WO2016028557A1 - Bague d'amortissement - Google Patents

Bague d'amortissement Download PDF

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Publication number
WO2016028557A1
WO2016028557A1 PCT/US2015/044764 US2015044764W WO2016028557A1 WO 2016028557 A1 WO2016028557 A1 WO 2016028557A1 US 2015044764 W US2015044764 W US 2015044764W WO 2016028557 A1 WO2016028557 A1 WO 2016028557A1
Authority
WO
WIPO (PCT)
Prior art keywords
contacting surface
damper
slip
contact
pivot
Prior art date
Application number
PCT/US2015/044764
Other languages
English (en)
Inventor
Sean R. SIMMONS
Original Assignee
Borgwarner Inc.
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 Borgwarner Inc. filed Critical Borgwarner Inc.
Publication of WO2016028557A1 publication Critical patent/WO2016028557A1/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
    • 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
    • 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
    • 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

Definitions

  • a tensioner including a pulley, a base having a sleeve, an arm pivotally engaged with the base with the pulley journalled to the arm, a torsion spring connected between the arm and the base, an adjuster member rotatably engaged within a sleeve hole, a damping member fixedly connected to the arm, and a retainer having an expandable member connectable to the adjuster, the expandable member engaged with a sleeve groove.
  • the damping member is compressed between the arm and the base in an axial direction and has a frictional engagement with the base to damp arm oscillation.
  • U.S. Patent Application Publication No. 2012/0316019 entitled “Tensioner” by Ward et al. and published December 13, 2012, discloses a tensioner including a sleeve, an adjuster cooperatively engaged with an inner surface of the sleeve, a pivot arm pivotally engaged with the sleeve, a pulley journalled to the pivot arm, a torsion spring engaged with the sleeve for urging the pivot arm, an elastomeric damping ring connected to the arm and in compressive frictional contact between the sleeve and the arm whereby a tangential friction force damps a pivot arm movement, and a retaining member connected to the adjuster and cooperatively engaged with the sleeve whereby the adjuster and sleeve are kept in a predetermined relation.
  • the elastomeric damping ring exerts a radial force on the sleeve.
  • a damper includes a first portion rotatable about a pivot, and a second portion fixed with respect to the pivot.
  • the first portion has at least one first contacting surface.
  • the second portion has at least one second contacting surface held in contact with the first contacting surface under a predetermined normal pre-load to form a contact area between the first portion and the second portion.
  • At least a portion of the first contacting surface or the second contacting surface has a convexly curved shape.
  • the contacting surfaces are held in micro-slip contact such that the contact area provides damping by way of micro- slip when a torque on the damper is less than a critical load value and by way of macro- slip when the torque on the damper is greater than or equal to the critical load value.
  • the damper is part of a tensioner.
  • Fig. 1 shows a perspective view of a damper with a damper ring on each contact surface in an embodiment of the present invention.
  • Fig. 4 shows a perspective view of the half of the damper of Fig. 3 with spokes.
  • Fig. 6 shows a cross sectional view of two contact surfaces of the damper of Fig. 5 under micro-slip conditions in an embodiment of the present invention.
  • the frictional damper is preferably used in a rotational mechanical tensioner for tensioning a chain or belt drive.
  • the damper includes two parts. One part is fixed to ground and the other part sees a torque load. The two parts are held together in surface contact with a normal load.
  • the damper is preferably shaped so that Hertzian contact stress is created when a normal load is applied. Hertzian contact stress is the localized stress that develops as two surfaces, at least one of which is curved, come in contact and deform slightly under the imposed loads. The amount of deformation depends on the modulus of elasticity of the materials. The contact stress is a function of the normal contact force, the curvature of the materials, and the modulus of elasticity of the materials.
  • Micro-slip occurs between contacting surfaces when a frictional load that is less than that necessary to produce macro-slip is applied to two contacting surfaces. Micro-slip requires at least a slight deformation of at least a portion of one or both contacting surfaces under the frictional load. When micro-slip occurs, at least a portion of the contacting surfaces remain in non-slip contact, while at least another portion of the contacting surfaces slide or slip with respect to each other under the frictional load. Additionally, micro-slip occurs when sliding occurs on the outer boundaries of the contact area, but the center of the contact area is held fixed by friction. In contrast, macro-slip occurs when sliding (translation) occurs across the entire Hertzian contact area.
  • micro-slip makes for a more efficient damper, since damping is generated even when macro-slip does not occur.
  • the micro-slip is preferably promoted both by the materials selected for the two parts of the damper and by the shapes of the contacting surfaces of the two parts of the damper.
  • At least one of the surfaces of the damper has at least one curved portion contacting the other surface of the damper.
  • the semi-circular cross-section feature may be pressed against a flat opposing contact surface.
  • the second surface is substantially flat or has a very large radius of curvature relative to the contact area, such as, for example, a radius at least 10 times the largest length dimension of the contact area.
  • the rings or spokes are held in contact with the second contact surface with a given pressure in the form of a normal force (F).
  • This pressure may be generated either by a spring force or by fixing the two parts of the damper a predetermined distance apart.
  • Damping may then be generated by either one of two mechanisms - a factional force from relative motion between the two rings or spokes or micro-slip between the two rings or spokes, which occurs without relative motion. In this way, the damper provides damping even at torque loads too small for relative motion between the two parts of the damper.
  • the rings or spokes, bonded to rigid substrates, are assembled into the tensioner and pressed together with a force (F).
  • This force (F) generates a friction force (f) so that when one substrate is held fixed and a tangential load (L) is applied to the other, a torque (T) is created, which is resisted by the friction force (f).
  • the friction force is overcome and macro-slip occurs when L > L cr it, where L cr it is the critical tangential load at which macro- slip occurs. Because of the shape of the damper surfaces, damping is created by micro-slip when L ⁇ Lcrit.
  • the damper may be used with any rotational tensioner that generates damping using axial force.
  • the damper may be applied to any standard tensioner arm or pulley.
  • the two parts forming the contact surfaces of the damper may be made of the same or of different materials.
  • the rings or spokes may be made from any metal, polymer, elastomer, ceramic, or composite of any type depending on the degree of micro-slip desired.
  • at least one elastomeric material is used to form at least one of the parts having a contact surface.
  • the elastomeric material is an ethylene vinyl acetate (EVA), an acsium alkylated chlorosulfonated polyethylene (ACSM), a polyacrylate (ACM), an ethylene/acrylic (EEA), a fluoroelastomer (FKM), a polychloroprene (CR), an epichlorohydrin ethylene oxide (EEO), a nitrile (NBR), a hydrogenated nitrile rubber (FiNBR), a silicone (MQ), a fluorosilicone (FVMQ), a chlorosulfonated polyethylene (CSM), or a perfluoroelastomer (FFKM).
  • EVA ethylene vinyl acetate
  • ACM acsium alkylated chlorosulfonated polyethylene
  • ACM polyacrylate
  • EOA ethylene/acrylic
  • FKM fluoroelastomer
  • CR polychloroprene
  • EEO epichlorohydrin
  • the damper works in two different domains, where L is the amplitude of the tangential force, ⁇ is the coefficient of friction between the two contacting surfaces, and F is the normal pressure force between the two contacting surfaces: L ⁇ ⁇ - micro-slip (1.1)
  • the damper 10 includes a fixed portion 20 and a moveable portion 30.
  • the fixed portion 20 includes a pair of flanges 21, 22 with mounting holes 23, 24 to mount the fixed portion 20 to a fixed surface of the engine (not shown).
  • the fixed portion 20 and the moveable portion 30 are stacked to align their central openings 26, 36, respectively, for insertion of a pivot pin (not shown - see reference number 74 in Fig. 5), around which the moveable portion 30 oscillates.
  • the damper 40 includes a fixed portion 50 and a moveable portion 60.
  • the fixed portion 50 includes a pair of flanges 51, 52 with mounting holes 53, 54 to mount the fixed portion 50 to a non-rotating surface (not shown).
  • the fixed portion 50 and the moveable portion 60 are stacked to align their central openings 56, 66, respectively, for insertion of a pivot pin (not shown see reference number 74 in Fig. 5), around which the moveable portion 60 oscillates.
  • the fixed portion 50 has a substantially flat contacting surface 90b, whereas the moveable portion 60 includes eight spokes 64 arranged around the moveable portion 60 to provide curved contacting surfaces 92a, as best shown in Fig. 4.
  • each portion 50, 60 is a single piece made of a single material.
  • the spokes 64 are made of a different material than the body 62 of the moveable portion 60.
  • one or more of the spokes 64 is made of an elastomeric material.
  • spokes 64 of a substantially identical shape are shown evenly spaced around the body 62 of the moveable portion 60, any number of spokes more than two may be used, the spokes may be unevenly spaced, or the spokes may have different shapes and may be made of the same or different materials within the spirit of the present invention.
  • the spokes 64 form areas of contact with the contacting surface of the fixed portion 50 that are substantially lines perpendicular to the direction of rotational force. In other embodiments, the spokes may be oriented to form contact area that are lines substantially tangential to the direction of rotational force or a predetermined angle between perpendicular and tangential.
  • the damper may include a stack of more than one pair of contacting surfaces forming contacting areas at different heights in the stack.
  • a damper may include two moveable portions 60 with curved contacting surfaces 92a contacting on either side of a central fixed portion 50 with contacting surfaces 90b on both sides.
  • the central fixed portion 50 may have flat contacting surfaces 90b on both sides or one or both sides may have curved contacting surfaces 90a. If the central fixed portion 50 has curved contacting surfaces 90a on one or both sides, the contacting surfaces 92a, 92b on the two flanking portions may be curved or flat.
  • the tensioner 70 includes a tensioner arm 72, which also serves as the moveable portion 72 of the damper 80.
  • the damper 80 in Fig. 5 is actually a double damper with a first damper 81 formed by the moveable portion 72 and a fixed portion 83 with contacting surfaces 92b, 90a and a second damper 82 formed by the moveable portion 72 and a fixed portion 84 with contacting surfaces 92b, 90a.
  • the moveable portion 72 and the fixed portions 81, 82 are stacked around a pivot pin 74 of the tensioner 70 to align their central openings.
  • the moveable portion 72 rotates around the pivot pin 74 when a force on the sliding surface 71 of the tensioner arm 72 from a tensioned chain or belt is sufficient to overcome friction between the contacting surfaces 92b, 90a of the damper 80.
  • each portion 83, 84 is a single piece made of a single material.
  • one or more of the rings 85, 86, 87, 88 is made of a different material than the body of the portion 83, 84.
  • one or more of the rings 85, 86, 87, 88 is made of an elastomeric material.
  • the two rings in each damper and the two dampers may be sized, shaped, and located for a predetermined damper pre-load to have either similar or different critical tangential loads.
  • the critical tangential loads of the two rings are within 5% of each other.
  • the critical tangential loads of the two rings are within 1% of each other.
  • the critical tangential loads of the two dampers are within 5% of each other.
  • the critical tangential loads of the two dampers are within 1% of each other.
  • the shapes of the contacting surfaces 90, 92 are preferably selected, in combination with the material properties of the portions forming the contacting surfaces 90, 92 to provide a predetermined combination of micro-slip and macro-slip damping properties.
  • An edge of the contact area 100 is shown in more detail in the enlarged view in Fig. 6.
  • the micro-slip region 104 spans the edge 102 of the contact area 100.
  • the shape of the second contacting surface 92a when not in contact with the first contacting surface 90, has a constant radius of curvature in the plane of Fig. 6 along the length of at least the portion of the contacting surface 92 subject to deformation. In other embodiments, the shape of the second contacting surface 92, when not in contact with the first contacting surface 90, has a radius of curvature in the plane of Fig. 6 that varies along the length of the contacting surface 92. In some embodiments, the shape of the second contacting surface 92, when not in contact with the first contacting surface 90, is symmetric in the plane of Fig. 6 that varies along the length of the contacting surface 92. In other embodiments, the shape of the second contacting surface 92, when not in contact with the first contacting surface 90, is asymmetric in the plane of Fig. 6 that varies along the length of the contacting surface 92.
  • the shapes of the contacting surfaces, the materials forming the contact surfaces, and the pre-load force are selected, in combination, to provide a contact area between the contact surfaces having a predetermined shape and
  • the pre-load force may deform the shape of one or both of the contacting surfaces as a result of the contact between the contacting surfaces.
  • the shape and dimensions of the contact area may be adjusted by adjusting one or more of the above-mentioned variables primarily to adjust or fine-tune the degree of micro-slip and macro-slip properties.
  • the shapes of the contacting surfaces, the materials forming the contact surfaces, and the pre-load force are preferably also selected, in combination, to provide a predetermined curved shape or curvature for the curved contacting surface from the region just inside the contact area to the region just outside the contact area under the conditions of the pre-load 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 porte sur un amortisseur, qui comprend une première partie pouvant tourner autour d'un pivot, et une seconde partie fixée par rapport au pivot. La première partie a au moins une première surface de contact. La seconde partie a au moins une seconde surface de contact maintenue en contact avec la première surface de contact sous une pré-charge normale prédéterminée de façon à former une zone de contact entre la première partie et la seconde partie. Au moins une partie de la première surface de contact ou de la seconde surface de contact a une forme incurvée de façon convexe. Les surfaces de contact sont maintenues en contact de micro-glissement, de telle sorte que la zone de contact assure un amortissement à l'aide d'un micro-glissement quand un couple sur l'amortisseur est inférieur à une valeur de charge critique, et à l'aide d'un macro-glissement quand le couple sur l'amortisseur est supérieur ou égal à la valeur de charge critique. Dans certains modes de réalisation, l'amortisseur fait partie d'un tendeur.
PCT/US2015/044764 2014-08-19 2015-08-12 Bague d'amortissement WO2016028557A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201462038933P 2014-08-19 2014-08-19
US62/038,933 2014-08-19

Publications (1)

Publication Number Publication Date
WO2016028557A1 true WO2016028557A1 (fr) 2016-02-25

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Country Status (1)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5456047A (en) * 1993-02-19 1995-10-10 Dorka; Uwe Friction device for protection of structural systems against dynamic actions
US20030216204A1 (en) * 2002-05-15 2003-11-20 Alexander Serkh Damping mechanism
US6702266B1 (en) * 2002-11-22 2004-03-09 The Gates Corporation Damping strut
US20120316018A1 (en) * 2011-06-08 2012-12-13 Peter Ward Tensioner
US20140014458A1 (en) * 2010-04-20 2014-01-16 Litens Automotive Partnership Tensioner with spring damper

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5456047A (en) * 1993-02-19 1995-10-10 Dorka; Uwe Friction device for protection of structural systems against dynamic actions
US20030216204A1 (en) * 2002-05-15 2003-11-20 Alexander Serkh Damping mechanism
US6702266B1 (en) * 2002-11-22 2004-03-09 The Gates Corporation Damping strut
US20140014458A1 (en) * 2010-04-20 2014-01-16 Litens Automotive Partnership Tensioner with spring damper
US20120316018A1 (en) * 2011-06-08 2012-12-13 Peter Ward Tensioner

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