WO2011124193A1 - Poulie à courroie de vilebrequin - Google Patents

Poulie à courroie de vilebrequin Download PDF

Info

Publication number
WO2011124193A1
WO2011124193A1 PCT/DE2011/000254 DE2011000254W WO2011124193A1 WO 2011124193 A1 WO2011124193 A1 WO 2011124193A1 DE 2011000254 W DE2011000254 W DE 2011000254W WO 2011124193 A1 WO2011124193 A1 WO 2011124193A1
Authority
WO
WIPO (PCT)
Prior art keywords
pulley
freewheel
crankshaft
ramp
crankshaft pulley
Prior art date
Application number
PCT/DE2011/000254
Other languages
German (de)
English (en)
Inventor
Peter Greb
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 DE112011101221T priority Critical patent/DE112011101221A5/de
Publication of WO2011124193A1 publication Critical patent/WO2011124193A1/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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/04—Freewheels or freewheel clutches combined with a clutch for locking the driving and driven 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
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
    • F16D43/202—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type
    • F16D43/2022—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with at least one part moving axially between engagement and disengagement
    • F16D43/2024—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with at least one part moving axially between engagement and disengagement the axially moving part being coaxial with the rotation, e.g. a gear with face teeth
    • 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
    • F16D47/00—Systems of clutches, or clutches and couplings, comprising devices of types grouped under at least two of the preceding guide headings
    • F16D47/04—Systems of clutches, or clutches and couplings, comprising devices of types grouped under at least two of the preceding guide headings of which at least one is a freewheel

Definitions

  • German patent application DE 195 35 889 A1 discloses a one-way clutch is known, which is arranged between a pulley and a shaft.
  • the known overrunning clutch is suitable for driving a generator and is part of a pulley, which serves to drive the generator.
  • By using the one-way clutch an internal damping is made possible, so that the torque transmission of the traction mechanism is improved.
  • European Patent EP 0 980 479 B1 discloses a belt drive system having a generator clutch freewheel clutch comprising a torsion coil spring and a one-way clutch mechanism. As a result, the driving torques of the generator pulley can be transmitted to a hub yielding. In addition, the generator pulley can be uncoupled from the hub in one direction.
  • German patent DE 196 36 628 C1 a freewheel with a clamping body is known, which is formed by a circumferentially extending gap, elastically deformed coil spring.
  • European Patent EP 0 782 674 B1 discloses a crank-shaft decoupler with a directionally switched clutch which serves to selectively transmit rotational forces between a mounting hub and a pulley.
  • German Offenlegungsschrift DE 10 2005 029 351 A1 discloses a drive wheel for driving an auxiliary unit of an internal combustion engine with a damping device.
  • the object of the invention is to provide a space-neutral solution for a decoupled from the crankshaft crankshaft pulley according to the preamble of claim 1.
  • the crankshaft pulley according to the invention should in particular a start-stop operation, a stationary climate and generator operation, preferably with a pulse starting possibility including Kurbelwellentilger, and / or damping of rotational irregularities in the belt drive, allow.
  • a crankshaft pulley for transmitting a torque between a crankshaft and a belt drive, with a pulley freewheel, characterized in that the pulley freewheel in the crank pulley with a is combined by an actuated clutch operable clutch, through which the pulley freewheel can be bridged.
  • the pulley freewheel is designed to lock when the crankshaft is rotating in the forward direction of rotation.
  • the direction of forward rotation of the crankshaft is, for example, referred to as the forward direction of rotation when the crankshaft is driven by an internal combustion engine of a motor vehicle.
  • the pulley freewheel has a reverse direction. In the opposite direction of rotation of the freewheel acts.
  • a preferred embodiment of the crankshaft pulley is characterized in that the coupling is designed positively.
  • the clutch is preferably designed as a dog clutch with two clutch partners, which are brought into positive engagement with each other for torque transmission. To generate the positive connection, one of the coupling partners is preferably moved in the axial direction toward the other coupling partner in order to connect the two coupling partners in a rotationally fixed manner to one another.
  • crankshaft pulley is characterized in that the clutch is actuated by a ramp mechanism.
  • the ramp mechanism is operated, for example, when the pulley or a pulley track rotates in the reverse direction.
  • the ramp mechanism via the actuating freewheel to a fixed housing part can be connected or connected.
  • the stationary housing part is preferably a crankcase in the engine compartment of the motor vehicle.
  • crankshaft pulley is characterized in that the ramp mechanism has at least one plateau with a shoulder to a maximum of the ramp.
  • the ramp with the ramp valley and the plateau with the shoulder are preferably arranged in the circumferential direction in a recurring order.
  • crankshaft pulley is characterized in that the coupling is designed to be self-opening by the spring device. With the help of the ramp mechanism, the clutch is closed at least for the duration of a startup process for starting the internal combustion engine.
  • crankshaft pulley comprises a coupling ring which, with the aid of pretensioned ten leaf springs is connected to a pulley track.
  • the leaf springs represent the previously described spring device.
  • FIG. 1 shows a crankshaft pulley according to the invention in a first longitudinal section
  • FIG. 2 shows the crankshaft pulley from FIG. 1 in a second longitudinal section
  • FIGS. 1 to 3 show a crankshaft pulley 1 according to the invention in various sectional views.
  • the crankshaft pulley 1 includes a pulley track 2, which is also referred to as a pulley or belt track for a short time and serves to couple a belt (not shown) of a belt drive to a belt starter generator and, alternatively, additionally to an air conditioning compressor.
  • the crankshaft pulley 1 is attached to a crankshaft 4 of a motor vehicle by means of a central screw 5, which is also referred to as a crankshaft screw.
  • the crankshaft 4 is driven by an internal combustion engine, which is also referred to as an internal combustion engine.
  • the freewheel inner ring has radially outer bearing races for different rolling elements of a bearing device 20.
  • the bearing device 20 is designed as a combined roller / ball bearings, by which a freewheel outer ring 22 is rotatably mounted on the central screw 5 and the crankshaft 4.
  • freewheel rollers 23 of the pulley freewheel 8 are arranged in the radial direction between the freewheel inner ring 18 and the freewheel outer ring.
  • the pulley freewheel 8 is preferably designed as a roller freewheel with a locking direction and a freewheeling direction.
  • the pulley track 2 can be driven via the pulley freewheel 8 in the reverse direction. In the opposite direction of rotation opens the pulley freewheel 8, so that no torque can be transmitted. With the clutch 10, the pulley freewheel 8 can be bridged.
  • a flange 24 extends radially outward.
  • a Tilgerflansch 26 is fastened by means of rivet connection elements 25, which extends from the rivet connection element 25 radially outwardly.
  • the Tilgerflansch 26 passes radially outward into a hollow cylinder section 27, which is arranged parallel to the axis of rotation of the crankshaft pulley 1.
  • the absorber mass 14 is mounted with the interposition of a rubber track 28.
  • the other ends of the leaf springs 36 are fastened to the coupling ring 34 by means of rivet connection elements 38.
  • the leaf springs 36 provide a rotationally fixed connection between the coupling ring 34 and the pulley track 2.
  • the leaf spring members 36 allow axial movement of the coupling ring 34 relative to the pulley track 2 in the axial direction.
  • the support of the axial force on the crankcase 50 is not critical, since the relevant components do not rotate relative to each other in this state.
  • a relatively weak (not shown) additional spring may be provided which slightly pushes a ramp disc of the ramp mechanism 40 in normal operation away from the crankcase 50 in order to avoid drag losses.
  • the dog clutch 10 tooth on tooth or claw is on claw, it closes under biasing force of the spring means 35 in a renewed forward rotation of the pulley track 2. Otherwise, the dog clutch 10 is closed directly upon actuation of the operating freewheel 45 via the ramp mechanism 40, so that the
  • Internal combustion engine can be started via the belt drive from the starter generator.
  • the ramp mechanism 40 comprises, as is indicated in greatly simplified form in FIG. 4, a ramp with a ramp valley and a ramp plateau, which is offset slightly downwards relative to the maximum of the ramp.
  • the ramp plateau drops steeply into the following Rampental.
  • the group Rampental, ramp, heel, Rampenplateau can also be several times distributed over the circumference provided on the ramp mechanism.
  • the pressure piece 39 In the operating states of generator operation and stationary air conditioning, the pressure piece 39 is held as a counter partner of the ramp mechanism 40 by the biasing force of the spring means 35 in the ramp valley. In a reverse rotation of the pulley track 2, the pressure piece 39 is moved along the ramp and performs an axial movement. At the end of the ramp, the pressure piece 39 is moved by the spring means 35 to the slightly lower ramp plateau. The heel prevents unwanted slippage or retraction along the ramp.
  • the starter generator is rotated in the opposite direction, so that the internal combustion engine can be started. Due to torsional vibrations, the pressure piece 39 can rotate with respect to the ramp part away from the ramp, since the actuating freewheel 45 prevents the pressure piece 39 from entraining the ramp part by friction. Torsional vibrations in the other direction cause the pressure piece 39 entrains the ramp part due to friction. As a result, the pressure piece 39 moves along the Rampenplateaus to the end. There it is pressed by the spring device 35 back into the Rampental and opens the dog clutch.
  • the length of the ramp plateau is designed in dependence on the number and the size of the torsional vibrations, which are known for example from simulations of tests, so that the dog clutch 10 remains securely meshed, at least for the duration of the starting process.
  • the pressure piece 39 is moved due to torsional vibrations further up to the Rampental.
  • the internal combustion engine When the internal combustion engine is running, it can transmit torque via the pulley freewheel 8 to the pulley track 2 and thus to the starter generator connected thereto for charging the battery. Rotationsuniformity of the internal combustion engine are thereby damped in that the pulley freewheel 8 transmits only the acceleration phases of the rotational irregularities, but in the deceleration phases is overtaken by the inertia of the belt drive.
  • This operating state is also referred to as generator operation.
  • FIG. 4 shows various operating modes I to IV of the crankshaft pulley 1 from FIGS. 1 to 3 as a linear model.
  • the ramp mechanism 40 In stationary climate mode I, the ramp mechanism 40 is held by the spring 35 in the ramp valley and taken with the pulley 2. Through the pulley freewheel 8, the crankshaft 4 stops when the internal combustion engine is switched off. The pulley freewheel 8 and the operating freewheel 45 overtake.
  • a combustion starter III takes the starter generator through the closed dog clutch 10, the crankshaft 4 with.
  • On-the-fly rotational irregularities cause the ramp mechanism 40 to lead in blocks to the end of the ramp plateau.
  • the dog clutch 10 spurts out again, that is, the clutch partners are released from their engagement.
  • the biasing force of the spring 35 is chosen so large that occurring during operation Reibwertschwankept be compensated.
  • the internal combustion engine which is also referred to as a combustor, takes the pulley 2 and thus, via the pulley freewheel 8, the starter generator during acceleration. If the combustor retards, the pulley freewheel 8 makes it possible for the pulley 2 and the towed ramp mechanism 40 to be overtaken.
  • the belt pulley freewheel 8 dampens vibrations in the belt drive.

Abstract

L'invention concerne une poulie à courroie de vilebrequin pour la transmission d'un couple entre un vilebrequin et un entraînement à courroie, comprenant une roue libre de poulie à courroie. L'invention est caractérisée en ce que la roue libre de poulie à courroie dans la poulie à courroie de vilebrequin est combinée avec un accouplement pouvant être actionné par une roue libre d'actionnement, accouplement par lequel la roue libre de poulie à courroie peut être shuntée.
PCT/DE2011/000254 2010-04-06 2011-03-10 Poulie à courroie de vilebrequin WO2011124193A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112011101221T DE112011101221A5 (de) 2010-04-06 2011-03-10 Kurbelwellenriemenscheibe

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010013965.3 2010-04-06
DE102010013965 2010-04-06

Publications (1)

Publication Number Publication Date
WO2011124193A1 true WO2011124193A1 (fr) 2011-10-13

Family

ID=44533577

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2011/000254 WO2011124193A1 (fr) 2010-04-06 2011-03-10 Poulie à courroie de vilebrequin

Country Status (2)

Country Link
DE (2) DE102011013478A1 (fr)
WO (1) WO2011124193A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012204368A1 (de) * 2012-03-20 2013-09-26 Robert Bosch Gmbh Kraftmaschinenanordnung umfassend eine fluidbetätigte Kupplungsanordnung und einen Freilauf
DE102013221835A1 (de) 2012-11-22 2014-05-22 Schaeffler Technologies Gmbh & Co. Kg Drehmomentübertragungseinrichtung

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012216116B4 (de) 2011-10-06 2022-01-05 Schaeffler Technologies AG & Co. KG Riemenscheibenentkoppler
DE102013202079A1 (de) 2012-02-28 2013-08-29 Schaeffler Technologies AG & Co. KG Riemenscheibenanordnung

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1018733A (en) * 1963-12-31 1966-02-02 English Electric Aviat Ltd Improvements in and relating to one-way clutches
GB2033980A (en) * 1978-10-12 1980-05-29 Dana Corp Hub clutch
US4694943A (en) * 1986-01-21 1987-09-22 Boulder 12 Investments Ground clutch assembly with dynamic engagement and disengagement
DE19535889A1 (de) 1995-09-27 1997-04-03 Schaeffler Waelzlager Kg Freilaufkupplung für einen Lichtmaschinenantrieb
DE19636628C1 (de) 1996-09-10 1998-04-23 Freudenberg Carl Fa Freilauf
EP0782674B1 (fr) 1994-10-14 1999-04-28 Tesma International Inc Decoupleur de vilebrequin
EP0980479B1 (fr) 1997-05-07 2003-08-27 Litens Automotive Partnership Systeme d'entrainement en serpentin avec decoupleur d'alternateur a roue libre ameliore
DE102005029351A1 (de) 2004-07-02 2006-01-26 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Triebrad zum Antreiben eines Nebenaggregates eines Fahrzeuges
DE102004040810A1 (de) * 2004-08-24 2006-03-02 Ina-Schaeffler Kg Vorrichtung zur Dämpfung von Drehschwingungen

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1018733A (en) * 1963-12-31 1966-02-02 English Electric Aviat Ltd Improvements in and relating to one-way clutches
GB2033980A (en) * 1978-10-12 1980-05-29 Dana Corp Hub clutch
US4694943A (en) * 1986-01-21 1987-09-22 Boulder 12 Investments Ground clutch assembly with dynamic engagement and disengagement
EP0782674B1 (fr) 1994-10-14 1999-04-28 Tesma International Inc Decoupleur de vilebrequin
DE19535889A1 (de) 1995-09-27 1997-04-03 Schaeffler Waelzlager Kg Freilaufkupplung für einen Lichtmaschinenantrieb
DE19636628C1 (de) 1996-09-10 1998-04-23 Freudenberg Carl Fa Freilauf
EP0980479B1 (fr) 1997-05-07 2003-08-27 Litens Automotive Partnership Systeme d'entrainement en serpentin avec decoupleur d'alternateur a roue libre ameliore
DE102005029351A1 (de) 2004-07-02 2006-01-26 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Triebrad zum Antreiben eines Nebenaggregates eines Fahrzeuges
DE102004040810A1 (de) * 2004-08-24 2006-03-02 Ina-Schaeffler Kg Vorrichtung zur Dämpfung von Drehschwingungen

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012204368A1 (de) * 2012-03-20 2013-09-26 Robert Bosch Gmbh Kraftmaschinenanordnung umfassend eine fluidbetätigte Kupplungsanordnung und einen Freilauf
DE102012204368B4 (de) * 2012-03-20 2015-02-05 Robert Bosch Gmbh Kraftmaschinenanordnung umfassend eine fluidbetätigte Kupplungsanordnung und einen Freilauf
US9360061B2 (en) 2012-03-20 2016-06-07 Robert Bosch Gmbh Prime mover arrangement comprising a fluid-actuated clutch arrangement and a freewheel
DE102013221835A1 (de) 2012-11-22 2014-05-22 Schaeffler Technologies Gmbh & Co. Kg Drehmomentübertragungseinrichtung
DE102013221839A1 (de) 2012-11-22 2014-05-22 Schaeffler Technologies Gmbh & Co. Kg Drehmomentübertragungseinrichtung
WO2014079426A1 (fr) 2012-11-22 2014-05-30 Schaeffler Technologies AG & Co. KG Dispositif de transmission de couple
WO2014079427A1 (fr) 2012-11-22 2014-05-30 Schaeffler Technologies AG & Co. KG Dispositif de transmission de couple

Also Published As

Publication number Publication date
DE112011101221A5 (de) 2013-01-24
DE102011013478A1 (de) 2011-10-06

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