US20080153642A1 - Eccentric tensioning device - Google Patents

Eccentric tensioning device Download PDF

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Publication number
US20080153642A1
US20080153642A1 US11/776,638 US77663807A US2008153642A1 US 20080153642 A1 US20080153642 A1 US 20080153642A1 US 77663807 A US77663807 A US 77663807A US 2008153642 A1 US2008153642 A1 US 2008153642A1
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US
United States
Prior art keywords
eccentric
tensioning device
work
base plate
traction means
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.)
Abandoned
Application number
US11/776,638
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English (en)
Inventor
Rainer Baumuller
Roland Arneth
Niels Flamig
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
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Schaeffler KG
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Assigned to SCHAEFFLER KG reassignment SCHAEFFLER KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ARNETH, ROLAND, BAUMULLER, RAINER, FLAMIG, NIELS
Priority to DE502007006275T priority Critical patent/DE502007006275D1/de
Priority to AT07822800T priority patent/ATE495391T1/de
Priority to PCT/EP2007/062667 priority patent/WO2008077696A1/de
Priority to EP07822800A priority patent/EP2115322B1/de
Publication of US20080153642A1 publication Critical patent/US20080153642A1/en
Priority to US12/754,224 priority patent/US7918755B2/en
Assigned to SCHAEFFLER TECHNOLOGIES GMBH & CO. KG reassignment SCHAEFFLER TECHNOLOGIES GMBH & CO. KG MERGER AND CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: SCHAEFFLER KG, SCHAEFFLER VERWALTUNGS DREI KG
Assigned to Schaeffler Technologies AG & Co. KG reassignment Schaeffler Technologies AG & Co. KG CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG
Assigned to SCHAEFFLER TECHNOLOGIES GMBH & CO. KG reassignment SCHAEFFLER TECHNOLOGIES GMBH & CO. KG MERGER AND CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: Schaeffler Technologies AG & Co. KG, SCHAEFFLER VERWALTUNGS 5 GMBH
Assigned to Schaeffler Technologies AG & Co. KG reassignment Schaeffler Technologies AG & Co. KG CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG
Assigned to Schaeffler Technologies AG & Co. KG reassignment Schaeffler Technologies AG & Co. KG CORRECTIVE ASSIGNMENT TO CORRECT THE PROPERTY NUMBERS PREVIOUSLY RECORDED ON REEL 037732 FRAME 0347. ASSIGNOR(S) HEREBY CONFIRMS THE APP. NO. 14/553248 SHOULD BE APP. NO. 14/553258. Assignors: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG
Abandoned legal-status Critical Current

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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
    • F16H7/1254—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means
    • F16H7/1281—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means where the axis of the pulley moves along a substantially circular path
    • 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
    • F16H7/10—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
    • F16H7/1236—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 fluid and restriction type, e.g. dashpot
    • 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
    • F16H2007/0842—Mounting or support of tensioner
    • 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
    • F16H2007/0842—Mounting or support of tensioner
    • F16H2007/0844—Mounting elements essentially within boundaries of final output members
    • 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
    • F16H2007/0846—Means for varying tension of belts, ropes, or chains comprising a mechanical stopper
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49826—Assembling or joining

Definitions

  • the present invention relates to an eccentric tensioning device for tensioning a traction means constructed, for example, as a flat belt or toothed belt, in a traction means drive.
  • the invention here relates to an eccentric tensioning device, which is provided for integration into a traction means drive of an internal combustion engine, which automatically guarantees a required pretensioning of the traction means through an adjustment moment generated on the side of a spring device.
  • Such a tensioning device is known, for example, from DE 40 33 777 A1.
  • This conventional tensioning device also designated as a double eccentric tensioning device, comprises an adjustment eccentric, which makes available a bore arranged eccentrically for receiving an attachment screw.
  • the tensioning device is mounted on a housing, especially a housing of the internal combustion engine, wherein the adjustment eccentric is supported by means of a base plate on the housing.
  • Placed on this adjustment eccentric is a working or operating eccentric, with there being a plain or slide bearing in an annular gap between a casing surface of the adjustment eccentric and an inner wall of the operating eccentric.
  • a rolling bearing surrounds the operating eccentric, whose outer ring provides the function of a running disk, which in the installed state presses against the traction means of the traction means drive and applies a force to this with a transverse force extending perpendicular to the running direction.
  • a torsion spring which forces the operating eccentric and the running disk connected to this operating eccentric continuously into a position loading and thus tensioning the traction means.
  • the invention is based on the objective of creating solutions, through which advantages are produced under assembly-specific aspects in the installation of tensioning devices of the type noted above.
  • an eccentric tensioning device for a traction means drive with:
  • a track roller device which as such comprises a running disk and a rolling bearing provided for supporting the running disk
  • a work eccentric for supporting the track roller device such that it can be displaced in a radial direction relative to the rotating axis of the rolling bearing through pivoting of the work eccentric
  • a fixing device for securing the work eccentric in a mounting position, in which the torsion spring is located in pretensioned state
  • the fixing device is constructed such that it is led into a released state, in which the running disk is forced under the effect of the work eccentric radially relative to the rotating axis of the rolling bearing against the associated traction means, within the scope of attaching the eccentric tensioning device to a flange surface carrying this device.
  • the work or operating eccentric is fixed in an end position under pretensioning of the torsion spring, wherein this secured state can be released by the installation of the tensioning device.
  • the work eccentric is preferably fixed in each mounting position so that relative movements between the work eccentric and the base plate and/or the adjustment eccentric are prevented.
  • the fixing device is constructed such that this automatically detaches in the course of tightening an attachment screw, through which as such the eccentric tensioning device, in particular the adjustment eccentric of this device, is screwed onto a flange surface carrying the tensioning device.
  • This automatic detachment or release process of the fixing device can be initiated, in particular, in that a free switching path is traversed or an axial play provided in the tensioning device is overcome within the scope of attaching the eccentric tensioning device to the flange surface of components of the tensioning device under the effect of the axial force applied by the attachment screw.
  • an engagement structure of the fixing device can be brought into a released state.
  • the engagement structure is preferably coupled rigidly with the work eccentric.
  • the fixing device according to the invention is preferably shaped so that in the mounting position, the engagement structure is engaged with a holding element, which is provided by the base plate.
  • the engagement structure is brought into the released state preferably through axial displacement of the engagement structure relative to the holding element.
  • the spring device provided for generating the torsion moment pivoting the work eccentric is preferably constructed as a helical spring.
  • This helical spring can be embodied so that it has several spring windings.
  • the helical spring can be constructed as a leg-less helical spring, so that the forces generated by this helical spring are introduced via the ends of the spring ends and optionally via a peripheral section offset from these ends by an angle of typically 90° into the appropriate components loaded by the spring.
  • the spring can also be provided in the area of the spring ends with engagement structures, especially in the form of hook sections formed by radially inwards or outwards bent wire ends.
  • the spring device can be shaped in terms of the cross section of the spring wire so that this has a polygonal, in particular a square or flat cross section. Furthermore, the spring device is preferably shaped so that in the installed state, this is also at least slightly flattened, e.g., to 30% of its length in the axially unloaded state.
  • the tensioning device according to the invention preferably comprises a damping or braking device, which as such is used for generating an eccentric braking moment, through which the pivoting of the work eccentric is braked.
  • This damping or braking device can be formed by an axially loaded disk structure, by a radially loaded bushing structure, or also by a cone structure.
  • at least one part of the loading force acting on this damping or braking device is generated or transmitted by the torsion spring.
  • the work eccentric can be made from a plastic material. Furthermore, it is also possible to construct the work eccentric in one piece with the inner ring of the rolling bearing. Furthermore, it is also possible to construct the running disk in one piece with the outer ring of the rolling bearing.
  • the work eccentric is supported on an adjustment eccentric.
  • the fixing device according to the invention preferably the position of the work eccentric is also fixed relative to the adjustment eccentric. It is possible to shape the tensioning device structurally so that the adjustment eccentric can be displaced by a small distance axially relative to the work eccentric or a base plate, wherein the released state of the fixing device can be generated in the course of the axial displacement of the adjustment eccentric, especially under the action of the attachment screw.
  • the base plate is preferably shaped such that this comprises an annular disk section provided for mounting on the flange surface.
  • This annular disk section can be shaped so that this is coupled locked in rotation with a bearing bushing in the area of an inner peripheral edge.
  • a projection or some other engagement structure can be formed, which as such is used for rotationally locked anchoring of the base plate on the flange surface.
  • the projection is shaped so that the rotationally locked anchoring of the base plate on the flange surface is reached before the axial release path has been overcome.
  • the tensioning device according to the invention so that the creation of the released state is not realized through axial loading of the tension roller device, but instead, for example, by pivoting the work eccentric back against the pivoting direction caused by the torsion spring.
  • a spring elastic locking element preloaded for example, in a released position, can be unlocked and here can release the work eccentric, so that this is pivoted towards the traction means running path under the effect of the torsion spring and thus the running disk can be lowered onto the traction means.
  • securing means are provided, through which re-engagement of the fixing device is prevented. In this way it becomes possible to guarantee that no inadvertent relocking of the fixing device is performed during the operation of the tensioning device.
  • the invention includes, in particular, the following variants:
  • a radially directed indexer connected to the operating eccentric is supported with a firm fit and/or a positive fit on a holding element of the base plate or the adjustment eccentric.
  • the work eccentric and thus the indexer connected to it are pressed and thus fixed in position on the holding element of the base plate due to the force of the torsion spring with a rotationally non-positive fit.
  • the indexer assumes this position through a limited axial displacement of the work eccentric relative to the adjustment eccentric, wherein this displacement acts against an axial force component of the torsion spring. From this starting position, the tensioning device is positioned loosely, i.e., without rigid attachment, to the internal combustion engine, with the help of the attachment screw.
  • an aligned installation position of the tensioning device is set.
  • the operating eccentric is fixed at an end stop, which is also designated as a hot stop, whereby the traction means, in particular a belt, can be mounted easily, i.e., can be placed on all of the running disks of the traction means drive.
  • the adjustment eccentric and the base plate connected to this eccentric are displaced axially in the direction of the internal combustion engine, whereby the indexer connected in one piece with the base plate detaches from the holding element and the torsion spring turns the operating eccentric into a position pretensioning the traction means.
  • the release of the indexer and thus the work eccentric from the locking during the mounting position is then reached as soon as an axial play “S” between the work eccentric and the base plate or the adjustment eccentric is equalized or reduced by tightening the tensioning device.
  • an indexer connected to the work eccentric or a similarly formed object is actively connected to a stop of the base plate.
  • the locking can be realized through suitable shaping of the base plate alone or with the help of additional elements, e.g., splints or a plate, which are removed after the traction means are placed, in order to tension the traction means.
  • Another variant for positioning the operating or work eccentric in a mounting position provides for the shaping of the locking device for maintaining the pretensioned torsion spring, so that this does not exceed the radial outer contours of the tensioning unit.
  • Suitable for this purpose is, for example, a groove or recess formed on the end towards the flange surface of the internal combustion engine in the work eccentric or in the base plate, in which a locking device is engaged through a positive fit, force-generated fit, or through a combination of these two fits, in order to prevent rotational movement of the work eccentric relative to the base plate or the adjustment eccentric in the mounting position.
  • the object interacting with the groove or the recess which is located according to the arrangement of the connecting rod either on the base plate or the work eccentric, can be constructed as a bent part, cast part, or as an add-on part (e.g., as a dowel pin).
  • the projection of the object out of the groove or the recess in the direction of the beginning of the groove is prevented by the clamping of the work eccentric and the associated limiting of the axial play of the tensioning unit.
  • the object encompasses the work eccentric. In the mounting position, in particular a molded part connected to the base plate engages in a groove or recess of the work eccentric. Due to the axial force of the torsion spring, in the mounting position there is effective locking between the base plate and the work eccentric.
  • the invention is directed, in particular, to tensioning devices, which guarantee a nearly constant pretensioning force of the traction means under all operating conditions and with which a long service life can be achieved.
  • the measures according to the invention allow a semi-automated setting of the desired traction means force for the first assembly and for service work for equalizing:
  • the invention is further directed also to a method for integrating an eccentric tensioning device in a traction means drive of an internal combustion engine, in which an eccentric tensioning device located in a pretensioned state is partially attached to a flange surface within the scope of a prepared assembly step, such that the eccentric tensioning device remains in a pretensioned state, wherein in this pretensioned state the eccentric tensioning device is configured and oriented such that the running roller of this device has a large distance from the traction means running path, and wherein the eccentric tensioning device is brought into a released state through tightening of an attachment screw used for the fastening, in which the pretensioned state is released and the running roller is lowered onto the associated traction means of the traction means drive.
  • FIG. 1 an axial section view for illustrating the construction of a double eccentric tensioning device according to the invention
  • FIG. 2 a perspective view of the base plate of the eccentric tensioning device according to FIG. 1 ,
  • FIG. 3 a perspective view of the work eccentric of the tensioning device according to FIG. 1 ,
  • FIG. 4 a detail view for illustrating the construction of the fixing device of the eccentric tensioning device according to FIG. 1 ,
  • FIG. 5 another axial section view for illustrating the eccentric tensioning device according to the invention, here in a state axially inserted and thus brought into a released position
  • FIG. 6 a perspective view of the work eccentric of an eccentric tensioning device according to the invention according to a second embodiment of the invention
  • FIG. 7 a perspective view of a base plate structure, which as such interacts with the work eccentric according to FIG. 6 ,
  • FIG. 8 a perspective view of a tensioning device formed with the inclusion of the work eccentric and the base plate according to FIGS. 6 and 7 ,
  • FIG. 9 a perspective exploded view for illustrating the construction of the eccentric tensioning device according to FIG. 8 .
  • FIG. 10 another perspective view for illustrating the double eccentric tensioning device according to FIG. 8 in unlocked state
  • FIG. 11 a perspective detailed view for illustrating the engagement state of the fixing device in a double eccentric tensioning device according to FIG. 8 ,
  • FIG. 12 a perspective view of a double eccentric tensioning device according to a third embodiment of the invention.
  • FIG. 13 a perspective view of a double eccentric tensioning device according to the invention according to a fourth embodiment of the invention with an indexer device blocked by a stop,
  • FIG. 14 a side view for illustrating additional details of the double eccentric tensioning device according to FIG. 12 .
  • FIG. 15 a perspective view of a fifth embodiment of a double eccentric tensioning device according to the invention with a securing pin lying outside of the periphery of the tension roller device,
  • FIG. 16 a perspective view of the base plate of the double eccentric tensioning device according to FIG. 15 .
  • FIG. 17 a a perspective view of the base plate for a double eccentric tensioning device according to a fifth embodiment of the invention.
  • FIG. 17 b a sketch for illustrating the function of the fixing device formed in interaction with the base plate according to FIG. 17 a
  • FIG. 18 another sketch for illustrating the construction of a base plate for realizing a fixing device according to the invention
  • FIG. 19 a view for illustrating the individual phases of the mounting process for connecting the tensioning device according to the invention to an internal combustion engine
  • FIG. 20 a basic sketch for illustrating another mechanism for automatically releasing a tensioning device according to the invention
  • FIG. 21 a basic sketch for illustrating another variant of an automatically releasable fixing device
  • FIG. 22 another sketch for illustrating a fixing device according to the invention with a spring elastic securing arm pretensioned into a released position.
  • FIG. 1 shows a tensioning device according to the invention in the form of an axial section view.
  • the tensioning device 1 comprises an adjustment eccentric 2 , which is inserted into a carrier body 3 constructed as a cylindrical bushing, by means of which the tensioning device 1 in connection with an attachment screw not shown in FIG. 1 can be connected to a flange surface F, especially an end of an internal combustion engine.
  • the tensioning device 1 further comprises a work or operating eccentric 5 , which is arranged rotatably on the carrier body 3 by means of a plain or slide bearing 4 .
  • the work eccentric 5 is surrounded by a rolling bearing 6 , on which in turn a running disk 7 is positioned, which makes firm contact with a traction means with in the installed state.
  • a torsion spring 9 is provided, which is supported with a first spring end on the work eccentric 5 and with the other spring end on a base plate 8 .
  • This base plate 8 is connected locked in rotation with the carrier body 3 in this embodiment.
  • the adjustment eccentric 2 can pivot about a pivoting axis E 2 defined by the attachment screw.
  • the work eccentric 5 can pivot about an eccentric axis E defined by the outer peripheral surface of the carrier body. This eccentric axis E is radially offset relative to a rotating axis X of the rolling bearing 6 .
  • the work eccentric 5 and the adjustment eccentric 2 are each arranged in a pivoted position, in which the greatest possible distance of the traction means running surface of the running disk 7 from the traction means running path is produced.
  • the base plate 8 is provided with an axially extending projection 10 , which engages in a corresponding receptacle of the internal combustion engine (indicated here as a bore) provided in the area of the flange surface.
  • An indexer 11 arranged locally on the work eccentric 5 illustrates the pivoted position of the work eccentric 5 in the installed state of the tensioning device 1 .
  • the tensioning device 1 is constructed such that an axial play “S” initially remaining between an end face of the work eccentric 5 and the base plate 8 is eliminated within the scope of the mounting of the tensioning device, especially tightening the attachment screw (as has already happened here).
  • the tensioning device comprises a locking device 12 , which automatically detaches within the scope of the advancing attachment of the tensioning device to the internal combustion engine and after placement of a traction means in the traction means drive due to a completed mounting step.
  • the following description relates in particular to the locking device 12 according to the invention and active here between the base plate 8 and the work eccentric.
  • the mounting step provided for releasing this locking device includes completing the tightening of the attachment screw not shown here in more detail. During this tightening, the axial play S mentioned above is overcome and the work eccentric 5 unlocked in this way pivots automatically into a position pretensioning the traction means under the effect of the torsion spring 9 .
  • FIGS. 4 and 5 show structural details of the locking device 12 with reference to detailed drawings.
  • FIG. 3 shows in the form of a perspective view how the work eccentric 5 is used in the tensioning device according to FIG. 1 .
  • the work eccentric 5 comprises an axially projecting section 13 , in which a recess or groove 14 and an engagement recess 16 is formed.
  • a radial cam 15 constructed in one piece with the base plate 8 shown in FIG. 2 locks in the engagement recess 16 .
  • a block can prevent the cam 15 from leaving the groove 14 in the direction of a beginning of the groove 16 .
  • Automatic detachment of the locking device 12 is realized through tightening of the attachment screw, in which the axial play “S” ( FIG. 1 ) between the end face of the work eccentric 5 and the base plate 8 is simultaneously reduced, whereby the cam 15 detaches from the engagement recess 16 and is inserted into the groove 14 . In this way, a released state is reached, in which the work eccentric 5 automatically pivots into a position pretensioning the traction means.
  • FIG. 4 shows in the form of an enlarged view the detail designated by the reference symbol Z in FIG. 1 .
  • the cam 15 connected to the base plate 8 is inserted into the groove 14 .
  • FIG. 5 shows the tensioning device 1 in a view, from which the construction of the locking device 12 becomes clearer.
  • the tensioning device is located in the state shown here in a released position, in which pivoting of the work eccentric 5 is allowed.
  • FIGS. 6 to 11 a second embodiment of a tensioning device according to the invention is shown, which differs from the first embodiment especially in terms of the shape of the fixing device or locking device 17 .
  • the base plate 8 is provided locally with an axially extending projection 18 .
  • a radially inwardly directed projection 19 is formed on the end on this projection 18 .
  • the work eccentric 5 has a corresponding recess 21 or groove 22 , in which the projection 19 locks with a positive fit in the mounting position, i.e., in the pretensioned state.
  • the projection 18 of the base plate 8 surrounds the outer contours of the work eccentric 5 in the region of the groove 22 or recess 21 , wherein the radial outer contours of the running disk 7 are not exceeded.
  • the tensioning device 1 is provided with a rotation limiter 23 for the work eccentric 5 .
  • the base plate 8 has a locally bent rim 24 , which engages with a positive fit in a recess 25 of the work eccentric 5 , wherein the extent of the recess 25 determines the maximum rotation of the work eccentric 5 relative to the base plate 8 .
  • the mounting-optimized tensioning device comprises a rolling bearing 6 , which is constructed as a sealed, double-row ball bearing and which comprises its own inner ring 6 a , an outer ring 6 b , and a bearing seal 6 c .
  • This rolling bearing 6 sits on an outer peripheral surface 6 a of the work eccentric 5 over the cylindrical inner surface formed by the inner ring 6 a .
  • the work eccentric 5 is constructed such that an eccentric axis E defined by its inner bore 5 b is radially offset relative to a rolling bearing rotating axis X defined by the inner ring 6 a .
  • This degree of offset corresponds to half the maximum necessary radial adjustment tensioning lift of the work eccentric in the operating state of this eccentric.
  • the coupling of an adjustment tensioning torque pivoting the work eccentric 5 is performed under the effect of the torsion spring 9 shown here and constructed as a helical spring. This torsion spring 9 is supported on an inner region that cannot be seen here in more detail in a bell-shaped section 5 c of the work eccentric 5 .
  • the rotationally locked anchoring of the torsion spring 9 on the work eccentric 5 is realized by a radially outwardly bent engagement end 9 a of the torsion spring 9 .
  • the attachment of the torsion spring 9 on the work eccentric 5 is implemented such that a sufficiently more reliable engagement is also guaranteed under unfavorable operating or mounting conditions. It is possible to provide retaining elements, through which an especially reliable coupling state between the torsion spring 9 and the work eccentric 5 is guaranteed on the work eccentric 5 , on the torsion spring 9 , or also via additional securing structures.
  • the torsion spring 9 is supported with its second end section 9 b on the base plate 8 .
  • the base plate 8 forms a structural component, which can be flanged at the projection 10 already discussed above so that it is locked from rotation to a flange surface provided for receiving the tensioning device, especially an end face of an engine block or cylinder head.
  • the base plate 8 further forms a structural component, through which the work eccentric 5 can be locked in a pivoted position, in which the torsion spring 9 arranged kinematically between the base plate 8 and the work eccentric 5 is tensioned.
  • This locked position can correspond especially to the position, in which the rolling bearing 6 has been lifted farther from the running path of the associated traction means of a traction means drive.
  • the locking device comprises a projection 18 , which is formed on the base plate 8 and which as such carries a catch structure that is constructed as a projection 19 and that can engage in a counter structure or groove 22 provided on the side of the work eccentric 5 , especially the bell section 5 c of this eccentric, as can be seen better from the other views.
  • an engagement state set between the base plate 8 and the work eccentric 5 is released, in that the work eccentric 5 is pushed in a direction of its eccentric axis E towards the base plate 8 , so that the projection 19 moves axially out of the groove 22 and thus unlocks the work eccentric 5 in the peripheral direction and thus allows pivoting of this eccentric under the effect of the pivoting moment applied by the torsion spring 9 .
  • the pivoting coupling of the work eccentric 5 with the base plate 8 is implemented in this embodiment by a carrier body 3 constructed as a bushing, which here is coupled preferably locked in rotation with an inner peripheral region 8 a of the base plate 8 . This coupling can be realized, in particular, by pressing a foot region 3 a of the carrier body 3 into the base plate 8 .
  • the work eccentric 5 does not sit directly on an outer peripheral surface 3 b provided by the carrier body 3 , but instead sits on the carrier body 3 under inclusion of a bushing constructed as a slide bearing, as shown here.
  • the slide bearing 4 can be constructed, so that a certain friction moment is generated by this bearing, through which the pivoting motion of the work eccentric 5 is braked or damped on the carrier body 3 .
  • the slide bearing 4 It is possible to shape the slide bearing 4 so that different braking moments for moving the work eccentric 5 in the adjustment tensioning direction and also in the counter direction are generated by this bearing.
  • the slide bearing bushing 4 it is possible, in particular, to construct the slide bearing bushing 4 as a slotted structure, so that especially when the work eccentric 5 pivots against the adjustment tensioning direction, a greater friction moment is produced than when the work eccentric 5 pivots in the adjustment tensioning direction.
  • the mounting-optimized tensioning device according to the invention can also be shaped in some other way in terms of the torsion spring device and also especially in terms of the damping device.
  • the attachment of the mounting-optimized tensioning device shown here can be performed by an attachment screw, which as such is passed through the inner bore 3 c provided by the carrier body 3 .
  • This inner bore 3 c is shaped so that this has a considerably larger diameter than the attachment screw required for sufficient attachment of the tensioning device.
  • the intermediate space remaining between the outer region of the shaft of the corresponding attachment screw and the inner peripheral wall 3 c can be filled by an eccentric body formed as an adjustment eccentric, so that in addition to the radial displacement of the rolling bearing 6 achieved by the work eccentric 5 , the entire tensioning device can also still be fixed through corresponding pivoting of the adjustment eccentric inserted into the inner bore 3 c.
  • the axial displacement of the work eccentric 5 towards the base plate takes place within the scope of tightening the attachment screw provided for attaching the tensioning device to an internal combustion engine.
  • the attachment screw is tightened only slightly, so that the tensioning device is definitely already sufficiently secured on the internal combustion engine, but the fixing device realized between the base plate 8 and the work eccentric 5 still remains in a secured state. Only after a traction means has been placed in the traction means drive, after the adjustment eccentric is pivoted into a position that is closest to the rolling bearing axis X on the running path of the traction means, is the attachment screw tightened further and thus the fixing device is brought into a released state.
  • the work eccentric 5 snaps into a tensioned position under the effect of the torsion spring 9 and thus exerts a pressure force on the traction means defined by the tensioning moment generating the torsion moment of the torsion spring 9 .
  • FIG. 10 in the form of a perspective detailed view, the fixing device provided in the tensioning device according to FIG. 9 is shown in an engaged state.
  • the work eccentric 5 is coupled locked in rotation with the base plate 8 .
  • This rotationally locked coupling is constructed by the engagement of the engagement structure constructed as projection 19 with the counter structure provided as engagement groove 22 and provided on the side of the work eccentric 5 .
  • the projection 19 can move out of the groove 22 into the area of the recess 21 and thus frees the work eccentric 5 relative to the base plate 8 .
  • the displacement of the work eccentric 5 is the direction of arrow P 1 is realized in this embodiment against an axial force generated by the torsion spring 9 .
  • an indexer 26 is formed, by means of which the pivoted state of the work eccentric 5 can be better seen from the outside.
  • the fixing device is shaped such that the locking structure engaged with the work eccentric 5 engages radially from the outside into a counter structure provided by the work eccentric 5 .
  • this fixing device it is also possible to shape this fixing device, as described in more detail in the following embodiment, such that this engages from the inside into a corresponding counter structure of the work eccentric 5 .
  • FIG. 11 the mounting-optimized tensioning device according to the invention from FIGS. 8 to 10 described above is shown in a state, in which the previously described fixing device is located in a detached position, in which the work eccentric 5 can be pivoted freely relative to the base plate 8 .
  • the engagement structure constructed as a projection 19 is located in the area of the recess 21 and in this position can no longer engage with the engagement structure constructed as groove 22 provided by the work eccentric 5 .
  • FIGS. 12 to 18 show additional constructions of locking devices according to the invention for the work eccentric 5 relative to the base plate 8 .
  • an indexer 26 connected in one piece with the work eccentric 5 is secured on the base plate 8 .
  • the locking device 27 can be realized through suitable shaping of the base plate 8 itself or with the help of additional elements, such as a sheet or a splint, wherein these elements must be removed for releasing the work eccentric 5 .
  • the locking device 27 comprises a sheet or a sheet clip 28 connected to the base plate 8 with an elongated hole or an inverted U-shaped bend open on one side. In the mounting position of the tensioning device 1 , the indexer 26 is supported for forming the locking device 27 with a firm contact fit on the sheet clip 28 .
  • the tensioning device 1 is seen in connection with a locking device 29 , in which the base plate 8 encloses a guide 30 , in which the indexer 31 of the work eccentric 5 is guided.
  • the guide 30 forms a receptacle 32 , which is designed for a pin 33 and with which an end position of the indexer 31 connected in one piece with the work eccentric 5 can be reached.
  • FIG. 16 shows the base plate 8 used in the tensioning device according to FIG. 15 in connection with the guide 30 as an individual part in perspective.
  • FIG. 17 a in the form of a perspective view, another embodiment for the shaping of a base plate 8 of a mounting-optimized tensioning device according to the invention is shown.
  • This base plate 8 is constructed as a sheet metal drawn part similar to embodiments described above.
  • the base plate forms several pivoting claws 34 , which are pivoted radially outwards within the scope of tensioning the base plate 8 on a flange surface carrying the tensioning device.
  • a pivot wing 35 is formed, which initially contacts the flange surface when the base plate 8 is set and which pivots the entire pivoting claw structure 34 about pivoting sections 36 , 37 in the course of further pressing the base plate 8 onto the flange surface.
  • the pivot sections 36 , 37 are shaped so that a slight, plastic deformation of the pivoting claws takes place within the scope the pivoting these pivoting claws 34 outwardly, so that the pivoting claws 34 no longer pivot back into the radially inwards pivoted position not shown here even after subsequent lifting. In this way the pivoting claws 34 are prevented from pivoting back inwards and thus cause an engaged state due to loosening of the tensioning of the base plate on the associated flange surface.
  • it becomes possible to bring the pivoting claws 34 as shown in FIG. 17 b , in engagement with a groove 22 constructed on the outer periphery of the work eccentric 5 or with some other engagement structure.
  • pivoting claws 34 it is also possible, as is visible from FIG. 18 , to shape the pivoting claws 34 so that these are pivoted inwardly within the scope of placing the base plate 8 on a flange surface not shown here in more detail and thus project out of corresponding catch geometries provided on the side of the work eccentric 5 and thus cause a release of the work eccentric 5 relative to the base plate 8 .
  • the attachment of the eccentric tensioning device 1 on the flange surface F only indicated here for an internal combustion engine BK takes place by means of an attachment screw 40 in three steps.
  • the tensioning device is set without special pressing force on the flange surface F, so that the projection 10 of the base plate 8 is inserted into the indexing recess U provided on the side of the internal combustion engine. In this way, the peripheral position of the base plate 8 is fixed.
  • the attachment screw 40 is inserted into the adjustment eccentric 2 .
  • the attachment screw 40 is tightened until the screw head of the attachment screw 40 is seated lightly and without special axial force on the end of the adjustment eccentric 2 .
  • the torsion spring 9 has not yet been loaded axially and thus the fixing device 12 has not yet been brought into a released position. After the attachment performed in this way for the tensioning device, the corresponding traction means can be inserted into the traction means drive of the internal combustion engine without using force.
  • the attachment screw 40 is charged with an increased tightening moment within the scope of the attachment step C.
  • the work eccentric 5 is forced together with the adjustment eccentric 2 axially towards the base plate 8 until the base surface of the adjustment eccentric 2 sits on the flange surface F.
  • the engagement element 15 formed on the base plate 8 emerges from a locking groove, as can be seen in this view, and thus releases the work eccentric 5 .
  • the work eccentric 5 now snaps into the tensioned position under the effect of the tensioning moment generated by the torsion spring 9 and in this way generates a transverse force applied to the traction means via the running disk 7 .
  • FIG. 20 another variant of a fixing mechanism automatically guided into a released state within the scope of the mounting process of the tensioning device is shown.
  • the generation of the released state is realized through axial displacement of the slide bearing bushing 4 .
  • the slide bearing bushing 4 is here provided with a conical section 4 a , which forces engagement claws 34 radially outwards for axial displacement indicated by the arrow symbol P 2 and brings these out of the engagement position shown here with corresponding counter structures of the work eccentric 5 .
  • the displacement of the slide bearing bushing 4 in the way shown here can be realized especially in that this is pushed axially under the effect of the rim 20 of the adjustment eccentric 2 .
  • FIG. 21 another variant of an automatically releasable fixing mechanism is shown.
  • the indexer 26 attached to the work eccentric is secured by a holding arm 41 .
  • This holding arm 41 is constructed in one piece with the base plate 8 .
  • a projecting length 42 of the holding arm 41 is charged with a pressure force, so that the entire arm 41 , as indicated by the arrow symbol P 3 , pivots upwards and thus releases the indexer 26 .
  • FIG. 22 another variant of a fixing device is shown.
  • the indexer 26 of the work eccentric 5 (not shown) is here secured by a hook section 43 of a spring elastic spring arm 44 pretensioned downwards.
  • the release of the fixing mechanism shown in this way can be realized in that the work eccentric 5 is pivoted by a small angular amount against its pretensioning direction, so that the hook structure shown here comes free from the indexer 26 and the entire spring arm 44 can tilt downwards. It is also possible to provide structures, through which the spring arm 44 can be forced downwards and in this way comes free from the indexer section 26 within the scope of the last tightening phase of an attachment screw.
  • the rolling bearing of the tensioning device is preferably constructed as a radial rolling bearing, which is comprised of an inner bearing ring and an outer bearing ring, as well as a plurality of cylinder bodies rolling between the bearing rings in groove-shaped raceways and held relative to each other by a bearing cage at a constant distance and which has axially on both sides of its cylinder bodies a seal, with which the intermediate space constructed as a grease storage area between the bearing rings is sealed, wherein this rolling bearing is distinguished in that this is constructed as a ball roller bearing, whose cylinder bodies are each constructed with two parallel side surfaces symmetrically flattened from a basic ball shape.
  • this ball rolling bearing offers an increased bearing capacity due to the higher number of cylinder bodies that can be mounted and due to the reduced installation space of the cylinder bodies together with an enlarged grease storage area.
  • the cylinder bodies constructed as ball rollers are preferably shaped so that these preferably have a width between their side surfaces of approximately 70% of the diameter of their basic ball shape and can be inserted at first axially “flat” into the radial rolling bearing through a distance between the concentric bearing rings having a height of approximately 80% of the diameter of the basic ball shape of the cylinder body and can each be pivoted through a corresponding rotation by about 90° in the raceways of the bearing rings.
  • the outer bearing ring here can form the running disk directly.
  • the inner bearing ring can be formed directly by the work eccentric.

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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)
US11/776,638 2006-12-21 2007-07-12 Eccentric tensioning device Abandoned US20080153642A1 (en)

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DE502007006275T DE502007006275D1 (de) 2006-12-21 2007-11-22 Exzenter-spannvorrichtung
AT07822800T ATE495391T1 (de) 2006-12-21 2007-11-22 Exzenter-spannvorrichtung
PCT/EP2007/062667 WO2008077696A1 (de) 2006-12-21 2007-11-22 Exzenter-spannvorrichtung
EP07822800A EP2115322B1 (de) 2006-12-21 2007-11-22 Exzenter-spannvorrichtung
US12/754,224 US7918755B2 (en) 2006-12-21 2010-04-05 Eccentric tensioning device

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DE102006061793.2 2006-12-21
DE102006061793 2006-12-21

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US12/754,224 Active US7918755B2 (en) 2006-12-21 2010-04-05 Eccentric tensioning device

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Cited By (18)

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US20060068957A1 (en) * 2004-09-29 2006-03-30 Stone Roger D Eccentric pivot arm tensioner
US20100145591A1 (en) * 2007-03-27 2010-06-10 Dayco Europe S.R.L. Drive for an internal combustion engine comprising an oil wet toothed belt and a tensioning shoe
US20100190594A1 (en) * 2007-06-05 2010-07-29 Adriano Rolando Pulley tensioner for an oil wet belt drive
US20100197432A1 (en) * 2007-07-05 2010-08-05 Schaeffler Kg Tensioning device for traction mechanism drives
US20110045929A1 (en) * 2006-12-04 2011-02-24 Adriano Rolando Pulley tensioner for a belt drive for use in contact with oil
US20110218066A1 (en) * 2007-06-05 2011-09-08 Adriano Rolando Pulley tensioner for an oil wet belt drive
ITTO20120631A1 (it) * 2012-07-17 2014-01-18 Lorett S P A Dispositivo tendicinghia meccanico.
WO2014089690A1 (en) * 2012-12-13 2014-06-19 Litens Automotive Partnership Tensioner and endless drive arrangement
FR3038028A1 (fr) * 2015-06-24 2016-12-30 Skf Ab Dispositif de galet tendeur
US20170138445A1 (en) * 2014-06-27 2017-05-18 Litens Automotive Partnership Endless drive arrangement with active idler
CN108443438A (zh) * 2018-05-16 2018-08-24 无锡永凯达齿轮有限公司 免调节张紧轮
CN110546405A (zh) * 2017-10-04 2019-12-06 利滕斯汽车合伙公司 具有改进的结构的正时皮带张紧器
US10753436B2 (en) * 2018-06-20 2020-08-25 Gates Corporation Tensioner
US11125305B2 (en) * 2019-06-20 2021-09-21 Gates Corporation Tensioner
CN113752001A (zh) * 2021-10-26 2021-12-07 苏州科米隆机电有限公司 一种自动装扭簧机构
WO2022056405A1 (en) * 2020-09-14 2022-03-17 Gates Corporation Tensioner adjuster
US11353092B2 (en) * 2017-04-28 2022-06-07 Litens Automotive Partnership Timing belt tensioner with improved construction
US12018753B2 (en) * 2021-10-29 2024-06-25 Gates Corporation Bearing pivot tensioner assembly

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FR2987411B1 (fr) * 2012-02-27 2014-09-12 Skf Ab Dispositif tendeur d'un element de traction et procede de montage d'un tel dispositif
DE102014202791A1 (de) * 2014-02-17 2015-08-20 Schaeffler Technologies AG & Co. KG Langlebiger Wälzkörperkäfig für Kugelrollenlager
FR3023891B1 (fr) * 2014-07-18 2018-01-05 Skf Ab Dispositif tendeur d'un organe de traction
DE102015222203B4 (de) * 2015-11-11 2020-03-12 Schaeffler Technologies AG & Co. KG Spielfreie Pendellagerung am Entkopplungsspanner
RU2619347C1 (ru) * 2016-03-18 2017-05-15 Денис Сергеевич Новиков Способ натяжения ремня привода механизма газораспределения двигателя автомобиля (варианты)
DE102017003300B3 (de) * 2017-04-05 2018-04-12 Mtu Friedrichshafen Gmbh Riemenspannvorrichtung
US11421561B2 (en) * 2017-07-05 2022-08-23 Gates Corporation Synchronous belt drive system
US11255414B2 (en) * 2019-05-15 2022-02-22 Gates Corporation Tensioner
DE102020120610A1 (de) * 2020-08-05 2022-02-10 Schaeffler Technologies AG & Co. KG Ölpumpenkettenspanner

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Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060068957A1 (en) * 2004-09-29 2006-03-30 Stone Roger D Eccentric pivot arm tensioner
US7637829B2 (en) * 2004-09-29 2009-12-29 The Gates Corporation Eccentric pivot arm tensioner
US20110045929A1 (en) * 2006-12-04 2011-02-24 Adriano Rolando Pulley tensioner for a belt drive for use in contact with oil
US8272983B2 (en) 2006-12-04 2012-09-25 Dayco Europe S.R.L. Pulley tensioner for a belt drive for use in contact with oil
US20100145591A1 (en) * 2007-03-27 2010-06-10 Dayco Europe S.R.L. Drive for an internal combustion engine comprising an oil wet toothed belt and a tensioning shoe
US8326514B2 (en) 2007-03-27 2012-12-04 Dayco Europe S.R.L. Drive for an internal combustion engine comprising an oil wet toothed belt and a tensioning shoe
US20100190594A1 (en) * 2007-06-05 2010-07-29 Adriano Rolando Pulley tensioner for an oil wet belt drive
US20110218066A1 (en) * 2007-06-05 2011-09-08 Adriano Rolando Pulley tensioner for an oil wet belt drive
US8292765B2 (en) * 2007-06-05 2012-10-23 Dayco Europe S.R.L. Pulley tensioner for an oil wet belt drive
US8641564B2 (en) 2007-06-05 2014-02-04 Dayco Europe S.R.L. Pulley tensioner for an oil wet belt drive
US20100197432A1 (en) * 2007-07-05 2010-08-05 Schaeffler Kg Tensioning device for traction mechanism drives
ITTO20120631A1 (it) * 2012-07-17 2014-01-18 Lorett S P A Dispositivo tendicinghia meccanico.
WO2014089690A1 (en) * 2012-12-13 2014-06-19 Litens Automotive Partnership Tensioner and endless drive arrangement
US20170138445A1 (en) * 2014-06-27 2017-05-18 Litens Automotive Partnership Endless drive arrangement with active idler
FR3038028A1 (fr) * 2015-06-24 2016-12-30 Skf Ab Dispositif de galet tendeur
US10215262B2 (en) 2015-06-24 2019-02-26 Aktiebolaget Skf Tension roller device
US11353092B2 (en) * 2017-04-28 2022-06-07 Litens Automotive Partnership Timing belt tensioner with improved construction
CN110546405A (zh) * 2017-10-04 2019-12-06 利滕斯汽车合伙公司 具有改进的结构的正时皮带张紧器
CN108443438A (zh) * 2018-05-16 2018-08-24 无锡永凯达齿轮有限公司 免调节张紧轮
US10753436B2 (en) * 2018-06-20 2020-08-25 Gates Corporation Tensioner
US11125305B2 (en) * 2019-06-20 2021-09-21 Gates Corporation Tensioner
CN114174697A (zh) * 2019-06-20 2022-03-11 盖茨公司 张紧器
WO2022056405A1 (en) * 2020-09-14 2022-03-17 Gates Corporation Tensioner adjuster
CN113752001A (zh) * 2021-10-26 2021-12-07 苏州科米隆机电有限公司 一种自动装扭簧机构
US12018753B2 (en) * 2021-10-29 2024-06-25 Gates Corporation Bearing pivot tensioner assembly

Also Published As

Publication number Publication date
ATE495391T1 (de) 2011-01-15
EP2115322B1 (de) 2011-01-12
US7918755B2 (en) 2011-04-05
DE202007005929U1 (de) 2007-12-13
EP2115322A1 (de) 2009-11-11
WO2008077696A1 (de) 2008-07-03
US20100190595A1 (en) 2010-07-29

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