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WO2007009631A1 - Dispositif d'amortissement pour une transmission par element flexible - Google Patents

Dispositif d'amortissement pour une transmission par element flexible Download PDF

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Publication number
WO2007009631A1
WO2007009631A1 PCT/EP2006/006749 EP2006006749W WO2007009631A1 WO 2007009631 A1 WO2007009631 A1 WO 2007009631A1 EP 2006006749 W EP2006006749 W EP 2006006749W WO 2007009631 A1 WO2007009631 A1 WO 2007009631A1
Authority
WO
WIPO (PCT)
Prior art keywords
damping device
friction
clamping arm
machine part
piston
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/EP2006/006749
Other languages
German (de)
English (en)
Inventor
Bernd Hartmann
Roman Kern
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IHO Holding GmbH and Co KG
Original Assignee
Schaeffler 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 KG filed Critical Schaeffler KG
Priority to EP06776180A priority Critical patent/EP1910710B1/fr
Publication of WO2007009631A1 publication Critical patent/WO2007009631A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes or chains 
    • F16H7/0829—Means for varying tension of belts, ropes or chains  with vibration damping means
    • F16H7/0831—Means for varying tension of belts, ropes or chains  with vibration damping means of the dry friction type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes or chains 
    • F16H7/0829—Means for varying tension of belts, ropes or chains  with vibration damping means
    • F16H7/0838—Means for varying tension of belts, ropes or chains  with vibration damping means of the dissipating material type, e.g. elastomeric spring
    • 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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes or chains 
    • F16H7/10—Means for varying tension of belts, ropes or chains  by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes or chains  by adjusting the axis of a pulley of an idle pulley
    • F16H7/1209—Means for varying tension of belts, ropes or chains  by adjusting the axis of a pulley of an idle pulley with vibration damping means
    • F16H7/1218—Means for varying tension of belts, ropes or chains  by adjusting the axis of a pulley of an idle pulley with vibration damping means of the dry friction type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes or chains 
    • F16H7/10—Means for varying tension of belts, ropes or chains  by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes or chains  by adjusting the axis of a pulley of an idle pulley
    • F16H7/1209—Means for varying tension of belts, ropes or chains  by adjusting the axis of a pulley of an idle pulley with vibration damping means
    • F16H7/1245—Means for varying tension of belts, ropes or chains  by adjusting the axis of a pulley of an idle pulley with vibration damping means of the dissipating material type, e.g. elastomeric spring

Definitions

  • the invention relates to a damping device for a traction mechanism, in which a pivotable about a rotational axis clamping arm for generating and maintaining a bias of a traction device via a tensioning roller on the traction means by means of mechanical damping means is supported damping.
  • Such damping devices known for example from DE 100 21 708 A1, EP 0779 452 A2 and DE 695 11 656 T2, have at least one plain bearing designed as a friction element, which is arranged coaxially on the axis of rotation and in operative connection with at least one likewise coaxially arranged spring is.
  • This spring exerts a force component acting in the circumferential direction of the traction mechanism drive, which supports the tensioning arm resiliently, in conjunction with a tensioning roller rotatably mounted at the free end of the tensioning arm, on the traction means.
  • the spring is advantageous, as described for example in DE 101 52 364 A1, designed for space optimization as a conically wound helical torsion spring.
  • the friction element is preferably designed as a conical friction bush which, in the case of shock movements or oscillations caused by pivoting movements of the tensioning arm, has a dampening effect.
  • the pivot bearing is fixed to a stationary machine part, for example, to a crankcase of an internal combustion engine in a motor vehicle, and the associated traction drive serves, for example, to drive one or more auxiliary units (generator, water pump, fan, etc.) of the motor vehicle.
  • auxiliary units generator, water pump, fan, etc.
  • Such tensioning and damping systems also known as cone clamps, have already proven themselves in practice.
  • the disadvantage of this, however, is that the damping units are coupled both functionally and geometrically to the pivot bearing of the pivoting arm. As a result, the design options in the design of the clamping system are relatively limited.
  • the clamping arm requires, in order to ensure a long service life, a relatively high construction and cost.
  • the cross section of the tensioning arm is essentially determined by the length of the damping system and, despite conical spring or friction elements, requires a relatively large structural depth.
  • the invention has for its object to provide a damping device on a clamping arm of a traction mechanism, which can be produced with lower cost and design effort, which is effective and low-wear during operation, and with a small space, especially with a reduced overall depth of Clamping arm is feasible.
  • the invention is based on the finding that, by utilizing a support on a machine part, with a damping unit independently constructed from the rotation axis of the tensioning arm, which can be positioned at an arbitrarily predefinable point of the tensioning arm, a cost-effective and space-saving possibility for realizing a very efficient mechanical damping in traction drives can be created.
  • the invention is therefore according to the features of claim 1 from a damping device for a traction mechanism drive, in which a pivotable about a rotational axis clamping arm for generating and maintaining a bias voltage traction means via a tensioning roller on the traction means by means of mechanical damping means is supported damping.
  • a friction damper spaced transversely to the rotation axis is integrated into the tensioning arm, with a piston projecting laterally from the tensioning arm, the end of which is supported on the front side by a stationary machine part, with means for compensating for an offset resulting from pivoting movements of the tensioning arm the machine part and the clamping arm, and with a arranged in a receiving space within the clamping arm friction body can be attenuated on the pivoting movements of the clamping arm by an associated sliding friction between the friction body and a friction surface.
  • This construction advantageously ensures that the clamping arm is supported and damped directly on a stationary component, for example on an internal combustion engine.
  • the support is via a piston, wherein the contact geometry is selected so that the force is always perpendicular to the Kolbenstimisation.
  • compensation means are provided which compensate for the resulting offset between the piston and clamping arm in its caused by shocks and / or vibrations pivoting movements.
  • the pivot bearing is relieved during pivotal movements of the arm.
  • the pivot bearing can be designed structurally simple.
  • the friction damper is installed transversely to the axis of rotation in the lever arm. This allows a very small overall depth of the lever arm, which is particularly important in the automotive sector, with a relatively small available space in the engine compartment, of increasing importance.
  • the friction body is designed as a truncated cone aligned with its base surface in the direction of the machine part. is formed, which is held in an accommodated in the receiving space and designed as a sliding annular cone seat, which is held by means of a spring element formschlüsssig against the truncated cone, wherein a contact surface between the truncated cone and the conical seat forms the friction surface.
  • the offset compensation means are formed as a rounding at the end face of the piston adjacent to the machine part and as a contact surface formed as a counter surface to the rounding on the machine part, in which the piston rolls during a pivoting movement of the clamping arm.
  • the friction damper generates friction by sliding movements in the sliding body during pivoting movements of the tensioning arm and thus dampens the traction mechanism.
  • the spring ensures that the sliding body and the friction body always abut against each other at their contact surface.
  • the damping device comprises a movably held in the receiving space cylinder, which has on its side facing away from the machine part end a rounding, which abuts a formed as a counter surface to the rounded bottom surface of the receiving space, wherein a contact surface between the rounding and the bottom surface is usable as a friction surface.
  • a contact surface between the rounding and the bottom surface is usable as a friction surface.
  • the offset compensation means are formed as a frictional connection between the piston and the machine part and as a arranged on the damping device holder, wherein the holder is arranged with a lateral play in the receiving space damping device against falling out of the clamping arm secures and allows a compensation movement of the damping device to a pivoting movement of the clamping arm within the receiving space.
  • the holder may advantageously be formed by an O-ring. This arrangement is structurally particularly simple and cost-effective.
  • a spring element which is supported between the tensioning arm and the machine part and which is effective as a tensioning device producing or reinforcing the tensioning means.
  • the piston support on the machine part of the mounted on its axis of rotation clamping arm can be preset with a certain biasing force on the traction means.
  • the friction surface can also be designed so that when pivoting movements of the clamping arm initially a static friction is overcome, which then passes into a sliding friction, whereby the bias voltage is supported.
  • the additional spring is another way to support the bias, making the bias more efficient. In principle, it is also possible that the additional spring generates the entire necessary bias.
  • the damping device according to the invention tion can thus act as a very effective combined tension and damping system for the traction drive.
  • the receiving space is formed as a housing, which forms with the friction damper received therein a pre-assembled component which can be inserted into a correspondingly formed recess of the clamping arm.
  • the housing forms with the friction damper a complete damping unit that can be easily inserted and anchored in a prepared recess of the clamping arm.
  • FIG. 1 shows a clamping arm of a traction mechanism drive in an exploded view with a first embodiment of a damping device according to the invention in section B-B of Fig. 2,
  • Fig. 3 shows a second embodiment of the damping device in one
  • Fig. 5 is an Arre as a piston support in a side view in section
  • the damping device shown in Fig. 1 comprises a friction damper 1, which is integrated in a clamping arm (lever arm) 2.
  • the clamping arm 2 has a widened profile 28 in the region of the friction damper 1.
  • the clamping arm 2 is rotatably mounted about a pivot point, or an axis of rotation 3 and forms a clamping device for a traction means in a traction drive, in which the clamping arm 2 is supported on the traction means via a (not shown) tension roller.
  • the traction mechanism drive can be arranged, for example, for driving one or more ancillary units on an engine of a motor vehicle.
  • the structure of such traction mechanisms and their operation are known in principle. Therefore, only the damping device according to the invention will be described in detail below.
  • the friction damper 1 is inserted transversely to the axis of rotation 3 in a conical receiving space 7. It has a conical friction body 8, which sits in a sliding body 10 designed as a conical seat.
  • the sliding body 10 is advantageously provided with walls designed as friction surfaces (inner wall 33, outer wall 34).
  • the outer wall 32 of the friction body 8 may be specially processed as a friction surface.
  • the conical wall 35 of the receiving space 7 and the conical outer wall 34 of the slider 10 are geometrically coordinated so that the slider 10 is held in the vicinity of the lateral outer wall 20 of the lever arm 2 and spaced from a bottom surface 22 of the receiving space 7 movable and positive.
  • a spring element 11 is supported between a bottom 12 of the slider 10 and the bottom 22 of the receiving space 7.
  • the spring 11 is advantageously designed as a conically wound helical compression spring which presses the conical seat or sliding body 10 against the friction body 8.
  • the friction body 8 is in turn based on a beneficial with him integrally connected, laterally projecting piston 4 on a machine part 6, for example, a combustion engine housing and presses the slider 10 against the wall of the receiving space. 7
  • the piston 4 is formed as a cylindrical projection on the friction body 8, whose end face 5 is rounded hemispherical.
  • a counter surface 13 is formed, against which the rounded piston face 5 runs and compensated by rolling movements the resulting offset in the pivotal movement of the clamping arm 2.
  • Fig. 3 shows a damping device 8 'with a cylindrical friction damper 1'.
  • the damping device 8 ' is integrally connected to a cylindrical piston 4', which protrudes laterally from the clamping arm 2.
  • the damping device 8 ' is also via a holder 15, advantageously designed as an O-ring 15, mounted with a lateral clearance 16 in a receiving space T within the clamping arm 2.
  • the O-ring 15 secures the friction damper 1 'and the damping device 8' from falling out and allows lateral pivoting movements within the receiving space 7 '.
  • the piston 4 ' has on the machine side a straight end face 5', which is connected via a frictional connection 14 with the machine part 6.
  • a rounding 21 is provided, which is adjacent to a bottom 22 'of the receiving space 7'.
  • the bottom 22 ' is rounded off corresponding to the rounding 21, so that a contact surface 9' results as a friction surface.
  • the friction damper 1 During operation, the friction damper 1 'deviates laterally from pivoting movements of the tensioning arm 2, wherein the friction body 8' slides over the friction surface 9 'and thereby dampens the pivoting movements.
  • friction damping means according to FIG. 1 can be arranged inside the damping device 8 '.
  • FIGS 4a and 4b show a roller bearing 17, over which the compensation movements between the friction damper 1 and the machine part 6 can be compensated.
  • the roller bearing 17 has a roller 27, which is fixed to a pivot bearing 26 of a connecting piece 30 to the piston 4 and the friction damper 1.
  • the roller 27 is supported on the machine part 6 from.
  • FIG. 5 shows a further possibility of a movement between the piston 4 and to allow the piston support on the machine part 6.
  • an arm 18 is provided with a roller 23 which is mounted in a semicircular recess 25 of a connecting piece 30 'to the piston 4 with a ball bearing 24.
  • FIG. 6 shows a damping device in which a pretensioning spring 19 is provided.
  • the spring 19 is advantageously designed as a cylindrical helical compression spring. It comprises the piston 4 with the rounded end face 5 coaxial and is supported between the outer wall 20 of the clamping arm 2 and a border 31 of the mating surface 13 on the machine part 6 from.
  • the spring 19 is tilted and compressed or stretched. The spring force counteracts this movement, whereby a clamping force on the tensioning arm 2 is transmitted to the traction means.
  • the spring 19 may be clamped with a bias between the arm 2 and the machine part 6, so that it causes a permanent preload of the traction means on the axis of rotation 3 of the clamping arm 2, which in a corresponding design, the entire necessary bias to ensure a frictional engagement between the traction means and a pulley (not shown) on which the traction means runs, so that the damping device simultaneously acts as a traction means biasing unit and as a damping unit.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

L'invention concerne un dispositif d'amortissement pour une transmission par élément flexible, dispositif dans lequel un bras tendeur, pouvant pivoter autour d'un axe de rotation et destiné à produire et à maintenir une précontrainte sur un élément flexible, s'appuie sur cet élément flexible par l'intermédiaire d'un galet tendeur en exerçant un effet amortisseur au moyen d'éléments d'amortissement mécaniques. L'objectif de cette invention est de réaliser un dispositif d'amortissement au niveau d'un bras tendeur d'une transmission par élément flexible. A cet effet, un amortisseur à friction (1, 1') est intégré dans le bras tendeur (2) et placé à une certaine distance de l'axe de rotation (3) perpendiculairement à ce dernier. Cet amortisseur comporte un piston (4, 4'), saillant d'un côté du bras tendeur (2) et dont l'extrémité (5, 5') s'appuie côté face sur une pièce de machine stationnaire (6), des moyens destinés à compenser un décalage entre la pièce de machine (6) et le bras tendeur (2), qui apparaît sous l'effet de mouvements de pivotement du bras tendeur (2), ainsi qu'un corps de friction (8, 8'), placé dans un espace de logement (7, 7') à l'intérieur du bras tendeur (2) et par l'intermédiaire duquel des mouvements de pivotement du bras tendeur (2) peuvent être amortis sous l'effet d'une friction de glissement associée entre le corps de friction (8, 8') et une surface de friction (9, 9').
PCT/EP2006/006749 2005-07-22 2006-07-11 Dispositif d'amortissement pour une transmission par element flexible Ceased WO2007009631A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06776180A EP1910710B1 (fr) 2005-07-22 2006-07-11 Dispositif d'amortissement pour une transmission par element flexible

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005034332.8 2005-07-22
DE200510034322 DE102005034322A1 (de) 2005-07-22 2005-07-22 Dämpfungsvorrichtung für einen Zugmitteltrieb

Publications (1)

Publication Number Publication Date
WO2007009631A1 true WO2007009631A1 (fr) 2007-01-25

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Application Number Title Priority Date Filing Date
PCT/EP2006/006749 Ceased WO2007009631A1 (fr) 2005-07-22 2006-07-11 Dispositif d'amortissement pour une transmission par element flexible

Country Status (2)

Country Link
DE (1) DE102005034322A1 (fr)
WO (1) WO2007009631A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11486473B2 (en) 2018-01-31 2022-11-01 Borgwarner Inc. Variable force tensioner arm with cap disk spring

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4822008A (en) * 1986-12-10 1989-04-18 Sfk Gmbh Vibration-damped spring
DE9006213U1 (de) * 1990-06-01 1990-08-02 SKF GmbH, 8720 Schweinfurt Teleskopförmiger Reibungsdämpfer
EP0779452A2 (fr) 1995-12-12 1997-06-18 Firma Muhr und Bender Dispositif de tension de courroie
DE69511656T2 (de) 1994-10-28 2000-01-13 Dayco Europe S.R.L., Colonnella Treibriemenspanner
DE10021708A1 (de) 2000-05-04 2001-11-08 Schaeffler Waelzlager Ohg Spannsystem mit einer gerichteten Dämpfung
DE10152364A1 (de) 2001-10-24 2003-05-08 Ina Schaeffler Kg Spannvorrichtung
WO2003089809A1 (fr) * 2002-04-15 2003-10-30 The Gates Corporation Tendeur
WO2005059402A1 (fr) * 2003-12-16 2005-06-30 Schaeffler Kg Dispositif de tension de courroies ou de chaines de moteurs a combustion interne
DE10360288A1 (de) * 2003-12-20 2005-07-21 Ina-Schaeffler Kg Mechanische Spannvorrichtung für Zugmittel mit gerichteter Reibdämpfung

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4241614A (en) * 1979-06-04 1980-12-30 Chouinard Raymond J Power take-off

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4822008A (en) * 1986-12-10 1989-04-18 Sfk Gmbh Vibration-damped spring
DE9006213U1 (de) * 1990-06-01 1990-08-02 SKF GmbH, 8720 Schweinfurt Teleskopförmiger Reibungsdämpfer
DE69511656T2 (de) 1994-10-28 2000-01-13 Dayco Europe S.R.L., Colonnella Treibriemenspanner
EP0779452A2 (fr) 1995-12-12 1997-06-18 Firma Muhr und Bender Dispositif de tension de courroie
DE10021708A1 (de) 2000-05-04 2001-11-08 Schaeffler Waelzlager Ohg Spannsystem mit einer gerichteten Dämpfung
DE10152364A1 (de) 2001-10-24 2003-05-08 Ina Schaeffler Kg Spannvorrichtung
WO2003089809A1 (fr) * 2002-04-15 2003-10-30 The Gates Corporation Tendeur
WO2005059402A1 (fr) * 2003-12-16 2005-06-30 Schaeffler Kg Dispositif de tension de courroies ou de chaines de moteurs a combustion interne
DE10360288A1 (de) * 2003-12-20 2005-07-21 Ina-Schaeffler Kg Mechanische Spannvorrichtung für Zugmittel mit gerichteter Reibdämpfung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11486473B2 (en) 2018-01-31 2022-11-01 Borgwarner Inc. Variable force tensioner arm with cap disk spring

Also Published As

Publication number Publication date
DE102005034322A1 (de) 2007-01-25

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