WO2012000469A2 - Poulie à courroie de vilebrequin - Google Patents

Poulie à courroie de vilebrequin Download PDF

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Publication number
WO2012000469A2
WO2012000469A2 PCT/DE2011/001213 DE2011001213W WO2012000469A2 WO 2012000469 A2 WO2012000469 A2 WO 2012000469A2 DE 2011001213 W DE2011001213 W DE 2011001213W WO 2012000469 A2 WO2012000469 A2 WO 2012000469A2
Authority
WO
WIPO (PCT)
Prior art keywords
crankshaft
crankshaft pulley
braking device
pulley
belt
Prior art date
Application number
PCT/DE2011/001213
Other languages
German (de)
English (en)
Other versions
WO2012000469A3 (fr
Inventor
Peter Greb
Lázlo MAN
Original Assignee
Schaeffler Technologies Gmbh & 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 Gmbh & Co. Kg filed Critical Schaeffler Technologies Gmbh & Co. Kg
Priority to DE112011102227T priority Critical patent/DE112011102227A5/de
Publication of WO2012000469A2 publication Critical patent/WO2012000469A2/fr
Publication of WO2012000469A3 publication Critical patent/WO2012000469A3/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W20/00—Control systems specially adapted for hybrid vehicles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/30—Conjoint control of vehicle sub-units of different type or different function including control of auxiliary equipment, e.g. air-conditioning compressors or oil pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
    • F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
    • F02B67/06—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus driven by means of chains, belts, or like endless members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
    • F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
    • F16D55/28—Brakes with only one rotating disc
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
    • B60W10/08—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of electric propulsion units, e.g. motors or generators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
    • B60W30/18—Propelling the vehicle
    • B60W30/18009—Propelling the vehicle related to particular drive situations
    • B60W30/18018—Start-stop drive, e.g. in a traffic jam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0058—Fully lined, i.e. braking surface extending over the entire disc circumference
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • F16D2121/20—Electric or magnetic using electromagnets
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/36—Pulleys
    • F16H2055/366—Pulleys with means providing resilience or vibration damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/36—Pulleys

Definitions

  • the invention relates to a crankshaft pulley for transmitting a torque between a crankshaft and a belt drive, with at least one freewheel and a transmission.
  • German Patent Application DE 10 2007 021 233 A1 discloses a drive train for a motor vehicle having a power transmission unit which has two freewheels acting in opposite directions and a planetary gear.
  • the object of the invention is to further optimize a crankshaft pulley according to the preamble of claim 1, in particular with regard to different operating functions and / or the required installation space.
  • the object is at a Kurbeiwellenriemenother for transmitting a torque between a crankshaft and a belt drive, with at least one freewheel and a transmission, solved in that the transmission is combined in the Kurbeiwellenriemenother with a braking device outside the Kurweiswellenriemenother.
  • the braking device different modes, for example, a starter generator and / or a stationary air conditioning can be realized in a simple manner.
  • the braking device allows a demand-dependent activation and / or deactivation of the transmission in certain operating conditions, such as the stationary air conditioning.
  • the freewheel and the transmission are arranged inside the crankshaft pulley.
  • An absorber mass is preferably also disposed inside the crankshaft pulley.
  • the braking device outside the Kurbeiwellenriemenside, in particular radially outward of a belt track of Kurfewellenriemenscale arranged.
  • the braking device is arranged in the axial direction overlapping the crankshaft pulley.
  • the braking device is preferably arranged in the vicinity of the Kurbeiwellenriemencase.
  • crankshaft pulley is characterized in that the braking device is designed as reibschlüsstge or positive electric brake.
  • the braking device preferably comprises a coil carrier with a coil which generates a magnetic field when it is energized. As a result of the magnetic field, an armature of the braking device can be attracted as needed to close the braking device.
  • the transmission is activated or deactivated as required by closing the brake device.
  • crankshaft pulley comprises a movable anchor body and a stationary coil carrier, which represent friction partners or form-fitting partners of the braking device.
  • the bobbin serves to receive the coil of the braking device. Fixed means that the bobbin is fixed relative to the crankshaft pulley. For this purpose, the bobbin is attached to a support structure, for example to a crankcase, outside the crankshaft pulley.
  • the fixed coil support provides the advantage that no rotary feedthrough is required for the voltage supply of the coil.
  • crankshaft pulley is characterized in that the anchor body and / or the coil carrier of the brake device are arranged radially outside a belt track of the crankshaft pulley / is.
  • the anchor body and the coil carrier are preferably arranged radially outside and in the axial direction overlapping the crankshaft pulley, in particular the belt track of the crankshaft pulley. According to a further aspect of the invention, no additional axial space is claimed by the braking device.
  • crankshaft pulley is characterized in that the transmission is designed as a planetary gear with a ring gear which is rotatably connected to the anchor body of the braking device.
  • the ring gear is disposed in the crankshaft pulley, that is radially within the belt track.
  • the anchor body is located outside the belt track.
  • the anchor body is connected, for example by a connecting element, for example a sheet metal part, with the ring gear.
  • the anchor body can also be made in one piece with the ring gear.
  • a further preferred embodiment of the crankshaft pulley is characterized in that the armature body is spaced in the axial direction of the bobbin in the de-energized state of a coil of the braking device.
  • the anchor body is in the de-energized state of the coil, for example by the biasing force of a spring device, spaced from the bobbin so that no frictional engagement between the anchor body and the bobbin occurs.
  • the braking device is normally preferably open.
  • the planetary gear is activated by means of the braking device.
  • crankshaft pulley is characterized in that the anchor body is braked with the ring gear in the energized state of the coil so that one or the belt track of the crankshaft pulley is coupled via the transmission with the crankshaft.
  • the activated by means of the braking device planetary gear can be provided in a simple manner required for starting the engine torque.
  • crankshaft pulley comprises a pulley freewheel having an inner ring rotatably connected together with a planetary carrier of the planetary gear to the crankshaft, and having an outer ring which is rotatably connected to the belt track of the crank pulley.
  • the pulley freewheel effective between the crankshaft and the belt track serves to dampen torque surges in the generator operation of the crankshaft pulley.
  • crankshaft pulley is characterized in that the outer ring of the pulley freewheel is combined with a sun gear of the planetary gear. Combined means that the outer ring of the pulley freewheel can be integrally connected to the sun gear of the planetary gear. But the outer ring can also be firmly bonded to the sun gear and with the help of fasteners.
  • a further preferred embodiment of the crankshaft pulley is characterized in that the coil carrier of the braking device has two recesses for performing at least a portion of a belt of the belt drive.
  • the size of the recesses depends on the size and arrangement of the bobbin outside the crankshaft pulley.
  • the size and shape of the recesses also depends on the belt itself and the arrangement of the belt in the belt drive.
  • the size and shape of the recesses are preferably selected so that the function of the belt is not affected during operation of the belt drive.
  • the recesses may be designed as unilaterally open slots, in which engages at least a portion of the belt.
  • the invention further relates to a drive train of a motor vehicle, as disclosed, for example, in German Offenlegungsschrift DE 10 2007 021 233 A1.
  • the power transmission unit described therein is replaced by the crankshaft pulley according to the invention.
  • Figure 1 is a greatly simplified representation of a drive train of a motor vehicle with a crankshaft pulley according to the invention
  • Figure 2 shows a detail of Figure 1 with a view of an indicated belt
  • Figure 3 is a detailed view of the crankshaft pulley of Figures 1 and 2 in longitudinal section.
  • crankshaft pulley 1 is shown in various views.
  • the crankshaft pulley 1 includes a pulley track 2, which is also referred to as a pulley or belt track for short, for example, for coupling a belt of a belt drive to a belt starter generator and / or at least one accessory such as an air conditioning compressor.
  • the crankshaft pulley 1 is in the drive train of a motor vehicle, as disclosed for example in the German patent application DE 10 2007 021 233 A1, at a Kur- Belwe! le 4 attached, which is rotatable about a rotation axis 5.
  • the motor vehicle is, for example, a hybrid vehicle with an internal combustion engine and an electric machine, which is embodied in particular as a generator.
  • the hybrid vehicle may be driven by the internal combustion engine alone or by the electric machine alone.
  • a pulley freewheel 6 is integrated in the crankshaft pulley 1.
  • the belt disk freewheel 6 is effective between the belt track 2 and the crankshaft 4.
  • the pulley freewheel 6 serves to damp torque shocks in the generator operation of the crankshaft pulley.
  • a Tilgermassenvic 7 is further integrated.
  • the absorber mass carrier 7 is fixedly connected to the crankshaft 4.
  • a damper mass 9 is mounted radially on the outside of the absorber mass carrier 7.
  • the absorber mass 9 represents a Kurbelwellentilger, which serves to eliminate unwanted torque oscillations, torque irregularities and / or torque shocks to protect the crankshaft during operation of the internal combustion engine.
  • a transmission 10 is further integrated, which is preferably designed as a planetary gear.
  • the planetary gear 10 includes a lockable on a crankcase 25 ring gear 11. With the ring gear 11 meshing planetary gears 12 which are rotatably mounted on a planet carrier 13. The planet gears 2 further mesh with a sun gear 14 which is integrated with the ring gear 11, the planetary gears 12 and the planet carrier 13 in the crankshaft pulley 1.
  • the crankshaft pulley 1 shown in Figures 1 and 2 comprises a braking device 20, which is designed as an electric brake, in particular as a frictional magnetic brake.
  • the braking device 20 comprises a stationary coil carrier 22 which carries a coil 23 and is fastened via a connecting element 24 to a crankcase 25 in the drive train of the motor vehicle.
  • the fixed bobbin 22 represents a first friction partner of the brake device 20.
  • An anchor body 28 represents a second friction partner of the brake device 20.
  • the anchor body 28 is movable relative to the bobbin 22 in the axial direction. When the anchor body 28 is spaced axially from the stationary bobbin 22, the anchor body 28 may rotate relative to the bobbin 22.
  • the internal combustion engine which is also referred to as an internal combustion engine, in a so-called start / stop operation or in a purely electric driving of the hybrid vehicle, stands still, that is, does not output torque
  • the brake device 20 can enter through the starter generator via the belt drive attached air conditioning compressor for stationary air conditioning.
  • the starter generator can set the crankshaft 4 in rotation via the belt drive and the planetary gear 10, whereby the internal combustion engine is started.
  • the planetary gear 10 the provided via the belt drive by the starter generator torque is increased, whereby a cold start of the brake motor is made possible.
  • the braking device 20 is opened again.
  • the starter generator can be driven by the crankshaft 4 via the pulley free wheel 6. This operation is also referred to as regenerative operation. In this case, crankshaft vibrations are damped by the pulley freewheel 6.
  • the pulley free-wheel 6 comprises an inner ring 41 and an outer ring 42.
  • the inner ring 41 of the belt disk freewheel 6 is fastened to the crankshaft (not shown in FIG. 2) by means of a mounting screw 44.
  • the outer ring 42 is rotatably supported by a rolling bearing 45 designed as a ball bearing on a screw head of the mounting screw 44.
  • the outer ring 42 is rotatably supported on the inner ring 41 of the pulley freewheel 6 by means of a rolling bearing 46 designed as a roller bearing.
  • the Tilgermassenvic 7 is attached to the inner ring 41 of the pulley freewheel 6.
  • the planetary carrier 13 is also secured to the inner ring 41 of the pulley freewheel 6 via an axial connecting portion 48 and a radial flange 49. As a result, the planet carrier 13 is also firmly connected to the crankshaft.
  • the outer ring 42 of the pulley freewheel 6 is connected via a connecting flange 60 fixed to the belt track 2.
  • the belt track 2 is integrally connected to the connecting flange 60.
  • the sun gear 14 of the planetary gear 10 is attached to the outer ring 42.
  • the ring gear 11 of the planetary gear 10 is mounted radially inward on the connecting element 29 of the anchor body 28 of the braking device 20.
  • the pulley freewheel 6, which is arranged parallel to the roller bearings 45, 46, is not designed to be centrifugal force-releasing.
  • the inner ring 41 of the pulley freewheel 6 is connected to the planet carrier 13 of the planetary gear 10.
  • the mounted on the planet carrier 13 planetary gears 12 mesh with the ring gear 11, which is connected via a connecting element 29 with the armature disk designed as anchor body 28.
  • the anchor body 28 is arranged together with the coil carrier 22 radially outside the belt track 2 of the crankshaft pulley 1.
  • the coil carrier 22, as can be seen in FIG. 1 is arranged on a side of the anchor body 28 facing away from the crankcase 25.
  • a belt 30 of the belt drive partially extends through the bobbin 22.
  • belt 30 is guided through two recesses 31, 32, which are provided in the bobbin 22.
  • the two recesses 31, 32 are designed as unilaterally open slots whose arrangement and size are adapted to the size and arrangement of the belt 30.
  • the belt 30 in the recesses 31, 32 of the bobbin 22 sufficient clearance, so that the function of the belt 30 is not affected during operation of the belt drive.
  • the brake device 20 is actuated only for a short period of time during a combustion start, that is, when the internal combustion engine, which is also referred to as an internal combustion engine, is started by the starter generator. Therefore, the bobbin 22, which is also referred to as a bobbin, in relation to the anchor body 28, which is also referred to as a yoke, small dimensions.
  • the bobbin 22 projects radially outside the belt track 2 in an axial direction into the region of the belt track 2 such that the bobbin 22 and the belt track 2 partly overlap in the axial direction.
  • the overlap in the axial direction is made possible by the recesses 31, 32. This provides the advantage that a particularly compact construction, in particular in the axial direction, of the crankshaft pulley 1 is made possible.
  • the normally open brake device 20 is energized and thereby closed.
  • a torque applied to the belt track 2 via the starter generator and the belt 30 is transmitted to the sun gear 14 of the planetary gear 10.
  • the ring gear 11 is braked by the closed brake device 20
  • an increased torque is generated on the planet carrier 13, which sets the crankshaft 4 of the internal combustion engine to start in rotation.
  • the pulley freewheel 6 is overtaken in this operating state, which is also referred to as a starter generator mode, in the freewheeling direction.
  • the energization of the braking device 20 is turned off. By appropriate springing the brake device 20 is opened, so that no more torque can be transmitted via the brake device 20. Then, the torque provided by the crankshaft 4 is transmitted to the belt track 2 via the pulley freewheel 6 closing in this torque direction in the case of positive torque surges for driving the belt drive. In this operating state, the generator can be driven by the internal combustion engine and an electrical energy storage can be charged.
  • the belt drive due to its inertia, can overtake the crankshaft 4 through the pulley freewheel 6, thus ensuring the function of the pulley damping and service life increase of the belt 30 and the units connected thereto.
  • the planetary gear 10 is decoupled due to the open brake device 20 on the ring gear 1 1, so that no torque transmission takes place on the planet carrier 13.
  • the pulley freewheel 6 only the ring gear 11 can rotate freely.
  • the planetary gears 12 can be sprung in the axial direction via friction plates.
  • the planetary gear - Eg be 10 can also be performed in other ways rattle and / or play.
  • the belt track 2 can rotate freely in one direction, since the pulley freewheel 6 can overtake.
  • the starter generator can drive an air conditioning compressor connected to the belt drive when the crankshaft 4 is stationary, in order to display the auxiliary air conditioning function.
  • the ring gear 11 of the planetary gear 10 can rotate in an opposite direction of rotation to the belt track 2.
  • the frictional braking device 20 is energized with rotating belt track 2 and closed. As a result, the internal combustion engine can be started. A braking of the belt track 2 for closing the brake device 20 is not required. As a result, an operating state designated as a change of mind can also be represented. As a change of mind operating state stopping and restarting the internal combustion engine is called before the crankshaft 4 has come to a standstill.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Automation & Control Theory (AREA)
  • Pulleys (AREA)
  • Retarders (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

La présente invention concerne une poulie à courroie de vilebrequin destinée à transmettre un couple de rotation entre un vilebrequin et un mécanisme d'entraînement à courroie, comprenant au moins une roue libre et un engrenage. L'invention se caractérise en ce que l'engrenage à l'intérieur de la poulie à courroie de vilebrequin est combiné à un dispositif de freinage à l'extérieur de la poulie à courroie de vilebrequin.
PCT/DE2011/001213 2010-06-29 2011-06-14 Poulie à courroie de vilebrequin WO2012000469A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112011102227T DE112011102227A5 (de) 2010-06-29 2011-06-14 Kurbelwellenriemenscheibe

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102010025437 2010-06-29
DE102010025437.1 2010-06-29
DE102010049924.2 2010-10-28
DE102010049924 2010-10-28

Publications (2)

Publication Number Publication Date
WO2012000469A2 true WO2012000469A2 (fr) 2012-01-05
WO2012000469A3 WO2012000469A3 (fr) 2012-08-09

Family

ID=45115953

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2011/001213 WO2012000469A2 (fr) 2010-06-29 2011-06-14 Poulie à courroie de vilebrequin

Country Status (2)

Country Link
DE (2) DE102011104242A1 (fr)
WO (1) WO2012000469A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011010091A1 (de) * 2011-02-01 2012-08-02 Audi Ag Kraftfahrzeug mit Riementrieb und Planetengetriebe zwischen Verbrennungskraftmaschine und elektrischer Maschine
DE102012202308A1 (de) * 2012-02-15 2013-08-22 Iwis Motorsysteme Gmbh & Co. Kg Getriebe sowie Verfahren zum Betreiben eines Getriebes
DE102013203009B4 (de) 2013-02-25 2021-09-16 Bayerische Motoren Werke Aktiengesellschaft Riementriebvorrichtung für einen Starter-Generator

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007021233A1 (de) 2006-05-17 2007-11-22 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Antriebsstrang, insbesondere für ein Kraftfahrzeug

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3338417C1 (de) * 1983-10-22 1985-04-18 Daimler-Benz Ag, 7000 Stuttgart Planetenraeder-Hilfsgetriebe fuer ein Kraftfahrzeug
JPS60209307A (ja) * 1984-04-03 1985-10-21 Nissan Motor Co Ltd 可変速補機駆動装置の変速制御方法
JP3810345B2 (ja) * 2002-06-04 2006-08-16 三菱電機株式会社 車両用伝動制御装置

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007021233A1 (de) 2006-05-17 2007-11-22 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Antriebsstrang, insbesondere für ein Kraftfahrzeug

Also Published As

Publication number Publication date
DE112011102227A5 (de) 2013-06-06
DE102011104242A1 (de) 2011-12-29
WO2012000469A3 (fr) 2012-08-09

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