 transmits the torsional vibration via the fourth torque transmission 30.4 to the transmission device 71.
  • the transmission device 71 is defined in terms of its degrees of freedom by the interconnection described above.
  • the ratio i which has the translation device 71, the torsional vibration in dependence on the ratio i in the first torque transmission path 75 and the second torque transmission path 80 depending on the gear ratio i between the third torque transmission 30.3 to the fourth torque transmission 30.4 and the fifth torque transmission 30.5 the fourth torque transmission 30.4 translated.
  • the translation device 71 in the embodiment serves as a torque branching device 65.
  • the torsional vibration is transmitted via the fifth torque transmission 30.5 forwarded without phase offset to the fourth rotational mass 100.4.
  • the corresponding proportion of torsional vibration for the first torque transmission path 75 is coupled into the first torque transmission path 75 via the first torque transmission path 75 or via the third torque transmission 30.3, depending on the transmission ratio of the transmission device 71.
  • the torsional vibration is further introduced into the third rotational mass 100.3 or the turbine wheel 15.
  • the turbine wheel 1 15 operates against the spring assembly 120 and the fourth rotational mass 100.4.
  • the phase shifter 130 is operated supercritically, so that the torsional vibration receives a phase offset via the spring arrangement 120 and thus the fourth rotational mass 100.4 is coupled in phase-shifted manner.
  • the fourth rotational mass 100.4 is thus used in the embodiment as a coupling device 70, which superimposed over the torque transmission paths 75, 80 transmitted torsional vibrations and added up.
  • the turbine wheel 15 as absorber mass in the force flow of the power splitter 60, a total mass of the torque transfer device 15, 200, 205 is reduced overall. Furthermore, by using the turbine wheel 1 15 in the line branching device 60, the absorber mass can be increased in a particularly simple manner.
  • the resonance frequency of the phase shifter 135 can be optimally tuned so that the phase shifter 135 has a particularly low natural frequency or resonance frequency.
  • the spring arrangement 120 can not be designed to be infinitely soft in order to further reduce the resonance frequency.
  • the space for torque transmission devices 15, 200, 205, in particular in the radial direction, is limited, so that by increasing the absorber masses by the turbine wheel 15 1, the resonance frequency is reduced even with the same space of the torque transfer devices 15, 200, 205 can be.
  • FIG. 4 shows a half-longitudinal section through a constructive embodiment of the torque transmission device 15 shown in FIG. 1.
  • the coupling device 50 has a plate carrier 300, which is arranged on the left side in FIG.
  • the plate carrier 300 serves to hold clutch plates (not shown) of the coupling device 50 torque-tight and axially displaceable.
  • the plate carrier 300 in the embodiment is a coupling output side and is part of the second rotational mass 100.2.
  • the plate carrier 300 is connected by means of a first positive connection 305 torque-locking with a drive plate 310.
  • the driver disk 310 extends substantially radially from the inside to the outside and is rotatably mounted on a hub 315 on the inside radially.
  • the hub 315 has a shoulder 320 on which the driving plate 310 rests on the right side.
  • the drive plate 310 is axially secured to the hub 315 via a first securing means 325.
  • the shoulder 320 has a first toothing 330 on the circumference.
  • the first shoulder 320 serves as a first sun gear of a planetary gear 335.
  • the planetary gear 335 here forms the translation device 71 shown in Figures 1 to 3 from.
  • the planetary gear 335 further includes a second sun gear 340 disposed on the right side of the first shoulder 320. Radially inside the second sun gear 340 is rotatably mounted on the hub 315.
  • the drive plate 310 is connected via a second positive connection 345 with a planetary pin 350.
  • the drive plate 310 and the planetary pin 350 together form a planet carrier 355 of the planetary gear 335.
  • the planetary pin 350 is encompassed circumferentially by a planetary gear 360 of the planetary gear 335.
  • the planetary gear 360 is formed in two stages and has a second toothing 365 in a first portion 370 of the planetary gear 360.
  • the first section 370 is arranged on the left side adjacent to the driving plate 310 and extends in the axial direction. Further, the planetary gear 360 has a second portion 375 disposed on the right side of the first portion 370.
  • the second portion 375 in the embodiment has a larger diameter relative to a Planetenradachse 380, about which the planetary gear 360 is rotatably mounted, as the first portion 370.
  • a Planetenradachse 380 about which the planetary gear 360 is rotatably mounted, as the first portion 370.
  • the first portion 370 and the second portion 375 the same Diameter or the first portion 370 has a larger diameter than the second portion 375.
  • the second sun gear 340 has a fourth toothing 385, which is arranged radially on the outside of the second sun gear 340.
  • the first toothing 330 engages in the second toothing 365 of the planetary gear 360.
  • the third toothing 376 engages the fourth toothing 385.
  • the planetary gear 360 rolls on the first shoulder 320, which is designed as a first sun gear, to a corresponding effective diameter by the engagement of the first and the second toothing 330, 365.
  • the second sun gear 340 rolls with the fourth toothing 385 on the third toothing 376 to a second effective effective diameter.
  • the second effective effective diameter is greater than the first effective effective diameter.
  • the second sun gear 340 is connected to the turbine wheel 15 by means of a material and / or positive connection 390. It is particularly advantageous if the material and / or positive connection 390 is a welded joint. In this case, the material and / or positive connection 390 is arranged radially inwards to the planetary gearwheel axis 380, so that a particularly compact connection between the second sunwheel 340 and the turbine wheel 15 can be provided.
  • an additional mass 400 is arranged by means of a third positive connection 395.
  • the additional mass 400 is arranged axially between the planetary gear 360 and the turbine wheel 15 1. Radially extends the additional mass 400 from the inside outward to about a diameter of the turbine wheel 15 1 15.
  • the additional mass 400 has an axially extending third section 405 and a radially extending fourth section 410, on which the additional mass 400 is connected radially on the inside to the turbine wheel 15 via the third connection 395.
  • the axially extending section 405 is arranged radially on the outside of the radially extending fourth section 410.
  • the third section 405 is arranged approximately at right angles to the fourth section 410 and parallel to the axis of rotation 125.
  • the axially extending portion 410 has a recess 415 which extends axially in the direction of the drive plate 310.
  • the indentation 415 is arranged radially outside the planetary gear 360.
  • the additional mass 400 forms radially on the outside by the indentation, the radially extending fourth portion 410 and the axially extending portion 405, a retainer 420, which receives the spring assembly 120.
  • the spring assembly 120 is fixed radially on the inside and by the axially extending third portion 405 radially outside. In axial direction, the spring assembly is determined by the drive plate 310 and the fourth section 410.
  • the spring arrangement 120 is formed in the embodiment by means of two spring elements 425, 430, wherein a first spring element 425 surrounds the second spring element 430 radially on the outside. Thereby, a rigidity of the spring assembly 120 can be increased. It is also conceivable that a two-stage in a spring stiffness is achieved by, for example, the second spring element 430 has a clearance angle before the second spring element 430 is actuated by the drive plate 310 in the circumferential direction.
  • the spring elements 425, 430 are formed as bow springs, which extend in the circumferential direction. Also compression springs would be alternatively conceivable.
  • the additional mass 400 also has a supporting element (not shown) on which the spring arrangement 120 is supported in the circumferential direction in order to discharge a torque from the spring arrangement 120 into the additional mass 400.
  • Carrier plate 310 introduced.
  • the drive plate 310 actuates the spring assembly 120 and compresses the spring assembly. From the spring assembly 120, the torque is introduced into the additional mass 400 and from there via the third connection 395 and the turbine 150 in the positive and / or cohesive connection 390, from where the torque via the second sun gear in the planetary 360 and is forwarded there in the paragraph 320 of the hub 315.
  • the hub 315 thus serves as the output side 25 and may ideally be connected, for example, to the transmission input shaft.
  • a torsional vibration is now introduced into the torque transmission device 15 via a plate carrier 300 in addition to the stationary torque, the torsional vibration causes a momentary rotation of the drive plate 310 coupled to the plate carrier 300 with respect to the hub 315.
  • the drive plate 310 takes along the planet pin 345 and thus ensures for a rotation of the planetary gear 360 with respect to the shoulder 320, but also with respect to the second sun gear 340.
  • the planetary gear 360 rolls on the shoulder 320 from.
  • the torsional vibration is split into two torsional vibration components, which are transmitted via the two torque transmission paths 75, 80, as explained above.
  • a second portion of the torsional vibration is introduced by the drive plate 310 in the spring assembly 120.
  • Phase-offset the second component of the torsional vibration is now introduced by the additional mass 400 via the third connection 395 into the positive and / or material-locking connection 390 and thus into the second sun gear 340.
  • the second sun gear 340 in turn rolls off on the second portion 345 of the planetary gear 360 and initiates the second portion of the torsional vibration in the second planetary gear 360.
  • the planetary gear 360 thus serves as a coupling device 70, as shown in FIG. The two components of the torsional vibration are superimposed in the planetary gear 360.
  • the second component has a phase shift of 180 ° through the phase shifter 135. Due to the superposition, the two components are then extinguished.
  • the additional mass 400 By connecting the additional mass 400 with the turbine wheel 15, the mass or an inertia at the output of the spring arrangement 120 can be increased particularly effectively, so that the resonance frequency of the phase shifter 135 is particularly low.
  • the additional mass 400 additionally fulfills the function of the retainer 420 in the embodiment, so that a particularly compact and simply designed torque transmission device 15 can be formed.
  • the additional mass 400 is produced in the embodiment by means of a stamping bending process, of course, other types of production for the additional mass 400 are conceivable. It is also conceivable that the geometry of the additional mass 400 is different.
  • FIG. 5 shows a first variant of the torque transmission device 15 shown in FIG. 4.
  • the torque transmission device 15 is essentially identical to the torque transmission device 15 shown in FIG. Deviating from this, the additional mass 400 has a first additional mass part 431 and a second additional mass part 435.
  • the first additional mass part 431 is formed like the additional mass 400 shown in FIG. Axially between the first additional mass part 431 and the turbine wheel 15 1, the second additional mass part 435 is arranged.
  • the second additional mass part 435 extends radially from the inside to the outside and is radially inwardly connected via the third connection 395 with the turbine wheel 1 15 but also with the first additional mass part 431.
  • a fifth section 440 of the second additional mass part 435 extends outward in a substantially radial direction perpendicular to the axis of rotation 125.
  • a sixth section 445 which extends away from the first additional mass part 431 in the direction of the turbine wheel 15.
  • the second additional mass part 435 has a wall 446, the wall 446 being in a seventh section 450, radially outward to the third section 405 of the first additional mass part 431 is arranged, is executed double-layered.
  • the seventh section 450 can be thickened and a mass of the additional mass part arranged radially on the outside, which has a particularly high mass inertia, can be increased.
  • the seventh section 470 is guided in the axial direction parallel to the rotation axis 125 and radially outside to the third section 405.
  • FIG. 6 shows a second variant of the torque transmission device 15 shown in FIGS. 4 and 5.
  • the torque transmission device 15 is designed substantially identical to the torque transmission device 15 shown in FIG.
  • the additional mass 400 as already shown in Figure 5, formed in two parts, wherein the first additional mass portion 431 is identical to the additional mass 400 shown in Figure 4 is formed.
  • the first additional mass part 431 is connected in a torque-locking manner to the turbine wheel 15 via the third connection 395.
  • the second additional mass part 435 is torque-connected to the first additional mass part 431, for example by means of a welded connection (not shown).
  • the second additional mass part 435 extends radially starting approximately from the recess 415 to the outside in order to increase a mass inertia of the additional mass 400 particularly efficiently.
  • the second additional mass part 435 is substantially L-shaped, with the seventh section 450 being arranged radially outside the third section 405.
  • the second additional mass part 435 is arranged in the axial direction between the first additional mass part 431 and the turbine wheel 15 1. In this case, an inner contour 465 of the second additional mass part 435 is at least partially against an outer contour 470 of the first additional mass part 431.
  • FIG. 7 shows a third variant of the torque transmission device 15 shown in FIG. 4.
  • the torque transmission device 15 is designed similarly to the torque transmission device 15 shown in FIG.
  • the second additional mass part 435 extends axially in the direction of the turbine wheel 1 15 and has a radially inner side arranged inner contour 475, which at least partially conforms to an outer contour 480 of the turbine wheel 15. This is achieved in particular by a substantially identical staltung the inner contour 475 and the outer contour 480 is reached. As a result, a flat abutment of the second additional mass part 435 on the turbine wheel 15 is achieved.
  • the seventh section 450 continues to extend substantially parallel to the axis of rotation 125. As a result, a mass of the second additional mass part 435 can be increased in a particularly simple manner.
  • a total volume of the additional mass 400 which is arranged radially outside half the maximum radial extent of the additional mass 400, is at least 50 percent of a total volume of the additional mass 400, preferably at least 75 percent of the total volume of the additional mass 400.

Landscapes

  • 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)

Abstract

L'invention concerne un dispositif de transmission de couple (15) servant à transmettre un couple entre un côté entrée (20) et un côté sortie (25). Le dispositif de transmission de couple peut être monté de manière rotative autour d'un axe de rotation (125). Un dispositif de répartition de puissance est prévu qui comporte un premier chemin de transmission de couple (75), un second chemin de transmission de couple (80) et un moyen de démultiplication (71). Le dispositif de répartition de puissance est accouplé au côté entrée et au côté sortie et il est adapté pour transmettre le couple entre le côté entrée et le côté sortie par l'intermédiaire des deux chemins de transmission de couple. Dans le premier chemin de transmission de couple est disposé un déphaseur (135) destiné à produire un déphasage des irrégularités de rotation, transmises par le premier chemin de transmission de couple, par rapport à des irrégularités de rotation transmises par le second chemin de transmission de couple. Un convertisseur hydrodynamique (55) est pourvu d'une roue de turbine (115). La roue de turbine est accouplée au dispositif de démultiplication.
PCT/DE2015/200073 2014-02-19 2015-02-10 Dispositif de transmission de couple WO2015124156A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112015000857.8T DE112015000857A5 (de) 2014-02-19 2015-02-10 Drehmomentübertragungseinrichtung
EP15708718.0A EP3108153A1 (fr) 2014-02-19 2015-02-10 Dispositif de transmission de couple

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014203022.6 2014-02-19
DE102014203022 2014-02-19

Publications (1)

Publication Number Publication Date
WO2015124156A1 true WO2015124156A1 (fr) 2015-08-27

Family

ID=52633023

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2015/200073 WO2015124156A1 (fr) 2014-02-19 2015-02-10 Dispositif de transmission de couple

Country Status (3)

Country Link
EP (1) EP3108153A1 (fr)
DE (1) DE112015000857A5 (fr)
WO (1) WO2015124156A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017122468A1 (de) 2017-09-27 2019-03-28 Schaeffler Technologies AG & Co. KG Drehmomentübertragungseinrichtung und hydrodynamischer Drehmomentwandler mit dieser

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011147633A1 (fr) 2010-05-25 2011-12-01 Zf Friedrichshafen Ag Système d'amortissement des vibrations torsionnelles
DE102011075244A1 (de) * 2010-05-25 2011-12-01 Zf Friedrichshafen Ag Hydrodynamische Kopplungseinrichtung, insbesondere Drehmomentwandler
DE102011075243A1 (de) * 2010-05-25 2011-12-01 Zf Friedrichshafen Ag Hydrodynamische Kopplungseinrichtung, insbesondere Drehmomentwandler
WO2014044476A2 (fr) * 2012-09-24 2014-03-27 Zf Friedrichshafen Ag Ensemble embrayage hydrodynamique, en particulier convertisseur de couple
WO2015010836A1 (fr) * 2013-07-23 2015-01-29 Zf Friedrichshafen Ag Convertisseur de couple
WO2015010839A1 (fr) * 2013-07-23 2015-01-29 Zf Friedrichshafen Ag Arrangement d'amortissement des vibrations torsionnelles pour la chaîne cinématique d'un véhicule automobile

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011147633A1 (fr) 2010-05-25 2011-12-01 Zf Friedrichshafen Ag Système d'amortissement des vibrations torsionnelles
DE102011075244A1 (de) * 2010-05-25 2011-12-01 Zf Friedrichshafen Ag Hydrodynamische Kopplungseinrichtung, insbesondere Drehmomentwandler
DE102011075243A1 (de) * 2010-05-25 2011-12-01 Zf Friedrichshafen Ag Hydrodynamische Kopplungseinrichtung, insbesondere Drehmomentwandler
WO2014044476A2 (fr) * 2012-09-24 2014-03-27 Zf Friedrichshafen Ag Ensemble embrayage hydrodynamique, en particulier convertisseur de couple
WO2015010836A1 (fr) * 2013-07-23 2015-01-29 Zf Friedrichshafen Ag Convertisseur de couple
WO2015010839A1 (fr) * 2013-07-23 2015-01-29 Zf Friedrichshafen Ag Arrangement d'amortissement des vibrations torsionnelles pour la chaîne cinématique d'un véhicule automobile

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017122468A1 (de) 2017-09-27 2019-03-28 Schaeffler Technologies AG & Co. KG Drehmomentübertragungseinrichtung und hydrodynamischer Drehmomentwandler mit dieser

Also Published As

Publication number Publication date
EP3108153A1 (fr) 2016-12-28
DE112015000857A5 (de) 2016-11-10

Similar Documents

Publication Publication Date Title
EP2577106B1 (fr) Appareil hydrodynamique de couplage
EP2697536B1 (fr) Boîte de vitesses, en particulier pour la chaîne cinématique d'un véhicule
DE102011075244A1 (de) Hydrodynamische Kopplungseinrichtung, insbesondere Drehmomentwandler
WO2014095186A1 (fr) Système d'amortissement de vibrations de torsion et procédé d'amortissement de vibrations de torsion
DE102011075242A1 (de) Drehschwingungsdämpfungsanordnung
DE102011075243A1 (de) Hydrodynamische Kopplungseinrichtung, insbesondere Drehmomentwandler
DE102011075241A1 (de) Nasslaufende Kupplungsanordnung
EP2951461A1 (fr) Ensemble d'amortissement de vibrations torsionnelles pour la chaîne cinématique d'un véhicule
EP2930396A2 (fr) Dispositif de transmission de couple et système d'entraînement doté d'un tel dispositif de transmission de couple
EP2951462A1 (fr) Ensemble d'amortissement de vibrations torsionnelles pour la chaîne cinématique d'un véhicule
EP2108859B1 (fr) Procédé et système de réduction des vibrations dans le flux d'entraînement d'un véhicule automobile comprenant une boîte de vitesse
DE102012217171B4 (de) Hydrodynamische Kopplungsanordnung, insbesondere Drehmomentwandler
WO2012097988A1 (fr) Chaîne cinématique d'un véhicule automobile
WO2014026814A1 (fr) Ensemble amortisseur de vibrations de torsion pour la chaîne cinématique d'un véhicule
WO2015124156A1 (fr) Dispositif de transmission de couple
WO2016000708A1 (fr) Amortisseur de vibrations de torsion
WO2015139912A1 (fr) Dispositif d'amortissement de vibrations en torsion pour chaîne cinématique d'un véhicule automobile
DE102013201621A1 (de) Drehschwingungsdämpfungsanordnung für den Antriebsstrang eines Fahrzeugs
DE102007049075A1 (de) Torisionsschwingungsdämpferanordnung
WO2015090866A1 (fr) Système d'amortissement de vibrations de torsion pour la chaîne cinématique d'un véhicule automobile

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 15708718

Country of ref document: EP

Kind code of ref document: A1

REEP Request for entry into the european phase

Ref document number: 2015708718

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2015708718

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 112015000857

Country of ref document: DE

REG Reference to national code

Ref country code: DE

Ref legal event code: R225

Ref document number: 112015000857

Country of ref document: DE