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WO2001084014A1 - Systeme de tension a amortissement dirige - Google Patents

Systeme de tension a amortissement dirige Download PDF

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Publication number
WO2001084014A1
WO2001084014A1 PCT/EP2001/004252 EP0104252W WO0184014A1 WO 2001084014 A1 WO2001084014 A1 WO 2001084014A1 EP 0104252 W EP0104252 W EP 0104252W WO 0184014 A1 WO0184014 A1 WO 0184014A1
Authority
WO
WIPO (PCT)
Prior art keywords
friction element
tensioning
traction device
arm
damping
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/EP2001/004252
Other languages
German (de)
English (en)
Inventor
Michael Bogner
Hermann Stief
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
INA Waelzlager Schaeffler OHG
Original Assignee
INA Schaeffler KG
INA Waelzlager Schaeffler OHG
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 Schaeffler KG, INA Waelzlager Schaeffler OHG filed Critical INA Schaeffler KG
Priority to AU60207/01A priority Critical patent/AU6020701A/en
Publication of WO2001084014A1 publication Critical patent/WO2001084014A1/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 
    • F16H7/10—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 present invention relates to a tensioning system with which a continuous pre-tensioning of the traction device, such as a belt or a chain, of a traction device drive can be maintained.
  • the clamping system is provided with a stationary housing, to which a clamping arm is assigned, which is pivotably arranged via a pivot bearing.
  • a spring element is arranged between the housing and the tensioning arm, with which a resilient support of the tensioning roller on the traction means can be ensured.
  • the tensioning system is provided with at least one damping device which is dependent on the direction of rotation.
  • Such a damping device enables damping of oscillating adjusting movements of the tensioning arm, which is limited to an adjusting movement of the tensioning arm, which runs counter to a tensioning arm movement which increases the pretensioning force of the traction means.
  • a traction mechanism drive with which auxiliary units such as the water pump, the generator, the fan for recooling the coolant and the compressor for the air conditioning system are driven.
  • Units of this type are usually driven by means of a traction mechanism drive, which comprises an endless belt, for which purpose the traction means are guided on the individual pulleys of the aggregates and on a pulley arranged at the end of the crankshaft from the internal combustion engine, via which the drive takes place.
  • a defined traction device Tension required.
  • the lifespan of the traction device is influenced by the damping of the tensioning system. Due to the degree of non-uniformity of the internal combustion engine and a non-continuous power consumption of the units - for example, the compressor of an air conditioning system is frequently switched on and off during vehicle operation - there is an abrupt, impulsive load on the traction mechanism drive. Such undamped loads reduce the lifespan of the traction mechanism.
  • DE 196 47 224 A1 shows a tensioning system for a belt tensioning device that can be used, for example, for the traction mechanism drive of an internal combustion engine.
  • This device comprises a damping device with a direction of rotation-dependent friction effect and thus an asymmetrical damping hysteresis.
  • the known device comprises two jaw-shaped friction lining carriers, each rotatable about a pivot pin, which are enclosed by a rotatable drum.
  • a mechanical, spring-elastic expansion element is provided in order to achieve a frictional engagement of the friction lining carrier on the cylindrical inner wall of the drum.
  • the damping which is dependent on the direction of rotation, is achieved in that both friction lining carriers are arranged running in the opposite direction to the rotation of the drum in one direction of rotation in the opposite direction of rotation.
  • the known device requires a large amount of space to accommodate the separate friction lining carrier.
  • the facility which comprises several individual parts, also requires cost-intensive assembly, which overall prevents acceptance for series production in large quantities.
  • the aforementioned problem is solved according to the invention by a friction element which is inserted in a receptacle designed as an annular gap.
  • the annular gap as an installation space for the damping device according to the invention is radially delimited on the inside radially by the bearing journal of the pivot bearing, via which the tensioning arm is pivotably mounted.
  • the annular gap is limited by the inner wall of a cylindrical receptacle of the tension arm or the housing.
  • the friction element according to the invention is non-positively supported on a component which radially delimits the annular gap.
  • the friction element is rotationally fixed to the associated further component which radially delimits the annular gap. This arrangement of the friction element enables the desired different damping force, depending on the direction of rotation, i.e. from the pivoting movement of the tension arm.
  • the attachment of the friction element is possible according to the invention on both components that radially limit the annular gap and thus the installation space of the friction element.
  • this design allows an increase in damping force for a pivoting movement of the tensioning arm both clockwise and counterclockwise.
  • the different fastening of the friction element enables a running arrangement of the friction lining clockwise or counterclockwise or a running arrangement of the friction lining in both directions of rotation. This results in a maximum of design options and operating principles for the damping device according to the invention.
  • the one-piece construction of the friction element according to the invention simplifies assembly, which can advantageously be automated at low cost.
  • the geometric design of the friction element as an annular component requires a reduced compared to the known prior art Space.
  • the damping device dependent on the direction of rotation enables a significant cost advantage over previously known damping devices.
  • the friction element which is fully cylindrical except for a gap dimension, is non-positively supported on a component which radially delimits the annular gap. If necessary, this configuration enables a simplified influence on the damping force, which can be defined as a function of the wrap angle and the pretensioning force.
  • the damping force is proportional to the position of the tension arm, and the damping force of static friction can increase until the friction element is displaced relative to the component on which it is in frictional engagement.
  • the damping device according to the invention which is dependent on the direction of rotation, consequently includes solid-state damping with subsequent sliding friction, as well as damping which is produced by a relative movement of two components.
  • the frictional torque of the friction element according to the invention can be influenced according to the conditions of use by varying the pretensioning force, which is dependent, for example, on the wall thickness and / or the wrap angle of the friction element.
  • the mode of action of the damping device arises from a relative movement between the friction element and a countercurrent partner.
  • Both the journal and the tension arm can serve as counter-rotating partners.
  • the friction element with a corresponding oversize, to achieve a preload is pushed onto the bearing journal in order to achieve initial damping.
  • the bearing journal is preferably arranged in a rotationally rigid manner and the friction element is positively attached to the tension arm. In this installation position, at least the end region of the friction element follows the movement of the tension arm.
  • the invention also includes a pivot pin arranged on the tensioning arm and on which the friction element is attached.
  • the damping device which is dependent on the direction of rotation, enables a defined friction on account of the non-positive contact with a component which radially limits the annular gap.
  • the friction in turn exerts a moment which acts on the friction element, with the result that the wall thickness of the friction element changes.
  • the friction element tries to constrict the bolt or the bearing journal. Since the bearing journal is rigid and inelastic, a counterforce is created that triggers an increased surface pressure.
  • the frictional torque thus has a direct influence on the resulting surface pressure of the friction element.
  • the generated friction torque changes depending on the direction of rotation, with the effect of directional damping.
  • the invention is for a clamping system with a rotationally fixed to the housing Bearing pin and a clamping arm, which is rotatably mounted on the bearing pin via a hub.
  • the invention further includes a clamping system in which the clamping arm is rotatably inserted in the housing via the bearing pin.
  • the invention also includes a friction element nt, which is non-positively supported on the inner wall of the tension arm holder.
  • a friction element arranged in this way is also provided with a parting line designed as a longitudinal slot.
  • the invention further includes a friction element enclosing the bearing journal in a non-positive manner and having a parting line, which friction element is provided with two mutually spaced end portions is attached to the tension arm.
  • the pretensioning force of the friction element is different, at least in the zones adjacent to the end sections, preferably due to a wall thickness of the friction element that differs from one another.
  • Directional damping also occurs due to a different angle of attack of the end sections, whereby a leverage effect can be achieved. For example, with the effect of pressing one end section onto the bearing journal and loosening the other end section.
  • the invention includes a relative movement between the friction element and the housing or the tensioning arm, the friction element being inserted into the receiving means of the tensioning arm with a corresponding oversize and thus ensuring sufficient initial damping.
  • the friction element is fastened in a form-fitting manner on the torsionally rigidly arranged bearing journal.
  • the tension arm enables a relative movement to the friction element.
  • the invention comprises a bearing journal which is integrally connected to the rotatably arranged tension arm and to which the friction element is fastened.
  • the friction element follows the movement of the bearing pin, this movement taking place relative to the movement of the stationary housing.
  • the friction element inserted in the annular gap delimited radially by the bearing journal and the tensioning arm is fastened to the component on which the friction element does not bear non-positively or does not enclose it non-positively.
  • this is preferably angled pointing radially outward, this end section engaging in a form-fitting manner in a recess in the bearing pin or the tensioning arm.
  • the parting line or longitudinal slot is provided between the end section and the free end of the friction element.
  • This design enables an almost closed cylindrical shape of the friction element, which has a positive effect on the damping characteristics.
  • This placement of the parting line ensures a large wrap angle of the friction element, which results in progressive damping when the actuating movement runs up.
  • Another friction element according to the invention which almost completely surrounds the bearing journal, is held in a form-fitting manner by means of the radially outwardly directed end sections in recesses of the tensioning arm which are arranged offset from one another.
  • a superimposed effect can be achieved, i.e. Friction moments in both directions of rotation that differ from each other.
  • the frictional moments can be influenced by factors such as the geometry, the shape and the component stiffness of the friction elements, and by different deflections of the end sections, with which the leverage in end zones of the end sections can be changed. This leverage can be interpreted differently according to the invention for the education of a direction-dependent damping.
  • the invention further includes, for a friction element fastened to an end section, a wall thickness that is variable over the circumference.
  • a friction element fastened to an end section a wall thickness that is variable over the circumference.
  • the wall thickness is preferably increased in order to achieve an almost constant prestressing force over the circumference of the friction element, combined with a defined friction torque.
  • the invention includes a friction element in which the wall thickness tapers toward the free end portion.
  • a friction element made of plastic interacts with a component made of metal, which radially delimits the installation space of the friction element.
  • a friction element made of a wear-resistant plastic enables next to one inexpensive manufacture, easy handling and assembly of the friction element. Through a suitable choice of material for the friction element, wear optimization can furthermore be achieved in order to achieve an improved service life of the clamping system.
  • the friction partners made of plastic and metal result in a damping device which advantageously does not cause any noise.
  • the invention further provides for combining the friction element with a spring bushing.
  • a slotted spring bushing made of spring steel is preferably suitable for this purpose, which, depending on the installation position of the friction element, surrounds it concentrically or bears on the inside in a force-fitting manner.
  • the invention includes a friction element made of plastic, in that a reinforcing ring, for example to reinforce and / or to achieve a greater pretensioning force, e.g. made of spring steel, or this is encapsulated by plastic.
  • the direction-dependent damping according to the invention can further be combined with a direction-independent damping. It is advisable to provide the clamping system with separate damping devices, each with a separate friction element. Such a clamping system offers the advantage of reducing the number of variants, depending on requirements, i. H. to be equipped with one or two damping devices depending on the respective engine or vibration characteristics of the internal combustion engine.
  • the configuration of the tensioning system according to the invention with two damping devices provides that the damping device, which is independent of the direction of rotation, is designed as a friction disk for receiving an axial force applied by the spring means.
  • the friction disk which is made in particular from a wear-resistant plastic, is supported, for example, on one side on a collar or a rim of the bearing journal and on the other side on a shoulder or a recess in the housing.
  • the damping device, which is independent of the direction of rotation is combined with a further, tion-dependent damping device according to a previously described type.
  • the invention further comprises a damping device which embodies both a direction-dependent and a direction-independent damping device in one structural unit.
  • a damping device which embodies both a direction-dependent and a direction-independent damping device in one structural unit.
  • This concept enables further component reduction and simplifies assembly work.
  • Such a combined damping device can be realized, for example, with an annular friction element which is inserted into a corresponding installation space of the tension arm and is supported in a radially prestressed manner on an inner wall of the tension arm and is rotationally fixed to the bearing journal.
  • the construction of the friction element which is also provided with a parting line, is therefore comparable to the previously described friction elements of the invention, which are provided exclusively for damping which is dependent on the direction of rotation.
  • an end-face contact surface of such a friction element is supported on the housing in order to achieve damping that is independent of the direction of rotation, or on a disk that is non-rotatably connected to the bearing journal.
  • a further design of the tensioning system according to the invention provides that it exclusively has a damping device that is dependent on the direction of rotation.
  • an axial bearing is provided in a support area between the rotatable clamping arm and the rotationally fixed housing.
  • a rolling bearing or a friction-reducing coating between the friction partners is suitable.
  • FIG. 1 shows a clamping system in a longitudinal section, provided with a damping device that is dependent on the direction of rotation.
  • tion device which is non-positively supported on a rotatable bearing journal;
  • FIG. 2 shows an alternative damping device that is dependent on the direction of rotation, the friction element of which rests non-positively on an inner wall of the tensioning arm and is positioned on the inside on the rotationally fixed bearing journal;
  • FIG 3 shows a clamping system provided with a combined direction of rotation dependent and direction of rotation independent
  • FIG. 4 shows a tensioning system in which a damping device is integrated, which only ensures damping dependent on the direction of rotation;
  • Figure 5 shows the sectional view 5-5, according to Figure 1, from which the installation position of the friction element according to the invention supported on the journal is clear;
  • FIG. 6 shows a representation largely corresponding to FIG. 4 with a friction element which is non-positively supported on an inner wall of the tensioning arm;
  • Figure 7 shows the arrangement of a friction element, which with. both
  • End sections is positively attached to the clamping lever.
  • the clamping system described below is of a known type, which is why the description is limited to the components essential to the invention.
  • the clamping system 1 shown in FIG. 1 is provided with a stationary housing 2, for example directly attached to the internal combustion engine, on the bearing journal 3 of which a clamping arm 4 can be pivoted is arranged.
  • a hub 5 of the clamping arm 4 is provided with a receptacle in which the bearing journal 3 engages.
  • a slide bearing 7 is used in an annular installation space, which is radially delimited radially by the inner wall 6 of the hub 5 and a lateral surface of the bearing journal 3, in order to achieve a low-friction pivoting movement of the hub 5 and thus of the pivot arm 4.
  • the clamping arm 4 which is oriented at right angles to a longitudinal axis 8 of the housing 2 and on which a rotatable tensioning roller 9 is arranged at the end.
  • a spring-loaded contact of the tensioning roller 9 on a traction means 10 takes place by means of a torsion spring 11.
  • the torsion spring 11 is arranged between the housing 2 and the tensioning arm 4, the spring ends of the torsion spring being rotationally fixed in each case. Due to a pretensioned installation position of the torsion spring 11, an always supported contact of the tensioning roller 9 with the traction means 10 is ensured.
  • the torsion spring 11 In addition to a torsional force or a torque component, the torsion spring 11 also exerts an expanding force acting in the axial direction, which acts on the tension arm 4 or the hub 5 in the direction of a friction disk 13 inserted between the housing 2 and the tension arm 4.
  • the friction disc 13 forms the damping device 34 and enables damping of the adjusting movements of the tensioning arm 4 which is independent of the direction of rotation and which is triggered by the traction means 10 due to changing power consumption of units which are connected to the traction means 10.
  • the tensioning system 1 is also provided with a damping device 14, in order to achieve a direction-dependent damping of adjusting movements of the tensioning arm 4.
  • the hub 5 has a receptacle 16 on the tensioning roller side, i. H. a radially stepped portion of the central bore.
  • the receptacle 16 forms an annular gap 17 for receiving a friction element 15a.
  • the annular gap 17 is radially delimited by an inner wall 18 of the hub 5 and an outer surface of the bearing pin 3.
  • FIG. 2 In further exemplary embodiments (FIG. 2, FIG. 3, FIG. 4) of a tensioning system 1 according to the invention, those with the first exemplary embodiment are matching components provided with the same reference numerals, so that reference can be made to the description of the embodiment of the first embodiment ( Figure 1).
  • FIG. 2 shows the clamping system 1, whose damping device 14 is dependent on the direction of rotation and is provided with the friction element 15b.
  • the annularly shaped friction element 15b which is provided with a parting line in the form of a longitudinal slot 19, lies non-positively on the inner wall 18 of the hub 5 of the clamping arm 4.
  • the friction element 15b is rotationally fixed to the bearing journal 3.
  • the further damping device 34 which is independent of the direction of rotation, represented by the friction disk 13 is inserted in an end recess of the tensioning arm 4 and is supported on one another on a shoulder of the housing 2.
  • the torsion spring 11 is inserted between the tension arm 4 and a support disk 12 which is connected to the bearing journal 3 in a rotationally fixed manner.
  • FIG. 3 shows the damping device 35 used in the tensioning system 1.
  • the damping device 35 according to FIG. 3 contains a device which enables both direction-dependent damping and direction-independent damping .
  • the friction element 33 is non-positively supported on the inner wall 18 of the hub 5 of the tensioning arm 4 and is fixed in position on the inside via an end section on the bearing journal 3 and thus ensures damping which is dependent on the direction of rotation.
  • the housing 2 is supported axially on an end face 32 of the friction element 33 via a shoulder 31.
  • the friction partners, the shoulder 31 and the end face 32 of the friction element 33 cause a damping device that is independent of the direction of rotation.
  • the contact surfaces between the friction partner, the shoulder 31 and the friction element 33 are preferably provided with a suitable wear-resistant coating.
  • FIG. 4 shows the clamping system 1 provided with the damping device 36, with which only a damping of rotation dependent on Adjustment movements of the tension arm 4 is achievable.
  • the friction element 15b the installation position and function of which was explained in the description of FIG. 2.
  • An axial bearing 30 is provided to support an axial force triggered by the torsion spring 11 between the housing 2 and the tensioning arm 4.
  • a roller bearing inserted into an annular groove 28 of the clamping arm 4, which abuts one another on a shoulder 29 of the housing 2, is particularly suitable for this purpose.
  • the installation position of the friction element 15a is illustrated in FIG. 5.
  • the direction-of-rotation-dependent friction element 15a effectively dampens the alternating stresses impulsed into the traction mechanism drive, which are transmitted from the traction mechanism 10 to the tensioning roller 9 and thus to the tensioning arm 4. Without damping, the alternating stresses caused inadmissibly large deflections or adjusting movements of the tensioning arm 4. In particular, high-frequency adjusting movements of the tensioning arm 4 can lead to disadvantageous noise development of the tensioning arm 1.
  • FIG. 5 shows on an enlarged scale the friction element 15a in the installed state.
  • the friction element 15a which is provided with a separating joint designed as a longitudinal slot 19 and is made of plastic, non-positively encloses the bearing journal 3.
  • a spring bushing 27 is used to achieve an increased preloading force of the friction element 15a on the bearing journal 3.
  • the slotted spring bushing 27 made of steel encloses the friction element 15a almost completely.
  • Adjacent to the longitudinal slot 19, the friction element 15a forms a radially outwardly bent end section 20 which engages in a form-fitting manner in a recess 21 of the tensioning arm 4.
  • the radial distance between the bearing journal 3 and the inner wall 18 of the tensioning arm 4 radially limits the annular gap 17.
  • This distance dimension exceeds the wall thickness “s” of the friction element 15a and a wall thickness of the spring bushing 27. This creates an annular gap between the outer contour of the friction element 15 or the spring bushing 27 and the inner wall 18 of the clamping arm 4, so that the damping effect of the friction element 15a due to the Installation situation is not hindered.
  • the friction element 15a which surrounds the journal 3 almost completely non-positively, has a self-locking which is dependent on the preloading force, the frictional torque of which varies depending on the pivoting direction of the tensioning arm 4.
  • a pivoting movement of the pivot arm 4 shown in FIG. 5 counterclockwise increases the frictional moment in which the friction element 15 is acted upon via the end section 20 in the direction of a movement that reduces the longitudinal slot 19.
  • This direction of rotation which can also be referred to as a running movement, increases the frictional torque until the static friction between the bearing journal 3 and the friction element 15a is overcome and the friction element 15a follows the pivoting movement of the tensioning arm 4 at least to a limited extent.
  • a reversal of the pivoting movement of the tensioning arm 4 in the clockwise direction which can also be referred to as a running movement in relation to the friction element 15a, brings about a movement which enlarges the longitudinal slot 19 with a significantly reduced frictional torque.
  • a spring bushing 27 is used to achieve an increased prestressing force of the friction element 15a on the bearing journal 3.
  • the slotted spring bushing 27 made of steel encloses the friction element 15a almost completely.
  • FIG. 6 shows the friction element 15b in the installed state, the increased damping effect of which is effective when the tensioning arm 4 is pivoted clockwise.
  • the friction element 15b is non-positively supported on the inner wall 18 of the tensioning arm 4 and is positioned on the bearing journal 3.
  • the bearing journal 3 is provided with a recess 23 into which a radially inwardly bent end section 22 of the friction element 15b engages.
  • FIG. 6 illustrates that the wall thickness "s" of the friction element 15b increases steadily starting from the end section 22. This design enables the biasing force of the friction element 15b and the friction torque directly connected to be influenced in a targeted manner.
  • FIG. 7 shows the friction element 15c, which engages with two end sections 24a, 24b, in spaced-apart recesses 25a, 25b of the tensioning arm 4 and is held therein in a form-fitting manner.
  • a modified damping characteristic compared to the friction elements 15a, 15b. This can be influenced both by different orientations or different adjustments of the end sections 24a, 24b as well as by a different transition or by different wall thicknesses between the end sections 24a, 24b in the cylindrical region of the friction element 15c.
  • the different geometry and component rigidity of the friction element 15c in the area of the respective end sections and / or the transitions enables damping that is dependent on the direction of rotation.
  • a web 26 connects the two end sections 24a, 24b.

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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

La présente invention concerne un système de tension (1) destiné à un mécanisme de traction (10), doté d'un boîtier (2) et d'un bras de tension (4) pivotant. Afin d'obtenir un amortissement du mouvement de pivotement oscillant du bras de tension (4), ledit amortissement dépendant de la direction de rotation, un élément de friction (15a) est placé dans un espace annulaire (17) formé entre le bras de tension (4) et le tourillon (3).
PCT/EP2001/004252 2000-05-04 2001-04-12 Systeme de tension a amortissement dirige Ceased WO2001084014A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU60207/01A AU6020701A (en) 2000-05-04 2001-04-12 Tensing system with directed damping

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10021708.7 2000-05-04
DE2000121708 DE10021708A1 (de) 2000-05-04 2000-05-04 Spannsystem mit einer gerichteten Dämpfung

Publications (1)

Publication Number Publication Date
WO2001084014A1 true WO2001084014A1 (fr) 2001-11-08

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2001/004252 Ceased WO2001084014A1 (fr) 2000-05-04 2001-04-12 Systeme de tension a amortissement dirige

Country Status (3)

Country Link
AU (1) AU6020701A (fr)
DE (1) DE10021708A1 (fr)
WO (1) WO2001084014A1 (fr)

Cited By (2)

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Publication number Priority date Publication date Assignee Title
CN105114565A (zh) * 2015-09-24 2015-12-02 中国嘉陵工业股份有限公司（集团） 一种链条张紧装置
EP3574738A1 (fr) * 2018-05-30 2019-12-04 CLAAS Selbstfahrende Erntemaschinen GmbH Transmission à courroie ainsi que son procédé de fonctionnement

Families Citing this family (6)

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Publication number Priority date Publication date Assignee Title
DE10158653C1 (de) * 2001-11-30 2003-07-17 Niemann Wolfgang Ketten-oder Riemenspanner
DE10216354A1 (de) * 2002-04-13 2003-10-23 Ina Schaeffler Kg Spannvorrichtung
DE102004015100A1 (de) * 2004-03-27 2005-10-13 Ina-Schaeffler Kg Spannvorrichtung für einen Zugmitteltrieb
DE102004053209A1 (de) 2004-11-04 2006-07-13 Schaeffler Kg Spannvorrichtung für einen Zugmitteltrieb mit richtungsabhängiger Dämpfung
DE102005034322A1 (de) 2005-07-22 2007-01-25 Schaeffler Kg Dämpfungsvorrichtung für einen Zugmitteltrieb
DE102009014263B4 (de) * 2009-03-20 2019-03-28 Schaeffler Technologies AG & Co. KG Zugmitteltrieb mit Schwingungsdämpfer

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EP0425246A1 (fr) * 1989-10-23 1991-05-02 Mitsuboshi Belting Ltd. Tendeur de courroie
JPH04244644A (ja) * 1991-01-31 1992-09-01 Ntn Corp オートテンショナ
EP0525512A1 (fr) * 1991-08-01 1993-02-03 Continental Aktiengesellschaft Dispositif pour tendre une courroie de transmission
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