WO2012143219A1 - Tendeur de courroie - Google Patents

Tendeur de courroie Download PDF

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Publication number
WO2012143219A1
WO2012143219A1 PCT/EP2012/055543 EP2012055543W WO2012143219A1 WO 2012143219 A1 WO2012143219 A1 WO 2012143219A1 EP 2012055543 W EP2012055543 W EP 2012055543W WO 2012143219 A1 WO2012143219 A1 WO 2012143219A1
Authority
WO
WIPO (PCT)
Prior art keywords
belt
spring
working position
belt drive
tensioner
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/EP2012/055543
Other languages
German (de)
English (en)
Inventor
Thomas Grabosch
Matthias Schmidl
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
Priority to CN201280019503.2A priority Critical patent/CN103492754B/zh
Publication of WO2012143219A1 publication Critical patent/WO2012143219A1/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 
    • F16H7/0829—Means for varying tension of belts, ropes or chains  with vibration damping means
    • F16H7/0831—Means for varying tension of belts, ropes or chains  with vibration damping means of the dry friction type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes or chains 
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0806—Compression coil 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 
    • F16H2007/0863—Finally actuated members, e.g. constructional details thereof
    • F16H2007/0865—Pulleys
    • 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 drive, comprising a driving pulley, one or more driven pulleys, a belt tensioned with belt pulleys and a belt tensioner with a tensioning pulley, a housing, a longitudinally movably mounted in the housing piston and the belt prestressing by means of the tensioning roller generating A helical compression spring, the force applied to the housing and the piston in the direction of extension of the belt tensioner and whose spring characteristic is tuned to the change in length of the belt tensioner within an operating range of the tension roller.
  • the nominal first external working position and the nominal second external working position of the tensioning roller are predetermined under consideration of dimensional component tolerances and thermally induced dimensional changes in the belt drive.
  • a belt tensioner to be considered in the context of the invention is composed of a linear tensioner and typically a roller lever which converts the longitudinal force resulting from the helical compression spring of the linear tensioner into belt tension via the tensioning roller mounted on the roller lever.
  • Generic linear tensioner for ancillary belt drives of internal combustion engines as they are basically known from WO2009 / 074566 and DE 10 2008 057 041 A1, consist to a large extent of plastic parts, to which the housing and the longitudinally movably mounted piston and expediently also between Include housing and piston arranged slide bearing.
  • severe wear on these contact partners can be observed, which is due to the oscillating longitudinal movement of the piston in the housing in conjunction with excessive transverse forces in the linear adjuster.
  • the present invention has for its object to improve a belt drive of the type mentioned in view of the required wear resistance of the bearings in the belt tensioner. Summary of the invention
  • i is a natural number.
  • the number of effective spring turns should be half-integer, so that the two ends of the effective turns and consequently the effective support points of the spring are offset by (ideally exactly) 180 °.
  • the inventive design of the belt drive applies, according to which the ends the effective spring coils are opposed by about 180 °, strictly speaking, only for the predetermined mean working position of the tension roller, while the spring has a different number of effective turns in the other working positions of the tension roller.
  • the average working position of the tensioning roller should be spaced symmetrically on the one hand to a nominal installation position of the tension roller and on the other hand to the first outer working position.
  • the nominal installation position corresponds to the component nominal dimensions or mean dimensions of the belt drive relative to room temperature (20 ° C.)
  • the first external working position corresponds to the maximum permissible component tolerance position of the belt tensioner in conjunction with the hot operation of the belt drive.
  • the selected average working position corresponds to a mean operating position of the tensioning roller (and thus a clamping length of the helical compression spring), in which rather the belt drive is operated most frequently when new.
  • the second outer working position of the tension roller corresponds to the maximum length of the belt tensioner component tolerance position in conjunction with the cold operation of the belt drive.
  • Figure 1 shows the layout of a belt drive to drive the ancillaries of a
  • Figure 3 is a known spring diagram of a helical compression spring
  • Figure 4 shows the torsional behavior of a helical compression spring under load
  • Figure 5 shows the spring forces on the belt tensioner in not inventive design of the belt drive
  • Figure 6 shows the spring forces on the belt tensioner in the inventive design of the belt drive.
  • FIG 1 shows an accessory belt drive of an internal combustion engine, not shown.
  • the belt drive comprises a driving pulley 6, which is arranged on the crankshaft of the internal combustion engine, and driven pulleys 7 to 10, which are arranged on the ancillaries (generator, air compressor, power steering pump, coolant pump), pulleys 1 1, 12 and one of the pulleys. 6 to 10 and the pulleys 1 1, 12 with bias winding belt 13 and a belt tensioner 14 to generate the belt pretension.
  • the principle known in its structural design belt tensioner 14 is shown in an enlarged view of Figure 2.
  • the belt tensioner 14 is composed of a linear tensioner 15 and a roller lever 16 with tensioning roller 17 mounted thereon.
  • the linear tensioner 15 comprises a housing 18, a piston 19 mounted longitudinally movably therein, and a cylindrical helical compression spring 20 clamped between the housing 18 and the piston 19 and acting in the direction of extension of the linear tensioner 15.
  • the housing 18 and the piston 19 are provided with fastening eyes 21, 22, wherein the first eye 21 on the housing 18 for stationary pivotal mounting of the linear tensioner 15 on the internal combustion engine is used and wherein the second eye 22 on the piston 19 (see Figure 6) for pivotal pivotal connection of the linear tensioner 15 with the roller lever 16 is used.
  • the stationary by the internal combustion engine pivot point 23 of the roller lever 16 is provided with a friction bushing which dampens the vibrations in the belt drive during pivotal movements of the roller lever 16.
  • the spring-loaded linear tensioner 15 is axially held together outside of the belt drive by a pin 25 which is mounted in the piston 19 and movably disposed in an axial pin stop forming slot 26 of the housing 18.
  • the piston 19, the housing 18 and the pin 25 are made of glass fiber reinforced polyamide and the sliding bush 24 made of temperature-resistant polyamide.
  • FIG. 3 shows, for a cylindrical helical compression spring 20, the wire height above the spring seat (ordinate) as a function of the wire length coordinate zeta ( ⁇ ) which runs along the spring turns (abscissa) according to the right-hand spring sketch. This typical course of the wire height results from the different pitches of the individual turns: with 1 and 5, the initial and the final turn are designated;
  • the eccentricity is additionally increased by a measure which results from a centering of the helical compression spring 20 'on the two spring supports 27, 28 carried out with a large radial play.
  • the eccentric Auflagerlhacks concept F ' L lead in conjunction with the Auflagerquer conductedn F' Q to the designated M ' L torques, due to their opposite direction of rotation as a longitudinal storage of the piston 19 in the housing 18 comparatively strongly deforming and oscillating in the high-frequency operation of the linear tensioner 15 'quickly wear the bending moment.
  • a linear tensioner 15 with inventive tuning of the helical compression spring 20 is shown in FIG.
  • An essential first difference is here selected number of effective spring coils in a predetermined operating position of the tension roller 17, as explained below with reference to Figure 1.
  • the contact and support points of the spring ends extend at 180 ° offset circumferential angles on the spring supports 27, 28, and designated with F L Auflagerlhacks
  • the spring 20 are on two maximum spaced lines of action and also eccentric to the longitudinal axis 31 of the linear tensioner 15.
  • a second difference relates to the clear and here to zero reduced radial clearance in the spring centering on the two spring supports 27, 28.
  • FIG. 1 illustrates the different positions that the tensioning roller 17 can nominally assume at the time of mounting the belt tensioner 14 and during operation of the belt drive:
  • - M denotes the (external) mounting position in which the tension roller 17 must be pivoted sufficiently far out of the belt drive to apply the belt 13;
  • - Ai refers to the first external working position of the operational work area of the tension roller 17.
  • the helical compression spring 20th maximum shortening tolerance position in conjunction with the dimensionally equivalent hot operation of the belt drive;
  • a 2 denotes the second outer working position of the operational work area of the tensioning roller 17.
  • all the component dimensions of the belt drive are in the belt tensioner 14 and thus the helical compression spring 20 maximum lengthening tolerance position in conjunction with the dimensionally equivalent cold operation of the belt drive;
  • the intermediate working position which lies exactly in the middle between the first outer working position A1 and the nominal mounting position N, is in the new state of the belt drive especially frequently started up and is therefore suitable for the wear rate of the longitudinal bearing in the Linear tensioner 15 decisive.

Landscapes

  • 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 transmission par courroie, qui comprend une poulie d'entraînement (6), une ou plusieurs poulies entraînées (7, 8, 9, 10), une courroie de transmission (13) enserrant les poulies avec une pré-tension (13) et un tendeur de courroie (14) comprenant un rouleau de tension (17), un boîtier (18), un piston (19) placé de manière mobile longitudinalement dans celui-ci et un ressort à compression hélicoïdale (20) générant la pré-tension de la courroie au moyen du rouleau de tension, dont la caractéristique de ressort est ajustée à la modification longitudinale du tendeur de courroie dans une plage de travail opérationnelle du rouleau de tension. Selon l'invention, la première position de travail extérieure nominale (A1) et la seconde position de travail extérieure nominale (A2) du rouleau de tension sont prédéterminées en prenant en compte des tolérances dimensionnelles des composants et des modifications dimensionnelles d'origine thermique dans la transmission par courroie. Afin d'améliorer la résistance à l'usure du tendeur de courroie, la plage de travail du rouleau de tension doit comprendre une position de travail intermédiaire prédéterminée (AM), à laquelle les spires du ressort à compression hélicoïdale sont tordues les unes contre les autres de manière à ce que le nombre de spires de ressort actives soit sensiblement de n = i+0,5, i étant un nombre naturel.
PCT/EP2012/055543 2011-04-21 2012-03-28 Tendeur de courroie Ceased WO2012143219A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201280019503.2A CN103492754B (zh) 2011-04-21 2012-03-28 带张紧器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011007877.0 2011-04-21
DE201110007877 DE102011007877A1 (de) 2011-04-21 2011-04-21 Riemenspanner

Publications (1)

Publication Number Publication Date
WO2012143219A1 true WO2012143219A1 (fr) 2012-10-26

Family

ID=46085541

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/055543 Ceased WO2012143219A1 (fr) 2011-04-21 2012-03-28 Tendeur de courroie

Country Status (3)

Country Link
CN (1) CN103492754B (fr)
DE (1) DE102011007877A1 (fr)
WO (1) WO2012143219A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107355520A (zh) * 2017-08-08 2017-11-17 重庆通用航空产业集团有限公司 张紧装置

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017003300B3 (de) * 2017-04-05 2018-04-12 Mtu Friedrichshafen Gmbh Riemenspannvorrichtung
US10830316B2 (en) * 2017-12-08 2020-11-10 Gates Corporation Tensioner
CN108278342B (zh) * 2017-12-26 2023-11-07 盖茨优霓塔传动系统（上海）有限公司 张紧器
CN109538722A (zh) * 2019-01-25 2019-03-29 南京工艺装备制造有限公司 一种多级行星滚柱丝杠副无间隙直线运动执行器

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007097261A1 (fr) * 2006-02-20 2007-08-30 Ntn Corporation Tendeur automatique hydraulique
WO2009074566A1 (fr) 2007-12-10 2009-06-18 Schaeffler Kg Élément élastique mécanique pour transmissions par lien souple
DE102008057041A1 (de) 2008-11-12 2010-05-20 Schaeffler Kg Linear wirkendes Spannelement

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE20319886U1 (de) * 2003-12-22 2005-05-04 Litens Automotive Gmbh Automatischer Riemenspanner
DE102007015676A1 (de) * 2007-03-31 2008-10-02 Schaeffler Kg Spannvorrichtung eines Zugmitteltriebs
CA2738697C (fr) * 2008-10-02 2017-01-03 Litens Automotive Partnership Tendeur compact avec amortissement durable
WO2010094127A1 (fr) * 2009-02-19 2010-08-26 Litens Automotive Partnership Tendeur présentant des propriétés de micro-réglage

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007097261A1 (fr) * 2006-02-20 2007-08-30 Ntn Corporation Tendeur automatique hydraulique
WO2009074566A1 (fr) 2007-12-10 2009-06-18 Schaeffler Kg Élément élastique mécanique pour transmissions par lien souple
DE102008057041A1 (de) 2008-11-12 2010-05-20 Schaeffler Kg Linear wirkendes Spannelement

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107355520A (zh) * 2017-08-08 2017-11-17 重庆通用航空产业集团有限公司 张紧装置

Also Published As

Publication number Publication date
CN103492754B (zh) 2016-03-16
DE102011007877A1 (de) 2012-10-25
CN103492754A (zh) 2014-01-01

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