WO2005052339A1 - Dispositif d'amortissement integre a un palier de pivotement - Google Patents

Dispositif d'amortissement integre a un palier de pivotement Download PDF

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Publication number
WO2005052339A1
WO2005052339A1 PCT/EP2004/010432 EP2004010432W WO2005052339A1 WO 2005052339 A1 WO2005052339 A1 WO 2005052339A1 EP 2004010432 W EP2004010432 W EP 2004010432W WO 2005052339 A1 WO2005052339 A1 WO 2005052339A1
Authority
WO
WIPO (PCT)
Prior art keywords
traction
drive
drive according
friction cone
cone
Prior art date
Application number
PCT/EP2004/010432
Other languages
German (de)
English (en)
Inventor
Ralph Painta
Michael Bogner
Herbert Graf
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 WO2005052339A1 publication Critical patent/WO2005052339A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/14—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of a driving or driven pulley
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0808—Extension 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
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1209—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means
    • F16H7/1218—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means of the dry friction type

Definitions

  • the invention relates to a traction mechanism drive of an internal combustion engine, which is intended for driving units.
  • a traction device in particular a belt, connects pulleys or belt pulleys of an output member and at least one drive member.
  • a pulley connected to the crankshaft of the internal combustion engine is preferably provided as the output member, from which units of the internal combustion engines are driven, the traction means connecting the pulleys of all the organs connected to the traction means drive.
  • a pivotably arranged drive element which is acted upon by a spring means, is provided in order to increase the pretension of the traction means.
  • the tensioning device is also assigned a damping device to compensate for vibrations of the traction mechanism drive.
  • a traction mechanism drive is preferably used to drive the individual units of an internal combustion engine, such as a water pump, air conditioning compressor, generator or power steering pump, in which a belt connects the individual belt pulleys of the units to be driven with the belt pulley arranged on the crankshaft of the internal combustion engine in a rotationally fixed manner.
  • the slip-free drive of this traction mechanism drive requires a tensioning device, which automatically over the entire life span even when the traction mechanism is elongating. duration of the internal combustion engine ensures sufficient tension of the traction means.
  • Known tensioning devices such as the device shown in DE 196 47 225 A1, comprise a force-loaded tensioning roller which is guided on the traction means.
  • the structure of this tensioning device is further provided with a base part arranged in a rotationally fixed manner, the axis of symmetry of which simultaneously forms the axis of rotation for the swivel arm, on the outside of which the tensioning roller is rotatably arranged.
  • a torsion spring is arranged between the base part and the swivel arm in order to achieve a non-positive support of the tensioning roller on the traction means.
  • a pressure cone is provided as a separate component, which, by means of a pressure spring arranged between the base part and the pressure cone, corresponds non-positively in an inner cone of the swivel arm designed with the outer contour of the pressure cone.
  • DE 100 57 818 A1 discloses a traction mechanism drive of an internal combustion engine designed as a two-disc drive.
  • the drive element of the traction mechanism drive is pivotably arranged and is supported on the internal combustion engine via a spring means, in order to achieve a sufficient pre-tensioning of the traction mechanism, which ensures a slip-free traction mechanism drive.
  • This known device provides a spring-damper unit as spring means in order to achieve a traction mechanism drive that is as vibration-free as possible. Summary of the invention
  • a pivot bearing which also functions as the tensioning device and is combined with the damping device is assigned to the pivotable unit.
  • This structure enables further optimization of the component and installation space, since a simple spring means without a damping device, for example a spring means designed as a coil spring, can be assigned to the pivoting unit provided with the pivot bearing according to the invention.
  • the invention provides as a damping device a force-actuated clamping element including two friction cones. When installed, the force-applied friction cones enable effective damping of undesired adjusting movements of the pivotably arranged drive element. In particular, the vibrations caused by the combustion process of the internal combustion engine and introduced into the traction mechanism drive as rotational non-uniformity can be damped.
  • the operation of the damping device according to the invention is based on the principle of a clamping element connection, in which an axial force spreads the friction cones connected via conical contact surfaces radially inwards and outwards, as a result of which relative movements between an inner component and an outer component on which the respective friction cones are supported are damped.
  • the axially acting spring means integrated in the pivot bearing is advantageously supported on an inner friction cone and, in cooperation with the outer friction cone, generates a desired spreading force in the radial direction.
  • the friction cones are supported by a contact surface running in a cone angle, the cone angle being designed with regard to optimal damping on the one hand and to avoid a self-locking effect on the other.
  • the axial force acting on the clamping element is dimensioned in such a way that a frictional connection is avoided, which brings about a torsionally rigid connection between the fixedly arranged component and the pivotable component of the rotary bearing. Due to the integrated solution, in which the pivot bearing is combined with the damping device, the invention reduces the required installation space and at the same time optimizes the scope of components.
  • the invention advantageously replaces the spring damping systems previously used for such tensioning systems or tensioning devices with a pure spring element, since the required damping of the traction mechanism drive takes place according to the invention with the tensioning element integrated in the pivot bearing of the pivotable drive element.
  • the friction cones are preferably designed such that they effectively avoid a disadvantageous self-locking effect.
  • a cone angle of ⁇ ⁇ 20 ° is provided. This angular value ensures, on the one hand, a desired damping of positioning movements of the pivotable drive element and, on the other hand, a permanent, wear-free relative movement between the friction cones.
  • the cone angle is designed in particular depending on the material of the friction cones and the required friction forces of the clamping element.
  • the invention includes, as a damping device, differently designed or arranged friction cones of the tensioning elements.
  • the relative movement can take place directly between the contact surfaces of the friction cones.
  • the relative movement between the outer surface of the outer friction cone and the associated support surface of the rotary bearing can be provided.
  • the invention further includes an arrangement in which there is a relative movement between the inner diameter of the inner friction cone and the associated support surface.
  • the invention includes, for example, a positionally fixed arrangement of the friction cones on the components of the rotary bearing on which the friction cones are supported. This structure ensures a preferred relative movement exclusively between the contact surfaces of the friction cones of the clamping element.
  • the configuration of the tensioning element comprises two cones of opposite conical design.
  • An outer friction cone has a cylindrical outer surface and a conical contact surface on the inside.
  • the associated internal friction cone forms a cylindrical inside and a conical contact surface on the outside.
  • the tensioning element is inserted in the installed state in a circular annular space of the rotary bearing, which is delimited radially on the outside by a bore of a torsionally rigid, stationary housing and radially on the inside by a bolt directly connected to the pivotable drive element.
  • a further advantageous embodiment of the invention provides for two axially spaced clamping elements to be arranged in the rotary bearing, between which a compression spring exerting axial forces on the clamping elements is arranged as spring means.
  • This structure advantageously provides two clamping elements arranged on the outside of the rotary bearing, which has an advantageous effect on the installation position of the pivotably arranged drive element. Due to the symmetrical arrangement of the clamping elements in the pivot bearing, there is no need for a further rolling bearing or sliding bearing in the annular space of the pivot bearing, since the double clamping element arrangement ensures a defined installation position of the swiveling drive shaft.
  • the invention provides for an installation position that simplifies assembly. For this purpose, it is advisable to insert the tensioning elements into the annular space of the pivot bearing in such a way that the associated compression spring is supported on the front on the inner friction cones.
  • each external friction cone of the tensioning elements is also advantageously supported axially on a cover, which further defines the installation position of the outer component of the rotary bearing.
  • the cover is fixed in position in a groove of the bolt.
  • the invention further includes sealing the annular space in the pivot bearing, which is intended to accommodate the tensioning elements according to the invention.
  • An elastic seal for example an O-ring, is particularly suitable for this purpose, which is inserted in a form-fitting manner in an end receptacle of the outer component of the rotary bearing and fills it in a sealing manner.
  • the receptacle which is open radially inwards and is intended for the seal, is delimited at the end by the cover on which the external friction cone and the external component are fixed in position. This effectively prevents contamination from entering the annular space of the rotary bearing.
  • a further advantageous embodiment of the invention provides for a rotary bearing to be implemented which, in addition to a tensioning element, also has a damping device and a spring means.
  • This measure makes it possible to dispense with a spring means which is used separately from the rotary bearing, which advantageously reduces the required component scope of the tensioning device and simplifies assembly.
  • this spring means integrated in the pivot bearing it is advisable to use a torsion spring which is attached with a spring end to the stationary component of the pivot bearing and is fixed with the further spring end to the pivotable component of the pivot bearing.
  • a swiveling unit that performs the function of the tensioning device, it makes sense to provide a starter generator. When starting, this unit has the task of driving the internal combustion engine. Immediately after the internal combustion engine has started, that is to say, normal operation or generator operation of the starter generator is established, in which the engine is driven by the internal combustion engine.
  • Figure 1 is a schematic representation of a traction drive comprising two pulleys
  • Figure 2 is a side view of a pivotably arranged drive member, which simultaneously forms the function of a tensioning device for a traction mechanism drive;
  • Figure 3 is an enlarged view of the pivot bearing of the pivotally arranged drive member;
  • Figure 4 shows an alternative to Figure 3 rotary bearing for a pivotable drive member.
  • FIG. 1 shows a traction mechanism drive 1, which includes a traction mechanism 2, in particular a belt.
  • the traction means 2 connects a first pulley 3 assigned to an output element 4 to a second pulley 6 assigned to a drive element 5.
  • a pulley 3 connected to a crankshaft of an internal combustion engine 7 is provided as the output element 4.
  • the drive member 5 forms a pivotally arranged unit of the Internal combustion engine 7, preferably a starter generator.
  • the drive member 5 is pivotally arranged via a pivot bearing 8 so that it supports the traction means 2, supported by the weight of the drive member, to achieve a slip-free drive.
  • a spring means 9 inserted between the internal combustion engine 7 and the drive element 5 reinforces the pretensioning of the traction means 2.
  • FIG. 2 illustrates the fastening of the drive member 5 and in particular the design of the rotary bearing 8.
  • the drive member 5 as a starter generator is connected to the internal combustion engine 7 shown in FIG. 1 by means of a separate lever 10.
  • the end of the lever 10 has a bore 11 which is intended for a bolt 12.
  • the bolt 12 is fixed in position in the fastening slugs 13a, 13b of the drive element 5.
  • a compression spring 39 is inserted between the tensioning elements 15a, 15b, which in the installed state causes the tensioning elements 15a, 15b, which are constructed in two parts and form a damping device 16, to spread.
  • the damping device 16 has the task of effectively dampening a vibration excitation of the traction mechanism drive 1, which is triggered in particular by the rotational irregularity of the internal combustion engine 7 and leads to vibrations of the traction mechanism 2, i. H. to avoid uncontrolled adjusting movements or pivoting movements of the drive member 5 around the axis of rotation of the rotary bearing 8.
  • the spring means 9 is rotatably supported with a first articulation point 17 on a holding bracket 18, the holding bracket 18 being fastened to the internal combustion engine 7 in the installed state.
  • the spring means 9 is connected to the drive element 5 with a second articulation point 19.
  • FIG. 3 shows the detailed structure of the rotary bearing 8, including all individual parts of the damping device 16.
  • Each clamping element 15a, 15b is composed of an inner friction cone 20, to which an outer friction cone 21 is assigned.
  • the internal friction cone 20, which is cylindrical on the inside, is supported in the installed state on the lateral surface of the bolt 12 serving as a support surface 22.
  • the conically shaped outer surface of the inner friction cone 20 forms, together with the inner friction cone 21, which is conical on the inside.
  • the outer cylindrical cone 21 on the outside is supported in the installed position on a support surface 24 of the bore 11 in the lever 10.
  • a spreading force is exerted on the tensioning elements 15a, 15b by means of the compression spring 39, which is supported at the end on the inner friction cones 20.
  • the damping device 16 the construction of which comprises two axially spaced clamping elements 15a, 15b, each comprising an inner friction cone 20 and an outer synchronizing ring 21, which are designed as closed rings and are supported by a conical contact surface 23, are displaced into one another by the force application of the compression spring 39 and deformed to a limited extent.
  • all friction cones of the tensioning element 15a, 15b are provided with a cone angle " ⁇ -i", “ ⁇ 2 " of ⁇ 20 °.
  • the design of the cone angle "CH”, “ ⁇ 2 " can be influenced by the choice of the material from which the components of the clamping element 15a, 15b are made.
  • the individual friction cones are fixed to the respective support surfaces 22, 24.
  • the inner friction cone 20 is provided with a radially inwardly directed lug 25 which engages in a form-fitting manner in a corresponding longitudinal groove or recess 26 in the bolt 12.
  • the outer friction cone 21 has a radially outwardly directed nose 27 which interacts with a longitudinal groove or recess 28 in the lever 9 in the region of the bore 11.
  • the preferably slotted, radially biased cover 29 are positively inserted in a groove 30 of the bolt 12 to achieve a positionally fixed arrangement.
  • a seal 31 is provided on both sides of the rotary bearing 8, which is inserted in each case in an end recess 32 of the lever 10. In the installed position, the seal 31 is non-positively and thus sealingly supported on the front side of the cover 29.
  • FIG. 4 shows the rotary bearing 8, which on the one hand has a damping device 16 with a tensioning element 15a, corresponding to the structure shown in FIG. 3.
  • the spring means 33 designed as a torsion spring is integrated into the annular space 14 and exerts a force component on the drive element 5 in order to increase the pretensioning of the traction means 2.
  • This structure eliminates the need for a separate spring means 9, as shown in FIG. 1.
  • the spring means 33 engages in a form-fitting manner with a spring end 34 which is bent radially outward into a longitudinal groove 35 of the lever 10. In the installed position, the further spring end 36 engages in a longitudinal groove 37 of the bolt 12.
  • the spring means 33 is pretensioned so that, transferred to the representation of the traction mechanism drive 1 according to FIG. 1, it triggers a counterclockwise force component on the drive element 5.
  • a sliding bearing 38 is also inserted in the annular space 14, in a section axially delimited by the spring means 33 and the cover 29. In conjunction with the tensioning element 15a, the slide bearing 38 has the task of ensuring that the drive element 5 is aligned with the lever 10 as free of play as possible.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

L'invention concerne un entraînement à élément de traction (1) d'un moteur à combustion interne (7) comportant un organe d'entraînement pivotant (5) servant de dispositif de serrage. Au moins un dispositif d'amortissement (16) conçu en tant qu'élément de serrage (15a, 15b) est intégré au palier de pivotement (8) de l'organe d'entraînement dans un espace annulaire (14).
PCT/EP2004/010432 2003-10-31 2004-09-17 Dispositif d'amortissement integre a un palier de pivotement WO2005052339A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10350939.9 2003-10-31
DE2003150939 DE10350939A1 (de) 2003-10-31 2003-10-31 In einem Drehlager integrierte Dämpfungseinrichtung

Publications (1)

Publication Number Publication Date
WO2005052339A1 true WO2005052339A1 (fr) 2005-06-09

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PCT/EP2004/010432 WO2005052339A1 (fr) 2003-10-31 2004-09-17 Dispositif d'amortissement integre a un palier de pivotement

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DE (1) DE10350939A1 (fr)
WO (1) WO2005052339A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006053623A1 (fr) * 2004-11-17 2006-05-26 Schaeffler Kg Dispositif de fixation d'un ensemble d'une transmission a courroie d'un moteur a combustion interne
CN110219952A (zh) * 2018-03-02 2019-09-10 舍弗勒技术股份两合公司 传动带张紧装置及带式传动机构

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005056417A1 (de) * 2005-11-26 2007-05-31 Schaeffler Kg Spannvorrichtung zum Spannen eines Antriebsriemens beziehungsweise einer Antriebskette
CN108843741B (zh) * 2018-09-08 2024-02-13 江阴市华方新能源高科设备有限公司 一种带阻尼缓冲输出回转式减速器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4300178C1 (de) * 1993-01-07 1994-04-28 Muhr & Bender Riemenspannvorrichtung
DE19647225A1 (de) * 1995-11-25 1997-05-28 Volkswagen Ag Riemenspannvorrichtung
US6360712B1 (en) * 2000-05-01 2002-03-26 Daimlerchrysler Corporation Self-aligning and locking mount for engine accessory
DE10057818A1 (de) * 2000-11-21 2002-05-23 Ina Schaeffler Kg Zugmitteltrieb für einen Startergenerator

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US4698049A (en) * 1986-04-11 1987-10-06 Litens Automotive Inc. Belt tensioner with frustoconical pivot bearing
DE4010928C2 (de) * 1990-04-04 1998-11-05 Litens Automotive Gmbh Automatischer Riemenspanner
DE19540706A1 (de) * 1995-11-02 1997-05-07 Schaeffler Waelzlager Kg Spanneinrichtung für Zugmittel mit Konus-Gleitlager
DE29721555U1 (de) * 1997-12-08 1999-04-08 Sachsenring Entwicklungsgesell Spannvorrichtung
DE19839888A1 (de) * 1998-09-02 2000-03-09 Schenck Ag Carl Schwingungsdämpfer auf Basis elektrorheologischer/magnetorheologischer Flüssigkeiten für Riemenspannsysteme
DE10146612B4 (de) * 2001-09-21 2016-09-01 Schaeffler Technologies AG & Co. KG Spannvorrichtung
DE10152364A1 (de) * 2001-10-24 2003-05-08 Ina Schaeffler Kg Spannvorrichtung
DE10159072A1 (de) * 2001-12-01 2003-06-18 Ina Schaeffler Kg Spannvorrichtung für einen Zugmitteltrieb

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4300178C1 (de) * 1993-01-07 1994-04-28 Muhr & Bender Riemenspannvorrichtung
DE19647225A1 (de) * 1995-11-25 1997-05-28 Volkswagen Ag Riemenspannvorrichtung
US6360712B1 (en) * 2000-05-01 2002-03-26 Daimlerchrysler Corporation Self-aligning and locking mount for engine accessory
DE10057818A1 (de) * 2000-11-21 2002-05-23 Ina Schaeffler Kg Zugmitteltrieb für einen Startergenerator

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006053623A1 (fr) * 2004-11-17 2006-05-26 Schaeffler Kg Dispositif de fixation d'un ensemble d'une transmission a courroie d'un moteur a combustion interne
CN110219952A (zh) * 2018-03-02 2019-09-10 舍弗勒技术股份两合公司 传动带张紧装置及带式传动机构

Also Published As

Publication number Publication date
DE10350939A1 (de) 2005-05-25

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