EP2019928A1 - Galet de tension ou de renvoi, en particulier pour l'entraînement par élément de traction d'un moteur à combustion interne - Google Patents

Galet de tension ou de renvoi, en particulier pour l'entraînement par élément de traction d'un moteur à combustion interne

Info

Publication number
EP2019928A1
EP2019928A1 EP07722402A EP07722402A EP2019928A1 EP 2019928 A1 EP2019928 A1 EP 2019928A1 EP 07722402 A EP07722402 A EP 07722402A EP 07722402 A EP07722402 A EP 07722402A EP 2019928 A1 EP2019928 A1 EP 2019928A1
Authority
EP
European Patent Office
Prior art keywords
bearing
ring
tensioning
rolling elements
ball
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
EP07722402A
Other languages
German (de)
English (en)
Inventor
Rainer Eidloth
Rainer Schenk
Georg Goppelt
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 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 KG filed Critical Schaeffler KG
Publication of EP2019928A1 publication Critical patent/EP2019928A1/fr
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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/006—Guiding rollers, wheels or the like, formed by or on the outer element of a single bearing or bearing unit, e.g. two adjacent bearings, whose ratio of length to diameter is generally less than one
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
    • F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
    • F16C19/28—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with two or more rows of rollers
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6607—Retaining the grease in or near the bearing
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7859—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a further sealing element
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/63—Gears with belts and 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
    • F16H2007/0863—Finally actuated members, e.g. constructional details thereof
    • F16H2007/0865—Pulleys

Definitions

  • Clamping or deflection roller in particular for the traction mechanism drive of an internal combustion engine
  • the invention relates to a tensioning or deflection roller according to the preamble of claim 1, and it is particularly advantageous to be arranged within a traction drive of an internal combustion engine clamping or pulleys or friction wheels for the uncoupled water pump drive to internal combustion engines.
  • the traction mechanism drive of an internal combustion engine is used to drive ancillary components of the motor vehicle, such as the light machine, the air conditioning compressor or the water pump and is generally designed as a belt drive driven by the crankshaft of the internal combustion engine. Since the individual ancillaries are functionally offset from one another arranged on the internal combustion engine, the traction mechanism drive provided with rotatably mounted on the internal combustion engine pulleys for the belt, each ensuring a sufficient wrap of the pulleys of the ancillaries. The required tension of the belt is adjusted by means of a tension roller, which is also attached to a spring force acted upon swivel arm rotatably mounted on the internal combustion engine.
  • Such clamping or deflection rollers consist essentially of a plastic or steel roller, which is essentially formed by an inner hub ring and an outer race and by a ring interconnecting both wheel disc, and from a position fixed in the hub ring of the roller radial rolling bearing, the one inner bearing ring and an outer bearing ring and from a variety between the bearing rings in grooved raceways rolling rolling elements, which are held by a bearing cage at regular intervals to each other.
  • the radial rolling bearing also has in each case a seal with which the trained as a grease deposit space between the bearing rings is sealed.
  • roller Such a tensioning or deflection roller is generic for example from DE 100 61 995 A1 previously known.
  • roller radial rolling bearing is formed in a conventional manner as a single-row deep groove ball bearing, which is cast with its outer bearing ring in the hub ring of the existing plastic roller.
  • the rolling elements of this deep groove ball bearing consist of a defined number of bearing balls, which roll in groove-shaped raceways in the inner and outer bearing ring and are held by a bearing cage at regular intervals to each other.
  • the seal formed as a grease deposit gap between the bearing rings is effected by a so-called two-stage seal, the first stage each consists of a reinforced lip seal and the second stage is formed in each case by one of the first stage with an annular sealing gap axially upstream further sealing disc.
  • the lip seals are each fixed in position in an annular groove at the outermost edge in the inner side of the outer bearing ring and are supported via an elastic sealing lip in each case a circumferential groove at the outermost edge in the outer side of the inner bearing ring of the radial roller bearing.
  • the further sealing disc is formed as a separate annular metal disc, which is plugged with its inner diameter on a head-side spigot of the mounting screw of the roller and clamped between the inner bearing ring and the screw head of the fastening screw.
  • the sealing disc extends radially over the entire height of the intermediate space between the bearing rings of the radial roller bearing and has on its outer circumference an elastic sealing lip which is supported on the axial end side of the outer bearing ring.
  • a disadvantage of this known tensioning roller is that the deep groove ball bearings used for their storage encounters more and more often at high performance and high-torque internal combustion engines by the high operating forces to the limits of its carrying capacity and thereby subject to increased wear, through which the deep groove ball bearing must be replaced prematurely ,
  • the cause of the limited load capacity of such deep groove ball bearing is to be seen in the limited number mountable bearing balls, which are introduced in such bearings in the so-called Exzentermontageclar in which the two bearing rings are arranged eccentrically to each other, thereby resulting free space between the bearing rings with the bearing balls filled and then the inner bearing ring is taking advantage of the elasticity of both bearing rings in the concentric position to the outer bearing ring.
  • the service life of the deep groove ball bearing is also dependent on the size or possible service life of the existing fat depot.
  • the size of the fat deposits is defined by the free volume of the space between the bearing rings, which is significantly reduced in the deep groove ball bearings used by the volume of the bearing balls and the bearing cage and at least in deep groove ball bearings with standard dimensions can not be extended without major expenses.
  • the invention is therefore based on the object to design a tensioning or deflecting roller, in particular for the traction drive of an internal combustion engine, which is mounted on a radial rolling bearing with standard dimensions, which increased load capacity and has an enlarged grease depot and thus characterized by lower wear and increased life and which additionally has an integrally formed sealing of the intermediate space the bearing rings.
  • this object is achieved in a tensioning or deflection roller according to the preamble of claim 1 such that the radial roller bearing is designed as a ball roller bearing whose rolling elements are formed as ball rollers with two symmetrically flattened from a spherical base and arranged parallel side surfaces, wherein the Kugelrollenla - Compared to a comparable ball bearing by the higher number of mountable rolling elements increased load capacity and at the same time by the reduced space of the rolling elements has an enlarged grease depot.
  • the trained as ball rollers rolling elements of the radial roller bearing preferably have a width between their side surfaces of about 70% of their basic ball shape.
  • the width of the raceways in the bearing rings is also at least 70% of the throughput.
  • the design of the ball rollers and the raceways with such a width has proven itself in practice with respect to the radial and axial load capacity of the bearing and corresponds approximately to the contact surface, which also have the balls conventional deep groove ball bearings to their careers in the bearing rings.
  • the distance between the bearing rings accordingly has a height of about 80% of the diameter of the ball basic shape of the rolling elements, so that the ball rollers in a lying position by the distance between the concentrically arranged bearing rings through first axially inserted into the radial roller bearing and then by a vertical and a horizontal rotation can be pivoted by 90 ° in the raceways of the bearing rings.
  • one of the characteristic features of the inventively designed clamping or deflection roller that trained as ball roller bearing radial roller bearing compared to a comparable ball bearing 30% to 40% more rolling elements and a correspondingly higher load rating and by the flattened side surfaces of Wälzkör- has at the same time a between 20% and 30% larger fat depot in the space between the bearing rings.
  • the higher number of rolling elements allows up to three times higher load capacity compared to comparable ball bearings while the larger grease supply additionally extends the life of such bearings by 1, 3 to 1, 5 times comparable ball bearings.
  • the axially on both sides of the rolling elements arranged sealing of the radial roller bearing is preferably designed as a two-step seal, the first stage each of a known reinforced lip seal but whose second stage in each case by a first stage with an annular sealing gap axially upstream another sealing disc which, together with the lip seal, can be pre-assembled by the tensioning roller manufacturer as a functional module.
  • the preferably reinforced by a sheet metal or plastic ring and made of an elastomer lip seals are on the one hand in each case fixed in position in an annular groove in the inner side of the outer bearing ring, which can be slightly offset by the narrow design of the rolling elements inwardly to the rolling elements out.
  • the lip seals are supported in a likewise known manner by sliding over one or more elastic sealing lips in each case in a circumferential groove in the outer side of the inner bearing ring of the radial roller bearing, which is also arranged offset slightly to the rolling elements.
  • the further sealing disks of the seal which are preferably produced without cutting from a metallic material, have a simple circular ring shape, each with an inner diameter-side annular flange, with which the sealing disks are preferably frictionally attached to the edge portions of the outer side of the inner bearing ring that are free by the inwardly offset lip seals.
  • the annular flange on the sealing disks is in an advantageous manner each pointing to the axial sides of the radial rolling bearing and forming a conclusion with these, so that the sealing disks can be fastened in a particularly cost-effective manner by pressing on the inner bearing ring and an integral component of the clamping or deflection roller form.
  • the further sealing discs of the seal extend radially almost over the entire height of the distance between the bearing rings and to improve the sealing effect outside diameter side optionally have additional elastic sealing lips , which are in sealing engagement with the free by the inwardly offset lip seals edge portions of the inside of the outer bearing ring. If even a water resistant, it is optionally possible to additionally insert in the annular sealing gaps between the lip seals and the sealing washers of the seal, in a known manner, in each case, a circumferential fat bead or a felt ring which at least partially seals the sealing gap fills.
  • the tensioning or deflection roller designed according to the invention thus has the advantage over the clamping or deflection rollers known from the prior art that it is mounted on a radial roller bearing of standard dimensions designed as a ball roller bearing, which is characterized by the increased number and the narrow construction the mountable rolling elements have a much higher load capacity and at the same time an enlarged fat depot compared to a comparable ball bearing and thus characterized by lower wear and increased life.
  • the ball roller bearing of the inventively designed clamping or deflection roller on a trained in integral construction sealing the gap to the bearing rings, which can be completely pre-assembled at the tension roller manufacturer and optionally formed watertight.
  • Figure 1 shows a cross section through a mounted on a single-row ball roller bearing according to the invention formed tension roller
  • Figure 2 shows a cross section through a mounted on a double row ball roller bearing according to the invention formed tension roller
  • Figure 3 is an enlarged view of a cross-sectional half of the single-row ball roller bearing according to Figure 1;
  • FIG. 4 is an enlarged view of a cross-sectional half of the double-row ball roller bearing according to FIG. 2.
  • FIGS. 1 and 2 A tensioning roller 1 for the traction mechanism drive of an internal combustion engine clearly emerges from FIGS. 1 and 2, which has a plastic or steel roller 2 which is essentially interconnected by an inner hub ring 3 and an outer race 4 and by a pair of rings 3, 4 connecting wheel disc 5 is formed.
  • a radial rolling bearing 6 is fixed in position in the hub ring 5 of the illustrated rollers 2, which consists of an inner bearing ring 7 and an outer bearing ring 8 and a plurality of rolling elements 12 and 12, 12 'arranged between the bearing rings 7, 8.
  • each radial roller bearing 6 further includes a respective seal 13, 14, with which the formed as a grease deposit space 15 between the bearing rings 7, 8 is sealed.
  • the attachment of the tension rollers 1 is then clearly visible in each case via the inner bearing ring 7 of their radial rolling bearing 6, which is centered on a receptacle 16 of a housing 17 and screwed with a fastening screw 18 on this housing.
  • the radial rolling bearings 6 shown are in each case designed as ball roller bearings whose
  • Rolling elements 12 and 12, 12 'as spherical rollers with two symmetrically flattened from a spherical base shape and arranged parallel to each other Side surfaces 19, 20 and 19, 19 ', 20, 20' are formed.
  • These trained as ball rolling elements 12 have a width between their side surfaces 19, 20 and 19, 20 and 19 ', 20' of about 70% of the diameter of their ball base shape and are initially by a height of about 80% of the diameter of the ball base the rolling elements 12 having distance 21 in a horizontal position between the concentric bearing rings 7, 8 inserted axially into the radial roller bearing 6 and then pivoted by a vertical and horizontal rotation through 90 ° in the raceways 9, 10 of the bearing rings 7, 8 ,
  • This mounting option and the flattened side surfaces 19, 20 and 19, 20 and 19 ', 20'der rolling elements 12 thereby, that designed as a ball roller bearing radial roller bearing 6 compared to comparable ball bearings 30% to 40% more rolling elements 12 and a correspondingly higher load rating and at the same time have between
  • the seal 13, 14 of the radial roller bearings 6 arranged axially on both sides of the rolling elements 12 is in each case designed as a preassemblable two-stage seal whose first stage consists of a reinforced lip seal 22, 23 and whose second stage respectively by a first stage with an annular sealing gap 26, 27 axially upstream further sealing disc 24, 25 is formed.
  • the reinforced by a metal or plastic ring unspecified lip seals 22, 23 are fixed in each case in an axially inwardly to the rolling elements 12 out offset annular groove 28, 29 in the inside of the outer bearing ring 8 and are supported by a plurality of elastic sealing lips 30, 31 grinding in each case a circumferential groove 32, 33 in the outer side of the inner bearing ring 7 of the radial roller bearing 6 from.
  • the further sealing disks 24, 25 of the seal 13, 14 produced without cutting from a metallic material have a circular ring shape, each with an inner diameter-side annular flange 34, 35, with which the sealing disks 24, 25 are pressed against the lip seals 22 displaced inwardly.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing Of Bearings (AREA)

Abstract

Galet de tension ou de renvoi, en particulier pour l'entraînement par élément de traction d'un moteur à combustion interne, qui est essentiellement constitué d'un galet de roulement en plastique ou en acier (2) formé d'une bague de moyeu interne (3), d'une bague de roulement externe (4) et d'un disque de galet (5) reliant les deux bagues (3, 4) entre elles, ainsi que d'un palier à roulement radial (6) fixé dans la bague de moyeu (3) du galet de roulement (2). Ledit palier à roulement radial est constitué d'une bague interne (7) et d'une bague externe (8) ainsi que d'une pluralité de corps roulants (12) roulant entre les bagues de palier (7, 8) dans des chemins de roulement (9, 10) en forme de rainure et maintenus à une distance régulière les uns des autres par une cage de palier (11), et possède axialement de chaque côté de ses corps roulants (12) un élément d'étanchéité (13, 14) à l'aide duquel est étanchéifié l'espace intermédiaire (15) situé entre les bagues de palier (7, 8) et conçu en tant que dépôt de graisse.
EP07722402A 2006-05-16 2007-05-10 Galet de tension ou de renvoi, en particulier pour l'entraînement par élément de traction d'un moteur à combustion interne Ceased EP2019928A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006022766A DE102006022766A1 (de) 2006-05-16 2006-05-16 Spann- oder Umlenkrolle, insbesondere für den Zugmitteltrieb einer Brennkraftmaschine
PCT/DE2007/000853 WO2007131479A1 (fr) 2006-05-16 2007-05-10 Galet de tension ou de renvoi, en particulier pour l'entraînement par élément de traction d'un moteur à combustion interne

Publications (1)

Publication Number Publication Date
EP2019928A1 true EP2019928A1 (fr) 2009-02-04

Family

ID=38472909

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07722402A Ceased EP2019928A1 (fr) 2006-05-16 2007-05-10 Galet de tension ou de renvoi, en particulier pour l'entraînement par élément de traction d'un moteur à combustion interne

Country Status (5)

Country Link
US (1) US8235851B2 (fr)
EP (1) EP2019928A1 (fr)
CN (1) CN101449070A (fr)
DE (1) DE102006022766A1 (fr)
WO (1) WO2007131479A1 (fr)

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DE102007009453A1 (de) * 2007-02-27 2008-08-28 Schaeffler Kg Mehrring-Exzenterwälzlager, insbesondere zur Wälzlagerung der Hauptzylinder von Druckmaschinen
US9416863B2 (en) * 2013-05-29 2016-08-16 Schaeffler Technologies AG & Co. KG Pulley ring
FR3006711B1 (fr) * 2013-06-07 2015-06-05 Skf Ab Systeme d'entrainement de pompe a eau et procede de montage
DE102014202791A1 (de) * 2014-02-17 2015-08-20 Schaeffler Technologies AG & Co. KG Langlebiger Wälzkörperkäfig für Kugelrollenlager
FR3018886B1 (fr) * 2014-03-19 2016-03-11 Skf Ab Dispositif de galet tendeur ou enrouleur
FR3018887B1 (fr) * 2014-03-19 2016-03-11 Skf Ab Dispositif de galet tendeur ou enrouleur
DE102015211867A1 (de) * 2015-06-25 2016-12-29 Volkswagen Aktiengesellschaft Anordnung eines drehbar gelagerten Elements an einem Gehäuse
US9845860B2 (en) * 2015-07-20 2017-12-19 Dayco Ip Holdings, Llc Retaining clamp for molded plastics
DE102017223317A1 (de) * 2017-12-20 2019-06-27 Aktiebolaget Skf Riemenscheibenvorrichtung, insbesondere für eine Spannrolle oder Laufrolle
DE102018201885A1 (de) * 2018-02-07 2019-08-08 Aktiebolaget Skf Abgedichtetes Lagermodul
FR3078759B1 (fr) 2018-03-06 2020-02-28 Aktiebolaget Skf Dispositif de poulie pour galet tendeur ou enrouleur
FR3078758B1 (fr) * 2018-03-06 2020-04-03 Aktiebolaget Skf Dispositif de poulie pour galet tendeur ou enrouleur
FR3079582B1 (fr) * 2018-04-03 2020-04-03 Aktiebolaget Skf Dispositif de poulie pour galet tendeur ou enrouleur
FR3079584A1 (fr) * 2018-04-03 2019-10-04 Aktiebolaget Skf Dispositif de poulie pour galet tendeur ou enrouleur
FR3079586B1 (fr) * 2018-04-03 2020-04-03 Aktiebolaget Skf Dispositif de poulie pour galet tendeur ou enrouleur
FR3079583B1 (fr) * 2018-04-03 2020-03-06 Aktiebolaget Skf Dispositif de poulie pour galet tendeur ou enrouleur
FR3080422B1 (fr) * 2018-04-19 2020-04-03 Aktiebolaget Skf Dispositif de poulie pour galet tendeur ou enrouleur
FR3082908B1 (fr) * 2018-06-26 2020-06-19 Aktiebolaget Skf Dispositif de poulie pour galet tendeur ou enrouleur
FR3090060B1 (fr) * 2018-12-18 2024-04-19 Skf Svenska Kullagerfab Ab Dispositif de poulie

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Also Published As

Publication number Publication date
DE102006022766A1 (de) 2007-11-22
US8235851B2 (en) 2012-08-07
US20090098967A1 (en) 2009-04-16
WO2007131479A1 (fr) 2007-11-22
CN101449070A (zh) 2009-06-03

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