WO1995029347A1 - Tendeur de courroie a amortisseur a friction directionnel - Google Patents

Tendeur de courroie a amortisseur a friction directionnel Download PDF

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Publication number
WO1995029347A1
WO1995029347A1 PCT/EP1994/004157 EP9404157W WO9529347A1 WO 1995029347 A1 WO1995029347 A1 WO 1995029347A1 EP 9404157 W EP9404157 W EP 9404157W WO 9529347 A1 WO9529347 A1 WO 9529347A1
Authority
WO
WIPO (PCT)
Prior art keywords
tensioning roller
friction
roller carrier
clamping device
friction ring
Prior art date
Application number
PCT/EP1994/004157
Other languages
German (de)
English (en)
Inventor
Werner Petri
Original Assignee
Ina Wälzlager 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 Ina Wälzlager Schaeffler Kg filed Critical Ina Wälzlager Schaeffler Kg
Priority to DE4480870T priority Critical patent/DE4480870D2/de
Publication of WO1995029347A1 publication Critical patent/WO1995029347A1/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
    • 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
    • F16H2007/0802—Actuators for final output members
    • F16H2007/081—Torsion springs
    • 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
    • F16H2007/084—Means for varying tension of belts, ropes, or chains with vibration damping means having vibration damping characteristics dependent on the moving direction of the tensioner

Definitions

  • the invention relates to a tensioning device for a traction center drive according to the precharacterizing features of claim 1.
  • Such a tensioning device is known from DE-A 37 04 521.
  • the structure has a tension roller support, in the outer annular space of which a torsion spring is inserted.
  • a bearing is provided in a cup-shaped recess in the tensioning roller carrier and a friction element is used adjacent to it.
  • the friction element consists of an inner and an outer sleeve which are arranged concentrically to one another.
  • the inner sleeve is non-rotatably connected to the stationary housing and the outer sleeve lies against the inside of the cup-shaped recess of the swivel arm, which is divided into several sections.
  • the sleeves are connected to one another by inclined spoke webs, which rise when the tensioning roller carrier is displaced in one direction of rotation, as a result of which the pretensioning of the outer sleeve on the inner wall is increased. If the direction of rotation is reversed, the torque causes the spoke webs to tilt less, combined with a reduction in the frictional force.
  • This training leads to a direction-dependent damping.
  • This construction requires a fine-tuned design of the friction-member d ⁇ . ⁇ 't it neither at a fraction of the spoke webs and an associated loss of the tensioning device, is not yet a sten ⁇ the attenuation. In addition, it is often not sufficient for tensioning devices to dampen the pivoting movement of the tensioning roller carrier only in one direction of rotation.
  • the object of the invention is therefore to design a tensioning device of the type mentioned at the outset in such a way that the damping characteristic is optimized.
  • a compact, inexpensive construction of the tensioning device should also be made possible.
  • This object is achieved according to the invention in that a friction ring is used as the damping device, which has a plurality of friction surfaces which are separate from one another and which are arranged in different directions in different planes and the friction ring interacts with the stationary housing.
  • both a direction-independent, permanent damping and a directional damping of the adjusting movement of the tensioning roller carrier acting in one direction of rotation can be achieved with one component.
  • This construction advantageously enables a space-optimized clamping device, since a superimposed, double-acting damping can be achieved with one component.
  • the vibration behavior of problematic traction mechanism drives can be controlled, in which both periodically occurring vibrations and impulses caused by suddenly occurring torques as a result of connected consumers, such as, for. B. generator or compressor, the traction drive.
  • This damping characteristic has a positive effect on the service life of the drive belt or drive chain of the traction drive and reduces the noise excitation of the traction drive.
  • the friction ring according to the invention also allows the use of a weakly dimensioned torsion spring due to a superimposition of the damping forces achievable with the friction ring, which results in a further cost advantage in addition to the inexpensive manufacture of the friction ring.
  • a circular recess is made in the stationary housing, in which the friction ring is fitted.
  • the friction ring lies with an axial friction surface supported by a spring force on an intermediate wall and with the radial friction surface against an annular shoulder.
  • the friction ring is non-rotatably connected to the swivel roller carrier and has an axial friction surface on the end face, for example on a hub.
  • the friction ring Concentrically with the hub, the friction ring is provided with a sleeve whose lateral surface 'is staltet ge as radial friction surface.
  • the radial friction surface of the sleeve abutting against the annular shoulder is connected to the hub by elastic, obliquely arranged webs. Due to the inclined bars these are aligned with a swiveling movement against the direction of inclination of the webs. In this way, the prestressing of the sleeve on the annular shoulder is increased, combined with an increased damping force.
  • the friction ring is fixed in a rotationally fixed manner on the swivel roller carrier. For this purpose, the pins are guided through slots arranged in an arc in the intermediate wall.
  • the tensioning roller carrier is integrally connected to a piece of pipe, to whose free end the friction ring is attached.
  • the pipe section is guided through a central opening in the intermediate wall.
  • the friction ring is secured against rotation from the area of the pipe section protruding from the intermediate wall.
  • the design of the friction ring provides for axial displacement of both friction surfaces. This ensures that there is no frontal contact of the sleeve on the intermediate wall, whereby a clear separation of functions between the axial and radial friction can be achieved.
  • the radial friction surface ends at the end with the axial friction surface or forms a slight protruding axial offset from it, so that an axial friction acts on the end face of the outer sleeve.
  • the friction ring is made of an elastic material, which can be constructed in one piece or in several parts.
  • a plastic such as a polymer PA 66 GF, is preferred as the elastic material.
  • the friction ring can be designed as a composite part in which the area of the axial and radial friction surface is made of a material that differs from the carrier part of the friction ring.
  • the webs are between the sleeve and the hub at an angle of approximately 20 to 30 ° to the vertical axis of the clamping device or of approximately 60 to 70 ° in the direction a rotational direction increasing the tension force of the traction mechanism drive. This angle of inclination is variable if, for. B. the proportion of the damping force of the radial friction surface in the total damping force of the damping device is to be changed.
  • both the stationary housing and the tensioning roller carrier have hollow-cylindrical, inductively shaped sections which form pot-shaped recesses.
  • the hollow cylindrical sections can be joined coaxially into one another, the section of the tensioning roller carrier preferably being guided in the stationary housing.
  • thin-walled components can advantageously be created, which reduce the overall weight of the tensioning device, without adversely affecting the strength.
  • the torsion spring is inserted into the recess of the tensioning roller carrier, which is supported on the bottom of the tensioning roller carrier and the intermediate wall of the stationary housing and is anchored thereon.
  • the bearing is provided according to claim 12 between the outer surface of the tensioning roller carrier and the stationary housing.
  • the bearing is arranged on a large diameter, which results in improved torsional rigidity of the entire clamping device.
  • FIG. 1 shows a clamping device according to the invention in a longitudinal section
  • Figure 2 is a sectional view taken along the line A-A in Figure 1;
  • Figure 3 is a front view of a friction ring with a multiple division of the sleeve
  • FIG. 4 shows a sectional view of the friction ring along the line B-B in FIG. 3
  • FIG. 5 shows a largely identical to the tensioning device in FIG. 1, which has a different friction ring attachment.
  • the tensioning device 1 shown in FIG. 1 essentially comprises two components provided with cup-shaped recesses, a stationary housing 2 and a tensioning roller carrier 3, which are partially coaxially joined.
  • a cylindrical section 5 of the tensioning roller carrier 3 is inserted into the recess 4 of the stationary housing and a bearing 6, in particular a plain bearing bush, is inserted in an annular space between the two components.
  • the cup-shaped recess 7 in the swivel arm 3 serves to guide a torsion spring 8 which is supported on an intermediate wall 9 of the fixed housing and on a bottom 10 of the swivel arm 3.
  • the tensioning roller carrier 3 experiences a torque through the torsion spring 8 and causes a tensioning force via the tensioning roller 11 against a traction mechanism drive not shown in FIG.
  • the tensioning roller carrier 3 is provided with pins 12 which are guided through the intermediate wall 9 and to which a friction ring 13 is fastened, which forms a damping device 14 for the tensioning device 1.
  • the disk-like friction ring 13 is inserted into a circular recess 15 on the end face in the stationary housing 2 and has a radial friction surface 16 and an axial friction surface 17.
  • the radial friction surface 16 rests against a radial extension of the stationary housing 2, which is one Ring shoulder 18 forms, the ring shoulder 18 the friction ring 13 axially and radially covered. Due to the force of the torsion spring 8, the friction ring 13 rests on the intermediate wall 9 in a non-positive manner via the axial friction surface 17.
  • FIG. 2 represents a connecting element between the tensioning roller carrier 3 and the friction ring 13.
  • the pegs 12 are each guided in arcuate longitudinal slots 19, which allow the tensioning roller carrier 3 to be displaced to the stationary housing 2.
  • the friction ring 13 is shown as a single part in a front view (FIG. 3) and in a sectional view (FIG. 4).
  • the friction ring 13 is preferably made of an elastic material, in particular plastic, and comprises an inner sleeve, referred to as a hub 20 and an outer sleeve 21, which are connected to one another by webs 22.
  • the webs are each inclined at an angle ( ⁇ ) of approx. 60 to 70 ° against the swivel direction (see arrow) or at an angle of approx. 20 to 30 ° to the vertical axis and each extend over the width (b) of the friction ring 13.
  • FIG. 3 shows the circular, axial friction surface 17, via which the friction ring 13 lies against the intermediate wall 9 and which corresponds to the end face of the hub 20 and three fastening eyes 23 arranged symmetrically over the circumference of the hub , in which a pin 12 engages.
  • FIG. 4 illustrates, there is an axial offset (x) between the hub 20 and the sleeve 21, which ensures that an end-side contact of the sleeve 21 on the intermediate wall 9 is excluded and the sleeve 21 is therefore only on the inside radially the ring shoulder 18 rests.
  • the sleeve 21 has a plurality of divisions 24.
  • FIG. 5 shows a further exemplary embodiment of a tensioning device 1 according to the invention, in which the components corresponding to the first exemplary embodiment (FIG. 1) are provided with the same reference numbers, so that reference is made to the explanations relating to FIG. 1 with regard to their description can.
  • the friction ring 13a according to FIG. 5 secured against rotation on the tensioning roller carrier 3a via a pipe section 26.
  • the pipe section 26 is connected in one piece from the base 10 to the tensioning roller carrier 3a and projects through an opening 27 in the intermediate wall 9 into the friction ring 13a.
  • the tube piece 26 is flanged on the end face and provided with axial grooves to achieve an anti-twist device.
  • the friction element 13 has a double damping effect.
  • An axial frictional force is achieved by the friction surface 17, for which purpose the normal force is applied by the torsion spring 8.
  • a further frictional force in the radial direction causes the friction surface 16, the outer diameter (d) of the friction ring 13 being larger than the inner diameter (D) of the ring shoulder 18 in the non-installed state in order to achieve a preload in the radial direction.
  • a displacement of the tension roller support 3 and the associated friction ring 13 against the pivoting direction see arrow in FIG.

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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 tendeur pour l'entraînement d'un mécanisme de traction, comprenant une enveloppe fixe et un porte-galet tendeur susceptible de pivoter, formant ensemble un palier oscillant, le dispositif tendeur étant muni d'un dispositif amortisseur pour l'amortissement du mouvement oscillant en fonction de sa direction. Conformément à l'invention, on utilise comme dispositif amortisseur (14) une bague de friction (13) présentant une pluralité de surfaces de friction (16, 17) disposées dans différentes directions et sollicitées indépendamment les unes des autres, et qui coopèrent avec l'enveloppe fixe (2), en vue d'assurer l'amortissement directionnel du mouvement oscillant, indépendamment du sens de rotation.
PCT/EP1994/004157 1994-04-23 1994-12-15 Tendeur de courroie a amortisseur a friction directionnel WO1995029347A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE4480870T DE4480870D2 (de) 1994-04-23 1994-12-15 Riemenspanner mit gerichteter Reibungsdämpfung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4414213.7 1994-04-23
DE19944414213 DE4414213A1 (de) 1994-04-23 1994-04-23 Riemenspanner mit gerichteter Reibungsdämpfung

Publications (1)

Publication Number Publication Date
WO1995029347A1 true WO1995029347A1 (fr) 1995-11-02

Family

ID=6516250

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1994/004157 WO1995029347A1 (fr) 1994-04-23 1994-12-15 Tendeur de courroie a amortisseur a friction directionnel

Country Status (2)

Country Link
DE (2) DE4414213A1 (fr)
WO (1) WO1995029347A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2374394A (en) * 2001-04-13 2002-10-16 Unitta Co Ltd Thin autotensioner
GB2377981A (en) * 2001-07-27 2003-01-29 Unitta Co Ltd Pulley autotensioner having a friction member
US6767303B2 (en) 2001-07-27 2004-07-27 Unitta Company Autotensioner

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10021708A1 (de) * 2000-05-04 2001-11-08 Schaeffler Waelzlager Ohg Spannsystem mit einer gerichteten Dämpfung
DE10209723B4 (de) 2002-03-06 2005-01-27 Claas Selbstfahrende Erntemaschinen Gmbh Einrichtung zur Dämpfung von Schwingungen in Zugmittelantrieben
US7901309B2 (en) * 2004-09-01 2011-03-08 Litens Automotive Partnership Tensioner for a timing chain
DE102004053209A1 (de) 2004-11-04 2006-07-13 Schaeffler Kg Spannvorrichtung für einen Zugmitteltrieb mit richtungsabhängiger Dämpfung
DE102006004507A1 (de) * 2006-02-01 2007-08-02 Schaeffler Kg Spanneinrichtung für ein Zugmittel, insbesondere für einen Riemen oder eine Kette
DE102010019054A1 (de) * 2010-05-03 2011-11-03 Schaeffler Technologies Gmbh & Co. Kg Spannvorrichtung

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4698049A (en) * 1986-04-11 1987-10-06 Litens Automotive Inc. Belt tensioner with frustoconical pivot bearing
DE3704521A1 (de) * 1987-02-13 1988-08-25 Skf Gmbh Spannvorrichtung fuer treibriemen
FR2664953A1 (fr) * 1990-07-20 1992-01-24 Skf Gmbh Amortisseur a friction directionnel.

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3912944A1 (de) * 1989-03-15 1990-09-20 Muhr & Bender Riemenspannvorrichtung
DE9017863U1 (de) * 1990-04-04 1992-07-30 MAGNA INTERNATIONAL GmbH, 6460 Gelnhausen Automatischer Riemenspanner
DE4224759C2 (de) * 1992-07-27 2002-04-18 Ina Schaeffler Kg Spannsystem, reibungsgedämpft für Riemen- oder Kettentriebe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4698049A (en) * 1986-04-11 1987-10-06 Litens Automotive Inc. Belt tensioner with frustoconical pivot bearing
DE3704521A1 (de) * 1987-02-13 1988-08-25 Skf Gmbh Spannvorrichtung fuer treibriemen
FR2664953A1 (fr) * 1990-07-20 1992-01-24 Skf Gmbh Amortisseur a friction directionnel.

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2374394A (en) * 2001-04-13 2002-10-16 Unitta Co Ltd Thin autotensioner
GB2374394B (en) * 2001-04-13 2005-08-10 Unitta Co Ltd Autotensioner
US7384355B2 (en) 2001-04-13 2008-06-10 Unitta Company Thin autotensioner
US7588507B2 (en) 2001-04-13 2009-09-15 Unitta Company Thin autotensioner
GB2377981A (en) * 2001-07-27 2003-01-29 Unitta Co Ltd Pulley autotensioner having a friction member
US6767303B2 (en) 2001-07-27 2004-07-27 Unitta Company Autotensioner
GB2377981B (en) * 2001-07-27 2005-02-09 Unitta Co Ltd Autotensioner

Also Published As

Publication number Publication date
DE4414213A1 (de) 1995-10-26
DE4480870D2 (de) 1997-07-17

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