WO2012010113A2 - Poulie de vilebrequin - Google Patents

Poulie de vilebrequin Download PDF

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Publication number
WO2012010113A2
WO2012010113A2 PCT/DE2011/001214 DE2011001214W WO2012010113A2 WO 2012010113 A2 WO2012010113 A2 WO 2012010113A2 DE 2011001214 W DE2011001214 W DE 2011001214W WO 2012010113 A2 WO2012010113 A2 WO 2012010113A2
Authority
WO
WIPO (PCT)
Prior art keywords
crankshaft
crankshaft pulley
torque
pulley
coupling
Prior art date
Application number
PCT/DE2011/001214
Other languages
German (de)
English (en)
Other versions
WO2012010113A3 (fr
Inventor
Peter Greb
Lászlo 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 DE112011102218T priority Critical patent/DE112011102218A5/de
Publication of WO2012010113A2 publication Critical patent/WO2012010113A2/fr
Publication of WO2012010113A3 publication Critical patent/WO2012010113A3/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
    • 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
    • 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
    • F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
    • F16D27/10—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings
    • F16D27/108—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with axially movable clutching members
    • F16D27/112—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with axially movable clutching members with flat friction surfaces, e.g. discs
    • 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 planetary gear.
  • 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 achieved in a crankshaft pulley for transmitting torque between a crankshaft and a belt drive, with at least one freewheel and a planetary gear, characterized in that the planetary gear in the crankshaft pulley is combined with a coupling device.
  • a coupling device different operating modes, for example a starter generator and / or a stationary air conditioning, can be realized in a simple manner.
  • the coupling device makes it possible to decouple the planetary gear in certain operating states, such as stationary air conditioning.
  • a preferred embodiment of the crankshaft pulley is characterized in that the clutch means comprises a sun gear clutch which transmits a torque between a belt track of the crankshaft pulley and a sun gear of the planetary gear in a torque transmitting position.
  • the sun gear clutch can be opened and closed, for example by a sliding sleeve. When closed, the sun gear clutch transmits torque.
  • a further preferred exemplary embodiment of the crankshaft pulley is characterized in that the clutch device comprises a planet carrier clutch which transmits a torque between the crankshaft and a planet carrier of the planetary gear in a torque transmission position.
  • the coupling device comprises a planetary carrier coupling, which transmits a torque between an axial slide and a planet carrier of the planetary gear in a torque transmission position.
  • a ring gear of the planetary gear is preferably mounted fixed to the housing, for example, attached to a crankcase.
  • crankshaft pulley is characterized in that the sun gear and the planet carrier clutch can be actuated via the axial slide, which is rotatably connected to the crankshaft.
  • the actuation of the axial slide is preferably rotationally coupled via a housing-fixed axial actuator, for example hydraulically or electrically. In a neutral position of the Axial sc hiebers both the planet carrier clutch and the sun gear clutch are open.
  • crankshaft pulley is characterized in that the planet carrier coupling and the sun gear enable torque transmission by positive engagement.
  • the two clutches are designed for example as jaw clutches. Through the axial slide both clutches can be closed.
  • the two positive clutches are preferably not together, but closed one after the other.
  • the sun gear is preferably closed before the Pianeten agokupplung.
  • crankshaft pulley is characterized in that the clutch means comprises an electromagnetically operable clutch which transmits torque in a torque transmission position between a belt track of the crankshaft pulley and a sun gear of the planetary gear.
  • the sun gear of the planetary gear meshes with planet gears, which are rotatably mounted on a planet carrier.
  • the planet gears also mesh with a ring gear, which is preferably fixed to the housing, for example, on a crankcase mounted.
  • crankshaft pulley comprises a fixed bobbin with a coil for actuating the clutch.
  • Fixed means that the bobbin is fixed relative to the crankshaft pulley.
  • the bobbin on a support structure, for example on a crankcase, outside the crankshaft pulley attached.
  • 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 clutch comprises a friction ring which is rotatably mounted relative to the fixed bobbin and fixedly connected to the sun gear of the planetary gear.
  • the friction ring represents a first friction partner of the clutch.
  • crankshaft pulley Another preferred embodiment of the crankshaft pulley is characterized in that the clutch comprises an anchor ring which is non-rotatably connected to the belt track of the crankshaft pulley.
  • the anchor ring represents a second friction partner of the coupling.
  • crankshaft pulley comprises a gear freewheel and / or a pulley freewheel.
  • the transmission freewheel is preferably arranged between the crankshaft and the planet carrier of the planetary gear.
  • the pulley freewheel is preferably arranged between the crankshaft and the belt track of the crankshaft pulley.
  • 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.
  • FIG. 1 shows a greatly simplified representation of a drive train of a motor vehicle with a crankshaft pulley according to a first embodiment
  • Figure 2 shows a similar drive train as in Figure 1 with a crankshaft pulley according to a second embodiment and Figure 3 is a detailed view of the crankshaft pulley of Figure 2 in longitudinal section.
  • crankshaft pulley 1; 41 shown in various embodiments in accordance with various embodiments.
  • the crankshaft pulley 1; 41 includes a pulley track 2; 42, which is also abbreviated to pulley or belt track, 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; 41 is in the drive train of a motor vehicle, as it is disclosed, for example, in the German patent application DE 10 2007 021 233 A1, on a crankshaft 4; 44 attached, which rotate about a rotation axis 5 rotatably.
  • crankshaft pulley 1; 41 is a pulley freewheel 6; 46 integrated.
  • the pulley freewheel 6; 46 is between the belt track 2; 42 and the crankshaft 4; 44 effective.
  • the function of the pulley freewheel 6; 46 will be described below with reference to the individual embodiments.
  • crankshaft pulley 1; 41 is further a Tilgermassenvic 7; 47 integrated.
  • the Tilgermassenange 7; 47 is fixed to the Kurbeiwelle 4; 44 connected.
  • a damper mass 9; 49 attached with the interposition of a rubber track 8; 48 is radially outward on the Tilgermassenvic 7; 47 a damper mass 9; 49 attached.
  • the absorber mass 9; FIG. 49 illustrates a crankshaft reducer that serves to cancel unwanted torque oscillations, torque nonuniformities, and / or torque surges of the crankshaft 14, 144 of an internal combustion engine.
  • the crankshaft pulley 1; 41 is further a planetary gear 10; 50 integrated.
  • the planetary gear 10; 50 comprises a housing-fixed ring gear 11; 51. Housing solid means fixed. With the ring gear 11; 51 mesh planet gears 12; 52, on a planetary carrier 13; 53 are rotatably mounted.
  • the Pfanetenzier 12; 52 further mesh with a sun gear 14; 54, which together with the ring gear 11; 51, the planet gears 12; 52 and the planet carrier 13; 53 in the crankshaft pulley 1; 41 is integrated.
  • the crankshaft pulley 1 shown in FIG. 1 comprises a clutch device 20 with a sun gear clutch 21 and a planet carrier clutch 22.
  • the clutch device 20 is actuated with an axial slide 24.
  • the axial slide 24 will turn actuated by an axial actuator 25, the axial actuator 25 is fixed to the housing, for example, on the crankcase mounted.
  • An actuator spring 26 is connected in parallel with the axial actuator 25.
  • An inner ring of the pulley freewheel 6 is fixed, for example by means of a mounting screw, to the crankshaft 4 of an internal combustion engine.
  • an outer ring of the pulley freewheel 6, for example by means of rolling bearing devices, rotatably mounted.
  • the belt track 2 is attached.
  • the sun gear clutch 21 is designed as a form-locking coupling, for example as a dog clutch.
  • a first coupling partner 31 of the sun gear clutch 21 is fixedly connected to the belt track 2.
  • a second coupling partner 32 of the sun gear 21 is fixedly connected to the sun gear 14 of the planetary gear 10.
  • the sun gear clutch 21 is opened and closed by a sliding sleeve which is rotationally actuated by the axial slide 24 via this.
  • a first coupling partner 35 of the positive planetary carrier coupling 22 is attached.
  • a second coupling partner 36 of the planetary carrier coupling 22 is connected to the planet carrier 13.
  • the actuation of the planet carrier coupling 22 also takes place via axial displacement of the axial slide 24, which is non-rotatably connected to the crankshaft 4.
  • the actuation of the axial slide 24 is rotationally coupled via the crankcase fixed axial actuator 25.
  • the sun gear clutch 21 When the axial slide 24 is displaced by the axial actuator 25, the sun gear clutch 21 first of all spurts. If, for example, positive-locking element is on interlocking element, in particular a tooth on tooth, then the sun gear coupling 21 only spurts in if a position is approached beforehand by a slight rotation of the belt track 2, which permits a meshing of the sun gear coupling 21.
  • the planet carrier clutch 22 spurts after the sun gear 21 a. If the planet carrier coupling 22 tooth is on tooth, then the planet carrier coupling 22 only then, if previously by a slight rotation of the planet carrier 13, initiated through the belt track 2, a position has been reached, which allows a meshing of the planetary carrier coupling 22.
  • a low torque acting on the belt track 2 is converted via the planetary gear 10 into a relatively large torque on the planet carrier 13, which is transmitted to the crankshaft 4 via the closed planet carrier clutch 22. Due to the greater speed of the belt track 2 relative to the planet carrier 13, the pulley freewheel 6 is in active planetary gear 10 in overtaking.
  • the axial slide 24 is moved by means of the axial actuator 25 in its neutral position, in which both clutches 21, 22 are opened.
  • a belt-driven starter generator can hold the belt track 2 at a synchronous speed of planet carrier 13 and crankshaft 4 until both clutches 21, 22 are spoked out, wherein a load-free or low-load operation for coupling is preferred.
  • the torque of the crankshaft 4 is transmitted to the belt track 2 via the pulley freewheel 6 closing in this torque direction in the event of positive torque surges in order to drive the belt drive and a generator arranged therein.
  • negative torque surges of the belt drive can overtake the crankshaft 4 due to its inertia through the pulley freewheel 6, whereby the function of the pulley damping and service life of the belt and the attached units is ensured.
  • crankshaft pulley 41 comprises an electromagnetically actuated coupling device 60 with a bobbin 61.
  • the bobbin 61 carries a bobbin of a coil 62.
  • the bobbin 61 is also referred to as the yoke of the electrically or electromagnetically actuated coupling device 60. Since the bobbin of the coil 62 is within the housing-fixed bobbin 61, a rotary feedthrough for supplying power to the coil 62 can be omitted.
  • a friction ring 63 also referred to as a yoke ring, is rotatable relative to the fixed bobbin 61 to form an air gap.
  • the air gap serves to ensure friction-free operation. In this case, the air gap should be as small as possible in order to pass through the electrical flow when operating the coupling device 60 well.
  • the friction ring 63 is fixedly connected to the sun gear 54 and represents a first friction partner of the coupling device 60.
  • An anchor ring 64 represents a second friction partner of the coupling device 60.
  • the anchor ring 64 is connected in a rotationally fixed manner to the belt track 42 by means of armature springs 65, which are preferably designed as leaf springs.
  • armature springs 65 By the armature springs 65, the anchor ring 64 is biased away from the friction ring 63, so that the coupling device 60 is kept open in the de-energized state.
  • the armature ring 64 is magnetically attracted to frictionally engage the friction ring 61.
  • a rotationally fixed connection between the belt track 42 and the sun gear 54 is created.
  • the pulley freewheel 46 is preferably not executed centrifugal force.
  • a likewise integrated into the crankshaft pulley 41 transmission freewheel 68 is advantageously carried out centrifugal force lifting.
  • the transmission freewheel 68 preferably has to be active only at start speeds of the crankshaft 44. By the fiehkraftabriolde execution of the gear freewheel 68 friction and / or drag losses can be minimized at higher speeds.
  • the pulley freewheel 46 comprises an inner ring 70, which is connected by means of a mounting screw 71 fixed to the crankshaft 44 of the internal combustion engine.
  • an outer ring 75 of the pulley free-wheel 46 is supported by means of two rolling bearings 73, 74.
  • a radial flange 76 extends radially outwardly, which is fixedly connected to a further radial flange 77, which extends from the belt track 42 radially inwardly.
  • the anchor ring 64 rotatably, but limited in the axial direction displaceable attached.
  • the friction ring 63 is rotatably supported by means of a bearing device 79.
  • the bearing device 79 is supported on a support member 80 which is fixedly connected to the ring gear 51.
  • the ring gear 51 in turn is fixedly connected to the coil carrier 61.
  • the bobbin 61 is, as seen in Figure 3, attached via a connecting element 81 fixed to an indicated crankcase 82.
  • the inner ring 70 of the pulley freewheel 46 is fixedly connected via the connecting body 72 and a flange 83 with an outer ring 85 of the Getriebeoklaufs 68.
  • the outer ring 85 is formed radially inward on the Tilgermassen 1985.
  • An inner ring 84 of the gearbox 68 is fixedly connected to the planet carrier 53.
  • the clutch device 60 must be able to transmit only the pulley torque for the starting operation during operation of the crankshaft pulley 41. Therefore, a particularly compact construction can be achieved.
  • the increased by the planetary gear 50 moments are supported on the ring gear 51 against the crankcase 62 and transmitted to the planetary carrier 52 via the compactly built gear freewheel 68 on the crankshaft 44.
  • air gap between the bobbin 61 and the friction ring 63 makes it possible to run the designated as yoke coil support 61 and the friction ring 63 also referred to as a yoke ring in the radial direction particularly small.
  • the bearing 79 of the bobbin 61 and the friction ring 63 can be stored exactly relative to each other.
  • the coupling device 60 which is normally opened by the armature springs 65, is energized and closed via the coil 62.
  • the torque applied via the starter generator and the belt of the belt drive to the belt track 42 is transmitted to the sun gear 54 of the planetary gear 50.
  • the ring gear 51 is mounted fixed to the housing, an increased torque on the planet carrier 53 is generated.
  • the thus turned in the reverse direction gear freewheel 68 locks and transmits the excessive torque to start on the crankshaft 44.
  • the pulley freewheel 46 is overhauled in this operating condition.
  • the energization of the coil 62 of the coupling device 60 is interrupted.
  • the coupling device 60 Due to the bias of the armature springs 65, the coupling device 60 is opened, so that no more torque can be transmitted. Now, the torque of the crankshaft 44 is transmitted via the closing in this torque direction pulley freewheel 46 at positive torque pulses on the belt track 42 to drive the belt drive and the generator disposed therein.
  • the belt drive can overhaul the crankshaft 44 due to its inertia through the pulley freewheel 46, whereby the function of the pulley damping and an increase in service life of the belt and the units connected thereto can be represented.
  • the clutch device 60 If the clutch device 60 is not energized, that is to say opened, then the peg transmission 50 on the sun gear 54 is decoupled from the belt track 42. At low speeds, the gear freewheel 68 is in overtaking. At high speeds, the gearbox freewheel lifts due to centrifugal force. As a result, the planet carrier 53 is decoupled from the crankshaft 44. Consequently, no torque is transmitted to the planet carrier 53 at high rotational speeds, so that the planetary gear 50 does not rotate. Unwanted vibrations and / or rattle noise of the decoupled planetary gear 50 are prevented by appropriate seal and bearing friction.
  • the belt track 2 can rotate freely in one direction, since the pulley freewheel 46 can overtake.
  • the starter generator can drive an air conditioning compressor connected to the belt drive when the crankshaft 44 is stationary, as a result of which the auxiliary air conditioning function is shown.
  • Coupling device Coil carrier

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Pulleys (AREA)

Abstract

L'invention concerne une poulie de vilebrequin conçue pour transmettre un couple entre un vilebrequin et un entraînement de courroie, comprenant au moins une roue libre et une boîte planétaire. Cette invention est caractérisée en ce que la boîte planétaire est combinée avec un dispositif de transmission dans la poulie de vilebrequin.
PCT/DE2011/001214 2010-06-29 2011-06-14 Poulie de vilebrequin WO2012010113A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112011102218T DE112011102218A5 (de) 2010-06-29 2011-06-14 Kurbelwellenriemenscheibe

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102010025435 2010-06-29
DE102010025435.5 2010-06-29
DE102010031957.0 2010-07-22
DE102010031957 2010-07-22

Publications (2)

Publication Number Publication Date
WO2012010113A2 true WO2012010113A2 (fr) 2012-01-26
WO2012010113A3 WO2012010113A3 (fr) 2012-04-12

Family

ID=44907693

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2011/001214 WO2012010113A2 (fr) 2010-06-29 2011-06-14 Poulie de vilebrequin

Country Status (2)

Country Link
DE (2) DE102011104144A1 (fr)
WO (1) WO2012010113A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012075981A1 (fr) * 2010-12-02 2012-06-14 Schaeffler Technologies AG & Co. KG Poulie de vilebrequin

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012216231B3 (de) * 2012-09-13 2013-12-05 Schaeffler Technologies AG & Co. KG Planetengetriebe mit einer Kupplungseinrichtung sowie Getriebeeinrichtung für ein Fahrzeug mit dem Planetengetriebe
DE102014206985A1 (de) * 2013-04-19 2014-10-23 Schaeffler Technologies Gmbh & Co. Kg Kupplungsaktor
FR3012194B1 (fr) * 2013-10-23 2016-12-09 Renault Sa Systeme de transmission pour moteur de combustion interne avec alterno-demarreur

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

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Publication number Priority date Publication date Assignee Title
US4800780A (en) * 1985-12-17 1989-01-31 G.E. Machine Tool Limited Accessory transmission
AT4792U1 (de) * 2000-05-17 2001-11-26 Tesma Motoren Getriebetechnik Reduktionsgetriebe für einen starter-generator einer verbrennungskraftmaschine
JP3712926B2 (ja) * 2000-08-28 2005-11-02 三菱電機株式会社 車両用交流発電機
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
WO2007116220A1 (fr) * 2006-04-08 2007-10-18 Integral Powertrain Ltd Systèmes de transmission
EP2549139B1 (fr) * 2008-04-04 2014-03-12 Litens Automotive Partnership Transmission à deux rapports à sélection automatique

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012075981A1 (fr) * 2010-12-02 2012-06-14 Schaeffler Technologies AG & Co. KG Poulie de vilebrequin

Also Published As

Publication number Publication date
WO2012010113A3 (fr) 2012-04-12
DE102011104144A1 (de) 2011-12-29
DE112011102218A5 (de) 2013-04-04

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