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WO2010130534A1 - Unité de tendeur de courroie - Google Patents

Unité de tendeur de courroie Download PDF

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Publication number
WO2010130534A1
WO2010130534A1 PCT/EP2010/055229 EP2010055229W WO2010130534A1 WO 2010130534 A1 WO2010130534 A1 WO 2010130534A1 EP 2010055229 W EP2010055229 W EP 2010055229W WO 2010130534 A1 WO2010130534 A1 WO 2010130534A1
Authority
WO
WIPO (PCT)
Prior art keywords
torsion spring
base part
friction
belt tensioning
tensioning unit
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/EP2010/055229
Other languages
German (de)
English (en)
Inventor
Johann Singer
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and 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 AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of WO2010130534A1 publication Critical patent/WO2010130534A1/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 
    • F16H2007/0889—Path of movement of the finally actuated member
    • F16H2007/0893—Circular path

Definitions

  • the invention relates to a belt tensioning unit, in particular for a belt pulley plane of an internal combustion engine with a rotatably mounted base part and a mounted on the base part and a counterforce against a tangential force of at least one torsion spring rotatable clamping part, wherein at a relative rotation between the base part and the clamping part at least a torsion spring by changing its diameter exerts a normal force on a friction between a part of the circumference of the clamping part and a partial circumference of the base part complementary thereto.
  • Typical embodiments of generic belt tensioner have a clamping part with a relation to a belt-biased idler.
  • the clamping part is against the action of an energy storage pivotable relative to the fixedly arranged on a housing of the internal combustion engine base rotatably limited.
  • DE 10 2004 047 422 A1 discloses a generic belt tensioning device with a base part and a tensioning part.
  • the effective between energy storage during rotation energy storage is formed by a single torsion spring which is clamped at one end in the base part and at the other end in the clamping part, so that widens in a relative rotation in a rotational direction, the torsion spring and the friction means applied with a normal force , Due to the spring geometry results in a normal force, which is dependent on the tangential force of the torsion spring, that is dependent on the torsional moment of the torsion spring.
  • a belt tensioning unit in particular for a pulley plane of an internal combustion engine having a rotationally fixed arrangement.
  • the at least one torsion spring changes its diameter by a normal force to one between a partial circumference the clamping part and a partial circumference of the base part complementary thereto exerts effective friction means and only a part of the normal force corresponding to the tangential force of the at least one torsion spring is applied to the friction device.
  • a single torsion spring is proposed, wherein the normal force is weakened by an additional energy storage, without affecting the torsional force.
  • a plurality of torsion springs causing the torsional force can be arranged parallel to one another, wherein only one torsion spring is involved in the formation of the normal force acting on the friction device.
  • the torsion springs can apply the normal force radially inward according to the loop principle or radially outward by means of a diameter extension, wherein the friction means are arranged corresponding radially inside or radially outside the torsion spring and a friction surface corresponding radially outwardly, for example, on the base part or radially inside, for example, arranged on the hub is and a corresponding friction lining, which may be formed in several parts of a friction material and a support member and may be effective as a friction ring via a circular segment or almost over the entire circumference, is disposed radially between the torsion spring and the friction surface.
  • the friction lining can thereby be rotationally received on the torsion spring or on the component which does not have the friction surface, for example in the case of a friction surface arranged on the base part, on the tensioning part.
  • a belt tensioning unit wherein the friction device is limited to a single circular segment, wherein a single torsion spring acts on a circular segment-shaped, radially between the outer circumference of at least one turn of the torsion spring and a arranged on an inner surface of the base member complementary friction surface with a normal force and the at least one turn on the side opposite the friction lining is braced by means of a radially effective energy storage device supported on the hub.
  • This energy storage can be formed from a single or more individual spring elements such as radially effective coil springs used.
  • an energy storage which is made of a pre-bent to a predetermined diameter leaf spring, which is supported with its back on the at least one turn and its two ends to the hub.
  • Such an energy store reduces the normal force of the torsion spring by forming a radial counterforce to the normal force, so that damping can be achieved, for example, up to 75%, down to small values of 10% or with a corresponding reduction in the stiffness of the energy store ,
  • the application width of a belt tensioning unit formed in this way increases in the case of the installation space prescribed by the prior art. Diameter changes of the base part to reduce the stiffness of the torsion spring can be omitted.
  • a belt tensioning unit may be proposed in which the friction device is formed by a friction surface arranged on the hub and a friction lining complementary thereto, which is acted upon by a normal force radially inward by at least one turn of a single torsion spring, wherein the Torsion spring is biased by a supported on the base part energy storage against the hub.
  • this is made of a pre-bent to a predetermined diameter sheet spring formed.
  • the leaf spring is supported radially at both ends on the base part. At least one end of the torsion spring is radially supported between the two ends.
  • Such an exemplary embodiment comprises a ski spring, which is drawn when the base part and the clamping part are twisted and forms a frictional engagement between the friction surface arranged on the hub and the friction lining. Due to the radial support of one end, preferably of the end connected to the clamping part of the torsion spring on the base part, the normal force is reduced so that the friction torque can be kept low despite stiff torsion spring to counteract large torques during rotation of the base part and clamping part.
  • the energy store is preferably connected rotationally connected to the base part, clamping part and / or the torsion spring.
  • the energy storage can be positioned accurately and over life.
  • the energy store can be taken opposite the friction lining by a corresponding fixation, so that a constant reduction of the normal force is achieved.
  • this may have corresponding flared lugs or lugs that are hooked into the corresponding component.
  • Another group of embodiments provides quasi the kinematic reversal to a belt tensioning unit with a single torsion spring whose normal force is weakened by an additional energy storage.
  • a comparatively soft torsion spring is used whose normal force is effective without weakening on the friction device.
  • a further, not acting on the friction device torsion spring is connected in parallel to this, so that the necessary torsional force is effective overall by the overall stiffness of the torsion springs.
  • two torsion springs are advantageously arranged radially one above the other.
  • the radially inner or radially outer torsion spring acts on the friction device.
  • the design of the torsion springs is done in such a way that the radially inwardly arranged Nete friction device by means of a constriction and the radially outer friction device is acted upon by an extension of the diameter of the corresponding torsion spring by the normal force.
  • the stiffness ratios of the two torsion springs to each other are largely freely designable to the desired overall stiffness and the desired damping.
  • the radially outer torsion spring acts on a friction lining arranged between the at least one turn and a friction surface arranged on an inner surface of the base part by means of an enlargement of the diameter during rotation of the base and clamping parts with a normal force.
  • FIG. 1 shows a section through a belt tensioning unit according to the prior art
  • FIG. 2 shows the torsion spring of the belt tensioning unit of FIG. 1 for explaining the force relationships
  • FIG. 3 shows a cross section through a belt tensioning unit according to the invention with a leaf spring acting on the torsion spring to reduce the normal force;
  • Figure 4 shows the leaf spring of Figure 3 in view
  • FIG. 5 is an illustration of the force relationships of the belt tensioning unit of Figure 3;
  • FIG. 6 shows an alternative embodiment of a belt tensioning unit according to the invention with a friction device arranged radially on the inside;
  • Figure 7 is a representation of the power ratios of the belt tensioning unit of Figure 6 and
  • FIG. 8 shows an alternative embodiment of a belt tensioning unit according to the invention with two torsion springs in section.
  • Figure 1 shows a belt tensioning unit 1 for a traction mechanism drive according to the prior art with a fixed, for example, attached to a housing of an internal combustion engine base 2 and limited to this about the axis of rotation 1 a displaceable clamping part 3, here as a pivot arm 4, the tensioner 5 rotatably receives, is formed.
  • the tension roller 5 engages in the belt, for example, a belt, and adjusts its bias and dampens registered in the traction drive vibrations by pivoting the pivot arm 4.
  • a voltage of the belt compensating force is thereby between the base part 2 and the arm 4 by an applied between these strained energy storage 6.
  • torsion spring 7 which is rotatably braced at one end rotatably with the base part 2 and at its other end with the pivot arm 4 by means of entrainment means, wherein in the figure 1, only the axially in the direction of torsion 7 molded driving device 11 of the swing arm 4 can be seen.
  • a friction device 8 is connected, which is formed from the friction lining 9 and provided on the inner circumference of the base part 2 complementarily shaped friction surface 10.
  • the friction lining 9 is taken at a relative rotation between the pivot arm 4 and base part 2 of the pivot arm 4 by means of a further provided on the pivot arm 4 driving device 12, which may be formed in a simpler design by the driving device 11 for the coil spring.
  • the tab 13 can be entrained in circumferential direction by the entrainment device 12, wherein the tab 13 engages axially in a driving device 12 designed as a recess and is thereby entrained in both directions of rotation.
  • the friction lining 9 can be installed under prestress or with a slight clearance relative to the friction surface 10.
  • the loading of the friction lining 9 relative to the friction surface 10 by means of a normal force of the torsion spring 7, which widens during a rotation of the pivot arm 4 relative to the base part 2.
  • the torsion spring 7 is designed with respect to its rigidity so that the pivot arm 4 counteracts the vibration moments of the belt and a biasing force of the belt. Depending on the given installation space, the torsion spring 7 is widened in the case of a swivel arm 4 rotating as a result of drive train vibrations. The resulting normal force acting on the friction device 8 is dependent on the rigidity of the torsion spring 7 and thus on its torsional force.
  • Figure 2 shows with reference to the components of Figure 1, the torsion spring 7 in view.
  • the torsion spring is installed at least under slight axial preload with the axial force F 3 between clamping part 3 and base part 2 and thereby develops a certain base friction.
  • the tangential force F t is effective at a rotation of the base part 2 and clamping part 3 and generates the torsional moment of the torsion spring 7.
  • the expansion of the torsion spring 7 causes the radially outwardly effective normal force F n .
  • the torsion spring 7 must be correspondingly designed to be strong, so that the normal forces F n acting on the friction lining 9 can cause self-locking.
  • a belt tensioning unit 1 ' according to the invention is shown in cross-section in FIG. 3, in which the normal force F n is reduced by an energy store 15 designed as a leaf spring 16.
  • the belt tensioning unit Y is formed from the base part 2, which has an integrally formed about the axis of rotation 1 a axial projection 17 on which the hub 18 of the clamping part 3 is received rotatably supported by means of the sliding bearing 19.
  • the torsion spring 7 is connected between the base part 2 and the clamping part 3, the ends of which are respectively supported on not shown driving devices in the circumferential direction and adjust the torsional moment between base part 2 and clamping part 3.
  • the leaf spring 16 between the hub 18 and the turns 14 braces, which acts on the torsion spring 7, the radial force F r , which is opposite to the normal force F n .
  • the leaf spring 16 therefore, on the one hand, the friction torque of the friction device 8 is reduced and on the other hand, the torsion spring 7 to the rotation axis 1 a centered in a sufficient manner.
  • the friction torque in conjunction with the corresponding friction pair of friction lining 9 and friction surface 10 over a wide damping range of the belt tensioning unit Y can be varied.
  • the friction lining 9 may be made, for example, of plastic such as perfluorocarbons or mixtures or copolymers with other plastics, of polyamide and the like.
  • a compensation spring such as the leaf spring 16 with lubricant advantageously the friction device 8, so that very low attenuation of a belt tensioning unit such as the belt tensioning unit V can be achieved.
  • Friction lining 9 and leaf spring 16 are - in a manner not shown - rotationally connected to the clamping part 3, for example, by engaging in corresponding recesses of the clamping part 3 tabs.
  • recesses or recesses may be provided, in which engage the ends of the leaf spring 16.
  • FIG. 4 shows the leaf spring 16 of FIG. 3 in a view.
  • the leaf spring 16 is pre-bent to a predetermined diameter, which is smaller than the diameter of the hub 18 and the windings 14 of the torsion spring 7.
  • the leaf spring 16 is designed in two parts, wherein the support member 22 has a tab 23 which is issued for axial positional fixation radially outward so as to engage between the turns 14 of the torsion spring 7 ( Figure 3).
  • the spring member 24 contributes substantially to the stiffness of the leaf spring.
  • Figure 5 shows the force of the torsion spring 7 of Figure 3 with reference to the reference numerals of Figure 3.
  • the torsion spring is rotated about the axis of rotation 1 a and widened. In this case, this is compensated by a reduced normal force F n , which acts on the friction device, and the radial force F r , which is supported by the leaf spring 16 relative to the hub 18.
  • the radial force F r to be compensated for by the leaf spring 16 is, for example, a range between 500 N, taking into account an optimized damping and an associated pressure 21 of the friction lining 9 with respect to the friction surface 10 and 4000 N.
  • FIG. 6 shows a cross-sectionally similar belt tensioning unit 1 "to the belt tensioning unit V shown in FIGS. 3 to 5.
  • a torsion spring 7 in the form of a stub axle spring 7a is effectively arranged between the base part 2 and the tensioning part 3.
  • the stub axle spring 7a thereby becomes twisted of base part 2 and clamping part 3 narrows with respect to their diameter by the tangential force F t and exerts a normal force F n on the arranged as a friction ring 9a around the hub 18 of the clamping part 3 friction lining 9, with the friction surface 10 on the outer circumference of the hub 18 through the normal force F is n-related frictional engagement.
  • Figure 7 shows the force of the torsion spring 7 of Figure 6 in the free cut.
  • the radius r of the torsion spring 7 is narrowed.
  • the normal force F n is compensated by a split counterforce, which is formed on the one hand by the radial force F r of the leaf spring 16 and on the other hand by the radial force F f of the friction device. Due to the distribution of forces to compensate for the normal force F n , the friction is reduced, thereby reducing the damping of the belt tensioning unit 1 ".
  • FIG. 8 shows an alternative embodiment of a schematically illustrated belt tensioning unit 1 '"arranged around the rotation axis 1a, the base part 2a received fixedly on the internal combustion engine rotatably receiving the tensioning part 3a with the tensioning roller 5 on a bearing sleeve 26.
  • Two torsion springs 7b, 7c are effectively arranged radially above one another on the tensioning part 3a, for which purpose the spring ends of both torsion springs 7b, 7c are supported on the tensioning part 3a and the base part 2a, respectively 2a arranged sleeve 27 are separated.
  • Friction device 8 makes, so that it has a correspondingly low attenuation at high torsional moments.
  • the friction device 8 can be designed similarly to the friction device 8 of FIG. In other embodiments, a friction device may also be provided corresponding to the friction device of Figure 3, wherein preferably the radially inner torsion spring exerts the normal force.

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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 une unité (1', 1'', 1''') de tendeur de courroie, en particulier pour un plan de poulie de courroie d'un moteur à combustion interne, qui présente une partie de base (2, 2a) disposée sans pouvoir tourner et une partie de serrage (3, 3a) montée au moyen d'un moyeu (18) sur la partie de base (2, 2a) et apte à tourner de manière limitée par rapport à cette dernière en opposition à une force tangentielle (Ft) exercée par au moins un ressort de torsion (7, 7b, 7c). En cas de rotation relative entre la partie de base (2, 2a) et la partie de serrage (3, 3a), le ou les ressort(s) de torsion (7, 7b, 7c) exerce(nt) par modification de leur diamètre une force normale (Fn) sur un dispositif de frottement (8) qui agit entre une partie de la périphérie de la partie de serrage (3, 3a) et une partie complémentaire de la périphérie de la partie de base (2,2a). Pour élargir la plage d'utilisation de l'unité (1', 1'', 1''') de tendeur de courroie, en particulier en termes des propriétés de frottement du dispositif de frottement et de rigidité du ou des ressort(s) de torsion (7, 7b, 7c), l'invention propose de n'appliquer sur le dispositif de frottement qu'une partie de la force normale (Fn) qui correspond à la force tangentielle (Ft) du ou des ressorts de torsion (7, 7b, 7c).
PCT/EP2010/055229 2009-05-09 2010-04-21 Unité de tendeur de courroie Ceased WO2010130534A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910020588 DE102009020588A1 (de) 2009-05-09 2009-05-09 Riemenspanneinheit
DE102009020588.8 2009-05-09

Publications (1)

Publication Number Publication Date
WO2010130534A1 true WO2010130534A1 (fr) 2010-11-18

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ID=42211876

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PCT/EP2010/055229 Ceased WO2010130534A1 (fr) 2009-05-09 2010-04-21 Unité de tendeur de courroie

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DE (1) DE102009020588A1 (fr)
WO (1) WO2010130534A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011138100A1 (fr) * 2010-05-03 2011-11-10 Schaeffler Technologies Gmbh & Co. Kg Tendeur de courroie
US9982761B2 (en) 2013-05-14 2018-05-29 Litens Automotive Partnership Tensioner with improved damping

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3716570A1 (de) * 1987-05-18 1988-12-01 Werner Kotzab Spannvorrichtung fuer riemen und dgl., insbesondere an kraftfahrzeugmotoren
JP2003278864A (ja) * 2002-03-27 2003-10-02 Koyo Seiko Co Ltd オートテンショナ
DE102004047422A1 (de) 2004-09-28 2006-04-13 Muhr Und Bender Kg Riemenspannvorrichtung mit hoher Dämpfung
DE102005052453A1 (de) * 2005-11-03 2007-05-10 Schaeffler Kg Spanneinrichtung für ein Zugmittel, insbesondere einen Riemen
DE102007015676A1 (de) * 2007-03-31 2008-10-02 Schaeffler Kg Spannvorrichtung eines Zugmitteltriebs

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3716570A1 (de) * 1987-05-18 1988-12-01 Werner Kotzab Spannvorrichtung fuer riemen und dgl., insbesondere an kraftfahrzeugmotoren
JP2003278864A (ja) * 2002-03-27 2003-10-02 Koyo Seiko Co Ltd オートテンショナ
DE102004047422A1 (de) 2004-09-28 2006-04-13 Muhr Und Bender Kg Riemenspannvorrichtung mit hoher Dämpfung
DE102005052453A1 (de) * 2005-11-03 2007-05-10 Schaeffler Kg Spanneinrichtung für ein Zugmittel, insbesondere einen Riemen
DE102007015676A1 (de) * 2007-03-31 2008-10-02 Schaeffler Kg Spannvorrichtung eines Zugmitteltriebs

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011138100A1 (fr) * 2010-05-03 2011-11-10 Schaeffler Technologies Gmbh & Co. Kg Tendeur de courroie
US9982761B2 (en) 2013-05-14 2018-05-29 Litens Automotive Partnership Tensioner with improved damping

Also Published As

Publication number Publication date
DE102009020588A1 (de) 2010-11-11

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