[go: up one dir, main page]

WO2005106287A1 - Tensioning system for a belt drive - Google Patents

Tensioning system for a belt drive Download PDF

Info

Publication number
WO2005106287A1
WO2005106287A1 PCT/EP2005/002044 EP2005002044W WO2005106287A1 WO 2005106287 A1 WO2005106287 A1 WO 2005106287A1 EP 2005002044 W EP2005002044 W EP 2005002044W WO 2005106287 A1 WO2005106287 A1 WO 2005106287A1
Authority
WO
WIPO (PCT)
Prior art keywords
clamping system
hub
tensioning
crank
tensioning rollers
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2005/002044
Other languages
German (de)
French (fr)
Inventor
Michael Bogner
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.)
IHO Holding GmbH and Co KG
Original Assignee
INA Schaeffler KG
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 INA Schaeffler KG, Schaeffler KG filed Critical INA Schaeffler KG
Publication of WO2005106287A1 publication Critical patent/WO2005106287A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes or chains 
    • F16H7/10—Means for varying tension of belts, ropes or chains  by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes or chains  by adjusting the axis of a pulley of an idle pulley
    • F16H7/1254—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 
    • F16H2007/0863—Finally actuated members, e.g. constructional details thereof
    • F16H2007/0874—Two or more finally actuated members

Definitions

  • the invention relates to a tensioning system for at least two separate traction mechanism drives of an internal combustion engine, which comprises tensioning rollers arranged offset parallel to one another, which are positioned in unison at one end of an adjusting lever which can be pivoted about a pivot point and which interacts with a power means.
  • a generic tensioning system is known, with which traction means of two separate traction mechanism drives are pretensioned at the same time.
  • the construction of this tensioning system comprises two legs arranged almost at right angles to one another with a common pivot point, each of which is supported by a tensioning roller on traction means by two separate traction means drives.
  • a force means is assigned to each leg, in order to achieve sufficient pretensioning of the traction means.
  • JP 012 037 48 A Another tensioning system is known from JP 012 037 48 A, which is assigned to two separate traction mechanism drives of an internal combustion engine.
  • the tensioning system includes two legs, which are arranged on a common axis of rotation and are largely at right angles to one another, on the ends of which a tensioning roller is arranged, each of which is supported by a traction means. Sufficient pre-tensioning of the tensioning rollers is ensured by means of a common power means.
  • the known clamping systems consistently require a large amount of space, combined with a large number of individual components. Summary of the invention
  • the object of the present invention is to provide a tensioning system for several traction mechanism drives simultaneously, which at the same time implements an individual pretensioning of the traction means which is sufficient for the function, while requiring little installation space.
  • the tensioning system comprises tensioning rollers which are positioned eccentrically to one another and which are assigned to traction means of separate traction means drives, in particular axially offset.
  • the tensioning rollers are each assigned to a crank pin, the crank pins positioned eccentrically to one another being connected via a hub rotatably inserted in the adjusting lever.
  • This design principle enables the simultaneous re-tensioning of several traction mechanism drives with just one tensioning system.
  • the invention By adjusting or freely positioning the tensioning rollers relative to the actuating lever, the invention enables tolerance compensation or the compensation of tolerances in the independent traction mechanism drives.
  • the arrangement of the crank pins provides that they are connected to one another via a hub which is rotatably inserted in the adjusting lever.
  • the tensioning system according to the invention always ensures sufficient tensioning of the tensioning means for the function of the traction mechanism drive.
  • the resulting degree of freedom of the tensioning pulleys which are automatically aligned with respect to the adjusting lever, enables, for example, a pendulum movement of the two eccentrically mounted tensioning pulleys to compensate for expansion or wear of the traction mechanism in addition to component tolerances of the individual traction mechanism drives.
  • the arrangement of the eccentrically positioned tensioners forms a pendulum scale, which can ensure a balance of forces on the tensioning rollers.
  • the concept according to the invention also offers the possibility of realizing different pretensioning forces in the traction means of the separate traction means drives.
  • the tensioning system according to the invention is particularly suitable for starter generators driven by traction means.
  • a drive plane i. H. a traction mechanism drive can only be provided for starting operation of the starter generator.
  • an increased pretensioning force can be achieved in the start mode, in order to achieve a slip-free drive that shortens the start phase, i.e. ensures a quick start of the internal combustion engine.
  • the second traction mechanism drive is preferably intended for driving individual auxiliary units of the internal combustion engine.
  • the preload force is adapted to a slip-optimized drive of the units.
  • the tensioning system according to the invention is not limited to the use of starter generators, but can be used for all types of traction mechanism drives in order to inexpensively realize an effective prestressing of the traction mechanisms of several traction mechanism drives with only one tensioning system.
  • the tensioning system is preferably designed in such a way that its crank pins are joined in such a way that a maximum eccentric offset of the tensioning rollers is achieved. This measure enables a desired large mutual influence of the pretensioning of both traction means of the separate traction means drives via the tensioning system according to the invention.
  • a preferred embodiment of the invention provides for the individual crank pins to be connected to one another by means of a non-positive and / or positive connection.
  • An axially extending de screw connection in which, for example, a bore of a crank pin corresponds to a threaded bore of the further crank pin for receiving a hexagon screw.
  • the invention further includes a crank disk which comprises an integral construction of the crank pins including the hub.
  • the crank disk is preferably designed as a cast part.
  • the invention further includes providing the crank pins with lever arms that differ from one another and / or using the associated tensioning rollers with different diameters.
  • the cylindrical hub formed between the crank pins is rotatably mounted in a receptacle of the adjusting lever in the installed state.
  • the hub of the ring flanges is laterally limited.
  • Optimal adjustment of the hub, which connects the two crank pins to each other, is ensured by a slide bearing bush inserted into the setting lever.
  • a low-friction, wear-optimized bearing of the hub can thus be implemented.
  • the ribs are designed in such a way that they enable low-friction, axial guidance of the ring flanges from the hub.
  • the interaction of the ring flanges with the ribs of the slide bearing results in improved guidance and prevents disadvantageous tilting of the hub and the crank pin and tensioning rollers in connection therewith even with different traction forces.
  • the embodiment of the invention further provides for the actuating lever, the carrier part of the tensioning rollers, to be designed as a toggle lever.
  • the fulcrum of the actuating lever is preferably arranged between an articulation point of a power means and an axis of rotation of the hub for the crank pins of the tensioning rollers.
  • This structural design forms two legs, the tensioning rollers preferably being assigned to the longer leg and the power means to the shorter leg of the actuating lever.
  • the invention includes, for example, a rectilinear actuating lever in which the power means is articulated between the axis of rotation of the tensioning rollers and the pivot point of the actuating lever.
  • this construction enables a shortened control lever, combined with an increased stroke of the power means.
  • a hydraulically acting component is advantageously provided as a suitable power means for the clamping system according to the invention.
  • the power means preferably including a helical spring, exerts a sufficient force on the adjusting lever, the force translated by the adjusting lever being transmitted to the respective traction means of the traction means drives by means of the tensioning rollers.
  • a spring means designed as a helical spring is also suitable as the power means for the tensioning system.
  • the invention further includes combining the clamping system with a power means designed as a ball screw drive.
  • the preferably electrically controllable or actuatable ball screw drive, the actuator enables the pretensioning force of the traction means of both traction mechanism drives to be continuously adjusted.
  • This actuator which preferably interacts with an electronic control, a sensor system or an engine management system of the internal combustion engine, influences the pretensioning of the traction means as a function of operating parameters of the internal combustion engine.
  • the traction element pre-tension can be adapted, for example, to the respective operating mode of the internal combustion engine or the units to be driven. the, whereby this power means can be used in particular for traction mechanism drives that contain a starter generator.
  • Pneumatic or electro-hydraulic actuators which interact with the adjusting lever of the tensioning system are also suitable as alternative power means for the tensioning system according to the invention.
  • a power means it is also possible to provide the tensioning system according to the invention with a plurality of power means, preferably with two power means arranged in parallel, which interact directly with the adjusting lever, in order to generate an increased pre-tensioning force of the traction means.
  • the tensioning system according to the invention can also be used for more than two traction mechanism drives arranged offset from one another.
  • the adjusting lever it is advisable to provide the adjusting lever with three axially offset tensioning rollers, which cooperate with rotatably mounted crank pins and which are each assigned to separate traction means.
  • FIG. 1 shows a schematic representation of the drive layout of two separate traction mechanism drives, the traction mechanisms of which are prestressed via a tensioning system;
  • FIG 2 is a view of an inventive clamping system in connection with a power means
  • Figure 3 is a sectional view of the arrangement and attachment of the two tensioning rollers on an adjusting lever of the tensioning system
  • FIGS. 4a, 4b each have a crank pin which, when put together, form a structural unit for receiving the tensioning rollers
  • 5 shows a representation comparable to FIG. 3, in which, deviatingly, the crank pin and the hub are assembled in one piece;
  • FIG. 6 a tensioning system provided with two power means arranged in parallel.
  • FIG. 1 The drive layout of two separate, separately arranged traction mechanism drives of an internal combustion engine in a schematic construction is shown in FIG. 1.
  • a first traction mechanism drive 1a the internal combustion engine not shown in FIG. 1, is used to drive individual units, such as air conditioning compressor 2, power steering pump 3 and water pump 4
  • Traction means 5 connects pulleys of the aforementioned units and a pulley 7, which is connected to a crankshaft 5 of the internal combustion engine and from which the traction mechanism drive 1 a is simultaneously driven.
  • the traction means 5 of the traction mechanism drive 1 a is guided between the power steering pump 3 and the water pump 4 on a deflection roller 8.
  • the further traction drive 1b which e.g.
  • the traction means 10 of the traction mechanism drive 1b connects the further pulley 11 of the crankshaft 5, which is arranged axially offset to the pulley 7, with the starter generator 9, wherein a deflection roller 12 ensures an increased wrap angle of the traction means 10 on the starter generator 9.
  • a tensioning system 13a which has two tensioning rollers 14a, 14b arranged offset comprises, each associated with a traction device 5, 10.
  • the tensioning rollers 14a, 14b are arranged at the end on an adjusting lever 16 which can be pivoted about a pivot point 17 and which furthermore interacts with a force means 18 at the end opposite the tensioning rollers 14a, 14b.
  • the hydraulic power means 18 comprises a hydraulic cylinder with a hydraulic element and a spring means.
  • the power means 18 is stationary with a first articulation point 19a, but is articulated, for example, is attached to a housing of the internal combustion engine and is connected to the further articulation point 19b with the actuating lever 16.
  • FIG. 2 shows the clamping system 13a in a side view and explains its individual parts.
  • the adjusting lever 16, which is designed as a toggle lever, is connected to the shorter leg via the articulation point 19b with the power means 18.
  • the tensioning rollers 14a, 14b are arranged on the further, longer leg of the adjusting lever 16.
  • the control lever 16, which largely forms a triangular shape, is offset from the fulcrum 17 of the control lever 16 and is further provided with a tool holder 20.
  • the tool holder 20 intended for a separate tool enables a simplified assembly of the traction means 5, 10, in which the actuating lever 16 can be pivoted in the installed position, for example against a direction of force of the power means 18.
  • FIG. 3 shows a section of the tensioning system 13a in a sectional illustration 3-3 according to FIG. 2.
  • This illustration illustrates a parallel or axially offset arrangement of the tensioning rollers 14a, 14b, which in the installed state of the tensioning system 13a on the traction means 5, 10 the traction mechanism drives 1a, 1b are guided.
  • the correspondingly roller-mounted tensioning rollers 14a, 14b are each assigned to a crank pin 21, 22, which are connected to one another via a hub 23 designed as an axis of rotation. In the installed position, the hub 23 is rotatably inserted in a receptacle 24 in the form of a bore in the actuating lever 16.
  • the tensioning rollers 14a, 14b are fastened to the crank pins 21, 22 by means of screw connections.
  • a hexagon screw 25, 26 is provided, the screw head is located on the front Rolling bearings 29, 30 supports and which is screwed into a threaded bore 27, 28 of the crank pin 21, 22, respectively.
  • crank pins 21, 22 are arranged opposite one another in order to achieve an eccentric positioning. This results in a corresponding eccentricity "eß," e 2 ", which defines a distance between the axis of rotation of the hub 23 and the center axis 15a, 15b of the tensioning rollers 14a, 14b.
  • eß eccentricity
  • e 2 eccentricity
  • a slide bearing bush 32 is inserted into the receptacle 24 of the actuating lever 16.
  • the slide bearing bush 32 for example in two parts and comprising two half-shells, forms a circumferential, radially outwardly directed rim 33a, 33b on both ends.
  • the crank pins 21, 22 are axially guided via associated ring flanges 34, 35, the rims 33a, 33b simultaneously preventing the ring flanges 34, 35 from directly contacting the adjusting lever 16.
  • the diameters “di” and “d 2 ” of the tensioning rollers 14a, 14 b designed differently from each other.
  • FIGS. 4a and 4b each show the crank pins 21, 22 in an individual part drawing.
  • the separate illustration of the crank pins 21, 22 illustrates, for example, the offset arrangement of the threaded bores 27, 28 in the crank pin characterized by the eccentricity “ei” and “e 2 ” 21 which at the same time defines the offset of the tensioning rollers 14a, 14b in the installed position.
  • the crank pins 21, 22 are non-positively connected to one another by means of the hexagon screw 26, these components being supported via the end faces 36, 37.
  • crank pin 21 is provided with a cylindrical fit 40, 41.
  • the crank pin 21 is provided with a cylindrical guide pin 42, which is enclosed in the installed position by the slide bearing bush 32, the rims 33a, 33b of which cooperate with the ring flanges 34, 35 of the crank pin 21, 22.
  • FIG. 5 shows the clamping system 13b, which comprises many components that match the clamping system 13a shown in FIG.
  • the clamping system 13b comprises a one-piece crank disk 43, for example designed as a cast part, which includes two crank pins 44, 45, between which the hub is arranged.
  • the hub is inserted into the receptacle 24 of the actuating lever 16, the receptacle 24 being assigned a half-shell 46 which is fastened to the actuating lever 16 by means of a screw connection 47.
  • This type of attachment of the crank disk 43 simultaneously enables simple handling and assembly of the slide bearing bush 32.
  • crank pins 44, 45 have eccentricities that differ from one another between the axis of rotation 31 of the crank disk 43 and the central axes 15a, 15b of the tensioning rollers 14a, 14b.
  • the eccentricity " ⁇ i" of the crank pin 45 exceeds the eccentricity "e 2 " of the crank pin 44.
  • FIG. 6 shows the clamping system 13a, which, in contrast to FIG. 2, is provided with two force means 18 arranged in parallel.
  • the adjusting lever 16 forms a T-shaped end piece, the articulation point 19b, at which both power means 18 are articulatedly connected to the adjusting lever 16.

Landscapes

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

Abstract

The invention relates to a tensioning system (13a) for at least two separate belt drives (1a, 1b) of an internal combustion engine. The tensioning system has tension rollers (14a, 14b), which are arranged so that they are parallelly offset from one another and which are assigned to an adjusting lever (16). The tension rollers (14a, 14b), while being positioned eccentric to one another, are guided on the belts (5, 10) of the belt drives (1a, 1b).

Description

Spannsystem für einen Zugmitteltrieb Clamping system for a traction mechanism drive

Gebiet der ErfindungField of the Invention

Die Erfindung betrifft ein Spannsystem für zumindest zwei getrennte Zugmitteltriebe einer Brennkraftmaschine, das parallel versetzt zueinander angeordnete Spannrollen umfasst, die übereinstimmend an einem Ende eines Stellhebels positioniert sind, der um einen Drehpunkt schwenkbar ist und mit einem Kraft- mittel zusammenwirkt.The invention relates to a tensioning system for at least two separate traction mechanism drives of an internal combustion engine, which comprises tensioning rollers arranged offset parallel to one another, which are positioned in unison at one end of an adjusting lever which can be pivoted about a pivot point and which interacts with a power means.

Hintergrund der ErfindungBackground of the Invention

Aus der JP 052 48 508 A ist eine gattungsbildende Spannsystem bekannt, mit der gleichzeitig Zugmittel von zwei getrennten Zugmitteltrieben vorgespannt werden. Der Aufbau dieses Spannsystems umfasst zwei nahezu rechtwinklig zueinander angeordnete Schenkel mit einem gemeinsamen Drehpunkt, die jeweils über eine Spannrolle an Zugmitteln von zwei getrennten Zugmitteltrieben abgestützt sind. Jedem Schenkel ist ein Kraftmittel zugeordnet, zur Erzie- lung einer ausreichenden Vorspannung der Zugmittel.From JP 052 48 508 A a generic tensioning system is known, with which traction means of two separate traction mechanism drives are pretensioned at the same time. The construction of this tensioning system comprises two legs arranged almost at right angles to one another with a common pivot point, each of which is supported by a tensioning roller on traction means by two separate traction means drives. A force means is assigned to each leg, in order to achieve sufficient pretensioning of the traction means.

Aus der JP 012 037 48 A ist ein weiteres Spannsystem bekannt, das zwei getrennten Zugmitteltrieben einer Brennkraftmaschine zugeordnet ist. Das Spannsystem schließt zwei auf einer gemeinsamen Drehachse angeordnete weitestgehend rechtwinklig zueinander ausgerichtete Schenkel ein, an denen endseitig eine Spannrolle angeordnet ist, die jeweils einem Zugmittel abgestützt sind. Über ein gemeinsames Kraftmittel wird eine ausreichende Vorspannung der Spannrollen sichergestellt. Die bekannten Spannsysteme erfordern übereinstimmend einen hohen Bauraumbedarf, verbunden mit einer großen Anzahl von Einzelkomponenten. Zusammenfassung der ErfindungAnother tensioning system is known from JP 012 037 48 A, which is assigned to two separate traction mechanism drives of an internal combustion engine. The tensioning system includes two legs, which are arranged on a common axis of rotation and are largely at right angles to one another, on the ends of which a tensioning roller is arranged, each of which is supported by a traction means. Sufficient pre-tensioning of the tensioning rollers is ensured by means of a common power means. The known clamping systems consistently require a large amount of space, combined with a large number of individual components. Summary of the invention

Die Aufgabe der vorliegenden Erfindung besteht darin, ein Spannsystem für gleichzeitig mehrere Zugmitteltriebe zu schaffen, das bei geringem Bauraumbedarf, gleichzeitig eine individuelle, für die Funktion ausreichende Vorspan- nung der Zugmittel realisiert.The object of the present invention is to provide a tensioning system for several traction mechanism drives simultaneously, which at the same time implements an individual pretensioning of the traction means which is sufficient for the function, while requiring little installation space.

Diese Problemstellung wird durch die Merkmale von Anspruch 1 gelöst. Gemäß der Erfindung umfasst das Spannsystem zueinander exzentrisch positionierte Spannrollen, die Zugmittel von getrennten, insbesondere axial versetzt ange- ordneten Zugmitteltrieben zugeordnet sind. Dazu sind die Spannrollen jeweils einem Kurbelzapfen zugeordnet, wobei die exzentrisch zueinander positionierten Kurbelzapfen über eine drehbar in dem Stellhebel eingesetzte Nabe verbunden sind. Dieses Konstruktionsprinzip ermöglicht das gleichzeitige Nachspannen mehrerer Zugmitteltriebe mit nur einem Spannsystem. Durch die Ein- Stellung bzw. freie Positionierung der Spannrollen gegenüber dem Stellhebel ermöglicht die Erfindung einen Toleranzausgleich bzw. die Kompensation von Toleranzen in den unabhängigen Zugmitteltrieben. Die Anordnung der Kurbelzapfen sieht vor, dass diese über eine Nabe miteinander verbunden sind, welche drehbar in dem Stellhebel eingesetzt ist.This problem is solved by the features of claim 1. According to the invention, the tensioning system comprises tensioning rollers which are positioned eccentrically to one another and which are assigned to traction means of separate traction means drives, in particular axially offset. For this purpose, the tensioning rollers are each assigned to a crank pin, the crank pins positioned eccentrically to one another being connected via a hub rotatably inserted in the adjusting lever. This design principle enables the simultaneous re-tensioning of several traction mechanism drives with just one tensioning system. By adjusting or freely positioning the tensioning rollers relative to the actuating lever, the invention enables tolerance compensation or the compensation of tolerances in the independent traction mechanism drives. The arrangement of the crank pins provides that they are connected to one another via a hub which is rotatably inserted in the adjusting lever.

Im Vergleich zu bisher bekannten Spannsystemen gewährleistet das erfindungsgemäße Spannsystem stets eine für die Funktion des Zugmitteltriebs ausreichende Vorspannung des Zugmittels. Der sich dabei einstellende Freiheitsgrad der sich selbsttätig gegenüber dem Stellhebel ausrichtenden Spann- rollen, ermöglicht beispielsweise mittels einer Pendel bewegung der beiden exzentrisch gelagerten Spannrollen neben Bauteiltoleranzen der einzelnen Zugmitteltriebe weiterhin eine Dehnung oder den Verschleiß des Zugmittels zu kompensieren. Die Anordnung der exzentrisch positionierten Spannrollen bildet eine Pendelwaage, welche ein Kräftegleichgewicht an den Spannrollen sicherstellen kann. Abhängig von der Geometrie, der Ausgestaltung bzw. der Anordnung der Spannrollen zueinander bietet das erfindungsgemäße Konzept außerdem die Möglichkeit unterschiedliche Vorspannkräfte in den Zugmitteln der getrennten Zugmitteltriebe zu realisieren.In comparison to previously known tensioning systems, the tensioning system according to the invention always ensures sufficient tensioning of the tensioning means for the function of the traction mechanism drive. The resulting degree of freedom of the tensioning pulleys, which are automatically aligned with respect to the adjusting lever, enables, for example, a pendulum movement of the two eccentrically mounted tensioning pulleys to compensate for expansion or wear of the traction mechanism in addition to component tolerances of the individual traction mechanism drives. The arrangement of the eccentrically positioned tensioners forms a pendulum scale, which can ensure a balance of forces on the tensioning rollers. Depending on the geometry, the design or the arrangement of the tensioning rollers with respect to one another, the concept according to the invention also offers the possibility of realizing different pretensioning forces in the traction means of the separate traction means drives.

Das erfindungsgemäße Spannsystem bietet sich insbesondere für zugmittelgetriebene Startergeneratoren an. Beispielsweise kann dabei eine Triebebene, d. h. ein Zugmitteltrieb ausschließlich für den Startbetrieb des Startergenerators vorgesehen werden. Mit dieser Maßnahme ist in dem Startmodus eine erhöhte Vorspannkraft realisierbar, zur Erzielung eines schlupffreien Antriebs, der die Startphase verkürzt, d.h. einen schnellen Start der Brennkraftmaschine sicherstellt. Der zweite Zugmitteltrieb ist bevorzugt zum Antrieb einzelner Nebenaggregate der Brennkraftmaschine bestimmt ist. Zur Erzielung einer hohen Le- bensdauer des Zugmittels, wird die Vorspannkraft an einen schlupfoptimierten Antrieb der Aggregate angepasst. Dabei ist das erfindungsgemäße Spannsystem nicht auf den Einsatz von Startergeneratoren beschränkt, sondern kann für alle Arten von Zugmitteltrieben eingesetzt werden, um kostengünstig eine effektive Vorspannung der Zugmittel von mehreren Zugmitteltrieben mit nur ei- nem Spannsystem zu realisieren.The tensioning system according to the invention is particularly suitable for starter generators driven by traction means. For example, a drive plane, i. H. a traction mechanism drive can only be provided for starting operation of the starter generator. With this measure, an increased pretensioning force can be achieved in the start mode, in order to achieve a slip-free drive that shortens the start phase, i.e. ensures a quick start of the internal combustion engine. The second traction mechanism drive is preferably intended for driving individual auxiliary units of the internal combustion engine. In order to achieve a long lifespan for the traction device, the preload force is adapted to a slip-optimized drive of the units. The tensioning system according to the invention is not limited to the use of starter generators, but can be used for all types of traction mechanism drives in order to inexpensively realize an effective prestressing of the traction mechanisms of several traction mechanism drives with only one tensioning system.

Vorteilhafte Ausgestaltungen der Erfindung sind Gegenstand der abhängigen Ansprüche 2 bis 17.Advantageous embodiments of the invention are the subject of dependent claims 2 to 17.

Bevorzugt ist das Spannsystem so ausgebildet, dass deren Kurbelzapfen so zusammengefügt sind, dass sich ein maximaler exzentrischer Versatz der Spannrollen einstellt. Diese Maßnahme ermöglicht eine gewünschte große gegenseitige Einflußnahme der Vorspannung beider Zugmittel der getrennten Zugmitteltriebe über das erfindungsgemäße Spannsystem.The tensioning system is preferably designed in such a way that its crank pins are joined in such a way that a maximum eccentric offset of the tensioning rollers is achieved. This measure enables a desired large mutual influence of the pretensioning of both traction means of the separate traction means drives via the tensioning system according to the invention.

Eine bevorzugte Ausgestaltung der Erfindung sieht vor, die einzelnen Kurbelzapfen mittels einer kraftschlüssigen und/oder formschlüssigen Verbindung miteinander zu verbinden. Dazu eignet sich insbesondere eine axial verlaufen- de Verschraubung, bei der beispielsweise zur Aufnahme einer Sechskantschraube eine Bohrung eines Kurbelzapfens mit einer Gewindebohrung des weiteren Kurbelzapfens korrespondiert.A preferred embodiment of the invention provides for the individual crank pins to be connected to one another by means of a non-positive and / or positive connection. An axially extending de screw connection, in which, for example, a bore of a crank pin corresponds to a threaded bore of the further crank pin for receiving a hexagon screw.

Die Erfindung schließt als Alternative weiterhin eine Kurbelscheibe ein, die einen einstückigen Aufbau der Kurbelzapfen einschließlich der Nabe umfasst. Bevorzugt ist dazu die Kurbelscheibe als ein Gußteil gestaltet.As an alternative, the invention further includes a crank disk which comprises an integral construction of the crank pins including the hub. For this purpose, the crank disk is preferably designed as a cast part.

Ergänzend schließt die Erfindung weiterhin ein, die Kurbelzapfen mit vonein- ander abweichenden Hebelarmen zu versehen und/oder die zugehörigen Spannrollen mit unterschiedlichen Durchmessern einzusetzen. Diese Maßnahmen allein oder in Kombination ermöglichen ebenfalls eine unmittelbare Beeinflussung der Vorspannkraft beider Zugmittel der getrennten Zugmitteltriebe.In addition, the invention further includes providing the crank pins with lever arms that differ from one another and / or using the associated tensioning rollers with different diameters. These measures, alone or in combination, also enable the pretensioning force of both traction means of the separate traction mechanism drives to be influenced directly.

Die zylindrisch gestaltete, sich zwischen den Kurbelzapfen bildende Nabe ist im eingebauten Zustand in einer Aufnahme des Stellhebels drehbar gelagert. Zur Erzielung einer verbesserten Führung ist die Nabe von Ringflanschen seitlich begrenzt. Der Durchmesser der auch als Bord zu bezeichnenden Ringflan- sehe übertrifft dabei deutlich den Durchmesser des Führungszapfens der Nabe.The cylindrical hub formed between the crank pins is rotatably mounted in a receptacle of the adjusting lever in the installed state. To achieve improved guidance, the hub of the ring flanges is laterally limited. The diameter of the ring flange, which can also be referred to as a flange, clearly exceeds the diameter of the guide pin of the hub.

Eine optimale Verstellung der Nabe, die beide Kurbelzapfen miteinander verbindet, gewährleistet eine in die Aufnahme des Stellhebels eingesetzte Gleitla- gerbuchse. Damit ist eine reibungsarme, verschleißoptimierte Lagerung der Nabe realisierbar. Bevorzugt bietet es sich an, ein zwei Halbschalen umfassendes Gleitlager zu verwenden, wobei diese jeweils beidseitig einen Bord aufweisen. Die Gestaltung der Borde erfolgt so, dass diese eine reibungsarme, axiale Führung der Ringflansche von der Nabe ermöglichen. Das Zusammen- wirken der Ringflansche mit den Borden der Gleitlagerung bewirkt eine verbesserte Führung und verhindert ein nachteiliges Verkippen der Nabe und der damit in Verbindung Kurbelzapfen und Spannrollen selbst bei unterschiedlichen Zugmittelkräften. Die Ausgestaltung der Erfindung sieht weiterhin vor, den Stellhebel, das Trägerteil der Spannrollen, als ein Kniehebel zu gestalten. Der Drehpunkt des Stellhebels ist dabei bevorzugt zwischen einem Anlenkpunkt eines Kraftmittels und einer Drehachse der Nabe für die Kurbelzapfen der Spannrollen angeordnet. Dieser konstruktive Aufbau bildet zwei Schenkel, wobei bevorzugt die Spannrollen dem längeren Schenkel und das Kraftmittel dem kürzeren Schenkel des Stellhebels zugeordnet ist.Optimal adjustment of the hub, which connects the two crank pins to each other, is ensured by a slide bearing bush inserted into the setting lever. A low-friction, wear-optimized bearing of the hub can thus be implemented. It is preferable to use a plain bearing comprising two half-shells, each of which has a rim on both sides. The ribs are designed in such a way that they enable low-friction, axial guidance of the ring flanges from the hub. The interaction of the ring flanges with the ribs of the slide bearing results in improved guidance and prevents disadvantageous tilting of the hub and the crank pin and tensioning rollers in connection therewith even with different traction forces. The embodiment of the invention further provides for the actuating lever, the carrier part of the tensioning rollers, to be designed as a toggle lever. The fulcrum of the actuating lever is preferably arranged between an articulation point of a power means and an axis of rotation of the hub for the crank pins of the tensioning rollers. This structural design forms two legs, the tensioning rollers preferably being assigned to the longer leg and the power means to the shorter leg of the actuating lever.

Alternativ zu einem als Kniehebel ausgebildeten Stellhebel schließt die Erfindung beispielsweise einen geradlinig gestalteten Stellhebel ein, bei dem das Kraftmittel zwischen der Drehachse der Spannrollen und dem Drehpunkt des Stellhebels angelenkt ist. Dieser konstruktive Aufbau ermöglicht einerseits einen verkürzten Stellhebel, verbunden mit einem vergrößerten Hub des Kraft- mittels.As an alternative to an actuating lever designed as a toggle lever, the invention includes, for example, a rectilinear actuating lever in which the power means is articulated between the axis of rotation of the tensioning rollers and the pivot point of the actuating lever. On the one hand, this construction enables a shortened control lever, combined with an increased stroke of the power means.

Als ein geeignetes Kraftmittel für das erfindungsgemäße Spannsystem ist vorteilhaft ein hydraulisch wirkendes Bauteil vorgesehen. Das bevorzugt eine Schraubenfeder einschließende Kraftmittel übt eine ausreichende Kraft auf den Stellhebel aus, wobei die von dem Stellhebel übersetzte Kraft mittels der Spannrollen auf die jeweiligen Zugmittel der Zugmitteltriebe übertragen wird.A hydraulically acting component is advantageously provided as a suitable power means for the clamping system according to the invention. The power means, preferably including a helical spring, exerts a sufficient force on the adjusting lever, the force translated by the adjusting lever being transmitted to the respective traction means of the traction means drives by means of the tensioning rollers.

Als Kraftmittel für das Spannsystem eignet sich außerdem ein als Schraubenfeder ausgebildetes Federmittel. Die Erfindung schließt weiterhin ein das Spannsystem mit einem als Kugelgewindetrieb ausgelegten Kraftmittel zu kombinieren. Der bevorzugt elektrisch ansteuerbare bzw. betätigbare Kugelgewindetrieb, der Aktuator, ermöglicht eine stufenlose Verstellung der Vorspannkraft der Zugmittel beider Zugmitteltriebe. Dieser Aktuator, der vorzugsweise mit einer elektronischen Steuerung, einer Sensorik oder einem Motormanagement der Brennkraftmaschine zusammenwirkt, beeinflußt die Vorspannung der Zugmittel in Abhängigkeit von Betriebsparametern der Brennkraftmaschine. Die Zugmittelvorspannung kann beispielsweise an den jeweiligen Betriebsmodus der Brennkraftmaschine bzw. der anzutreibenden Aggregate angepasst wer- den, wodurch dieses Kraftmittel insbesondere für Zugmitteltriebe einsetzbar ist, die einen Startergenerator beinhalten.A spring means designed as a helical spring is also suitable as the power means for the tensioning system. The invention further includes combining the clamping system with a power means designed as a ball screw drive. The preferably electrically controllable or actuatable ball screw drive, the actuator, enables the pretensioning force of the traction means of both traction mechanism drives to be continuously adjusted. This actuator, which preferably interacts with an electronic control, a sensor system or an engine management system of the internal combustion engine, influences the pretensioning of the traction means as a function of operating parameters of the internal combustion engine. The traction element pre-tension can be adapted, for example, to the respective operating mode of the internal combustion engine or the units to be driven. the, whereby this power means can be used in particular for traction mechanism drives that contain a starter generator.

Als alternative Kraftmittel für das erfindungsgemäße Spannsystem eignen sich außerdem pneumatisch oder elektro-hydraulisch wirkende Aktuatoren, die mit dem Stellhebel des Spannsystems zusammenwirken. Anstelle eines Kraftmittels bietet es sich weiterhin an, das erfindungsgemäße Spannsystem mit mehreren, bevorzugt mit zwei parallel angeordneten Kraftmitteln zu versehen, die direkt mit dem Stellhebel zusammenwirken, zur Erzeugung einer erhöhten Vor- Spannkraft der Zugmittel.Pneumatic or electro-hydraulic actuators which interact with the adjusting lever of the tensioning system are also suitable as alternative power means for the tensioning system according to the invention. Instead of a power means, it is also possible to provide the tensioning system according to the invention with a plurality of power means, preferably with two power means arranged in parallel, which interact directly with the adjusting lever, in order to generate an increased pre-tensioning force of the traction means.

Das erfindungsgemäße Spannsystem ist weiterhin einsetzbar für mehr als zwei versetzt zueinander angeordnete Zugmitteltriebe. Beispielsweise bietet es sich dazu an, den Stellhebel mit drei axial versetzten, mit drehbar gelagerten Kur- beizapfen zusammenwirkenden Spannrollen zu versehen, die jeweils getrennten Zugmitteln zugeordnet sind.The tensioning system according to the invention can also be used for more than two traction mechanism drives arranged offset from one another. For example, it is advisable to provide the adjusting lever with three axially offset tensioning rollers, which cooperate with rotatably mounted crank pins and which are each assigned to separate traction means.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt. Es zeigen:Embodiments of the invention are shown in the drawings. Show it:

Figur 1 in einer schematischen Darstellung das Trieblayout von zwei getrennten Zugmitteltrieben, wobei deren Zugmittel über ein Spannsystem vorgespannt sind;1 shows a schematic representation of the drive layout of two separate traction mechanism drives, the traction mechanisms of which are prestressed via a tensioning system;

Figur 2 in einer Ansicht ein erfindungsgemäßes Spannsystem in Verbindung mit einem Kraftmittel; Figur 3 in einer Schnittansicht die Anordnung und Befestigung der zwei Spannrollen an einem Stellhebel des Spannsystems; Figuren 4a, 4b jeweils einen Kurbelzapfen, die zusammengefügt eine Baueinheit bilden zur Aufnahme der Spannrollen; Figur 5 eine der Figur 3 vergleichbare Darstellung, bei der abweichend die Kurbelzapfen und die Nabe einstückig zusammengefügt sind;Figure 2 is a view of an inventive clamping system in connection with a power means; Figure 3 is a sectional view of the arrangement and attachment of the two tensioning rollers on an adjusting lever of the tensioning system; FIGS. 4a, 4b each have a crank pin which, when put together, form a structural unit for receiving the tensioning rollers; 5 shows a representation comparable to FIG. 3, in which, deviatingly, the crank pin and the hub are assembled in one piece;

Figur 6 ein Spannsystem versehen mit zwei parallel ange- ordneten Kraftmitteln.FIG. 6 a tensioning system provided with two power means arranged in parallel.

Detaillierte Beschreibung der ZeichnungenDetailed description of the drawings

Das Trieblayout von zwei getrennten, separat angeordneten Zugmitteltrieben einer Brennkraftmaschine in einem schematischen Aufbau zeigt die Figur 1. Ein erster Zugmitteltrieb 1a, der in Figur 1 nicht abgebildeten Brennkraftmaschine dient zum Antrieb von einzelnen Aggregaten, wie Klimakompressor 2, Lenkhilfspumpe 3 und Wasserpumpe 4. Ein Zugmittel 5 verbindet dabei Riemenscheiben der zuvor genannten Aggregate sowie eine mit einer Kurbelwelle 5 der Brennkraftmaschine in Verbindung stehende Riemenscheibe 7, von der gleichzeitig der Zugmitteltrieb 1a angetrieben wird. Zur Erzielung eines vergrößerten Umschlingungswinkels ist das Zugmittel 5 des Zugmitteltriebes 1a zwischen der Lenkhilfspumpe 3 und der Wasserpumpe 4 an einer Umlenkrolle 8 geführt. Axial versetzt zu dem Zugmitteltrieb 1a verläuft der weitere Zugmittel- trieb 1b, der z.B. zum Antrieb eines Startergenerators 9 oder zum Antrieb anderer Aggregate bestimmt ist. Das Zugmittel 10 des Zugmitteltriebs 1b verbindet dabei die weitere axial zur Riemenscheibe 7 versetzt angeordnete Riemenscheibe 11 der Kurbelwelle 5 mit dem Startergenerator 9, wobei eine Umlenkrolle 12 einen vergrößerten Umschlingungswinkel des Zugmittels 10 an dem Startergenerator 9 sicherstellt.The drive layout of two separate, separately arranged traction mechanism drives of an internal combustion engine in a schematic construction is shown in FIG. 1. A first traction mechanism drive 1a, the internal combustion engine not shown in FIG. 1, is used to drive individual units, such as air conditioning compressor 2, power steering pump 3 and water pump 4 Traction means 5 connects pulleys of the aforementioned units and a pulley 7, which is connected to a crankshaft 5 of the internal combustion engine and from which the traction mechanism drive 1 a is simultaneously driven. In order to achieve an enlarged wrap angle, the traction means 5 of the traction mechanism drive 1 a is guided between the power steering pump 3 and the water pump 4 on a deflection roller 8. The further traction drive 1b, which e.g. is intended to drive a starter generator 9 or to drive other units. The traction means 10 of the traction mechanism drive 1b connects the further pulley 11 of the crankshaft 5, which is arranged axially offset to the pulley 7, with the starter generator 9, wherein a deflection roller 12 ensures an increased wrap angle of the traction means 10 on the starter generator 9.

Zur Erzielung von ausreichend vorgespannten Zugmitteln 5, 10 ist ein Spannsystem 13a vorgesehen, das zwei versetzt angeordnete Spannrollen 14a, 14b umfasst, die jeweils einem Zugmittel 5, 10 zugeordnet sind. Die Spannrollen 14a, 14b sind dabei endseitig an einem Stellhebel 16 angeordnet, der um einen Drehpunkt 17 schwenkbar ist und der weiterhin an dem von den Spannrollen 14a, 14b gegenüberliegenden Ende mit einem Kraftmittel 18 zusammen- wirkt. Das hydraulische Kraftmittel 18 umfasst einen Hydraulikzylinder mit einem Hydraulikelement sowie ein Federmittel. Das Kraftmittel 18 ist mit einem ersten Anlenkpunkt 19a ortsfest, jedoch gelenkig, beispielsweise an einem Gehäuse der Brennkraftmaschine befestigt ist und steht mit dem weiteren Anlenkpunkt 19b mit dem Stellhebel 16 in Verbindung.In order to achieve sufficiently pretensioned traction means 5, 10, a tensioning system 13a is provided which has two tensioning rollers 14a, 14b arranged offset comprises, each associated with a traction device 5, 10. The tensioning rollers 14a, 14b are arranged at the end on an adjusting lever 16 which can be pivoted about a pivot point 17 and which furthermore interacts with a force means 18 at the end opposite the tensioning rollers 14a, 14b. The hydraulic power means 18 comprises a hydraulic cylinder with a hydraulic element and a spring means. The power means 18 is stationary with a first articulation point 19a, but is articulated, for example, is attached to a housing of the internal combustion engine and is connected to the further articulation point 19b with the actuating lever 16.

Die Figur 2 zeigt das Spannsystem 13a in einer Seitenansicht und erläutert dessen Einzelteile. Der als Kniehebel ausgebildete Stellhebel 16 ist mit dem kürzeren Schenkel über den Anlenkpunkt 19b mit dem Kraftmittel 18 verbunden. An dem weiteren, längeren Schenkel des Stellhebels 16 sind die Spann- rollen 14a, 14b angeordnet. Der weitestgehend eine Dreieckform bildende Stellhebel 16 ist versetzt zu dem Drehpunkt 17 des Stellhebels 16 weiterhin mit einer Werkzeugaufnahme 20 versehen. Die für ein separates Werkzeug bestimmte Werkzeugaufnahme 20 ermöglicht eine vereinfachte Montage der Zugmittel 5, 10, in dem der Stellhebel 16 in der Einbaulage, beispielsweise entgegen einer Kraftrichtung des Kraftmittels 18 schwenkbar ist.FIG. 2 shows the clamping system 13a in a side view and explains its individual parts. The adjusting lever 16, which is designed as a toggle lever, is connected to the shorter leg via the articulation point 19b with the power means 18. The tensioning rollers 14a, 14b are arranged on the further, longer leg of the adjusting lever 16. The control lever 16, which largely forms a triangular shape, is offset from the fulcrum 17 of the control lever 16 and is further provided with a tool holder 20. The tool holder 20 intended for a separate tool enables a simplified assembly of the traction means 5, 10, in which the actuating lever 16 can be pivoted in the installed position, for example against a direction of force of the power means 18.

Die Figur 3 zeigt einen Ausschnitt des Spannsystems 13a in einer Schnittdarstellung 3-3 gemäß Figur 2. Diese Darstellung verdeutlicht eine parallele bzw. axial versetzte Anordnung der Spannrollen 14a, 14b, die im eingebauten Zu- stand des Spannsystems 13a an den Zugmitteln 5, 10 der Zugmitteltriebe 1a, 1b geführt sind. Die übereinstimmend wälzgelagerten Spannrollen 14a, 14b sind jeweils einem Kurbelzapfen 21 , 22 zugeordnet, die über eine als Drehachse ausgebildete Nabe 23 miteinander verbunden sind. In der Einbaulage ist die Nabe 23 in einer als Bohrung ausgebildeten Aufnahme 24 des Stellhebels 16 drehbar eingesetzt. Die Befestigung der Spannrollen 14a, 14b an den Kurbelzapfen 21, 22 erfolgt mittels Verschraubungen. Dazu ist jeweils eine Sechskantschraube 25, 26 vorgesehen, deren Schraubenkopf sich stirnseitig an dem Wälzlager 29, 30 abstützt und die jeweils in eine Gewindebohrung 27, 28 des Kurbelzapfens 21 , 22 verschraubt ist.FIG. 3 shows a section of the tensioning system 13a in a sectional illustration 3-3 according to FIG. 2. This illustration illustrates a parallel or axially offset arrangement of the tensioning rollers 14a, 14b, which in the installed state of the tensioning system 13a on the traction means 5, 10 the traction mechanism drives 1a, 1b are guided. The correspondingly roller-mounted tensioning rollers 14a, 14b are each assigned to a crank pin 21, 22, which are connected to one another via a hub 23 designed as an axis of rotation. In the installed position, the hub 23 is rotatably inserted in a receptacle 24 in the form of a bore in the actuating lever 16. The tensioning rollers 14a, 14b are fastened to the crank pins 21, 22 by means of screw connections. For this purpose, a hexagon screw 25, 26 is provided, the screw head is located on the front Rolling bearings 29, 30 supports and which is screwed into a threaded bore 27, 28 of the crank pin 21, 22, respectively.

Von einer Drehachse 31 der Nabe 23 ausgehend, sind die Kurbelzapfen 21, 22 zur Erzielung einer exzentrischen Positionierung zueinander entgegengesetzt angeordnet. Dabei stellt sich eine übereinstimmende Exzentrizität „eß , „e2" ein, die ein Abstandsmaß zwischen der Drehachse der Nabe 23 und den Mittenachse 15a, 15b der Spannrollen 14a, 14b definiert. Zur Erzielung einer leichtgängigen, reibungsarmen Stellbewegung der Nabe 23 in Verbindung mit den Kurbelzapfen 212, 22 sowie den Spannrollen 14a, 14b ist eine Gleitlagerbuchse 32 in die Aufnahme 24 des Stellhebels 16 eingesetzt. Die beispielsweise zweiteilig gestaltete, zwei Halbschalen umfassende Gleitlagerbuchse 32 bildet an beiden Stirnseiten einen umlaufenden, radial nach außen gerichteten Bord 33a, 33b. An den Borden 33a, 33b sind die Kurbelzapfen 21 , 22 über zugehö- rige Ringflansche 34, 35 axial geführt, wobei die Borde 33a, 33b gleichzeitig eine unmittelbare Anlage der Ringflansche 34, 35 an dem Stellhebel 16 vermeiden. Um eine Einflußnahme auf die Zugmittelkräfte der Zugmitteltriebe 1a, 1b ausüben zu können sind die Durchmesser „di" und „d2" der Spannrollen 14a, 14b abweichend zueinander ausgelegt.Starting from an axis of rotation 31 of the hub 23, the crank pins 21, 22 are arranged opposite one another in order to achieve an eccentric positioning. This results in a corresponding eccentricity "eß," e 2 ", which defines a distance between the axis of rotation of the hub 23 and the center axis 15a, 15b of the tensioning rollers 14a, 14b. To achieve a smooth, low-friction adjusting movement of the hub 23 in conjunction with the crank pin 212, 22 and the tensioning rollers 14a, 14b, a slide bearing bush 32 is inserted into the receptacle 24 of the actuating lever 16. The slide bearing bush 32, for example in two parts and comprising two half-shells, forms a circumferential, radially outwardly directed rim 33a, 33b on both ends. On the rims 33a, 33b, the crank pins 21, 22 are axially guided via associated ring flanges 34, 35, the rims 33a, 33b simultaneously preventing the ring flanges 34, 35 from directly contacting the adjusting lever 16. In order to influence the traction forces of the traction mechanism drives 1a, 1b are the diameters “di” and “d 2 ” of the tensioning rollers 14a, 14 b designed differently from each other.

Die Figuren 4a und 4b zeigen jeweils in einer Einzelteilzeichnung die Kurbelzapfen 21, 22. Die getrennte Darstellung der Kurbelzapfen 21, 22 verdeutlicht beispielsweise die durch die Exzentrizität „ei" und „e2" gekennzeichnete, versetzte Anordnung der Gewindebohrungen 27, 28 in dem Kurbelzapfen 21 die gleichzeitig den Versatz der Spannrollen 14a, 14b in der Einbaulage definiert. Mittels der Sechskantschraube 26 werden die Kurbelzapfen 21 , 22 kraftschlüssig miteinander verbunden, wobei sich diese Bauteile über die Stirnflächen 36, 37 abstützen. Zur Erzielung einer verdrehgesicherten Anlage der Kurbelzapfen 21 , 22 dient beispielsweise ein axial vorspringender Zapfen 38 an der Stirnflä- ehe 37 des Kurbelzapfens 22, oder eine exzentrische Vertiefung welcher oder welche in der Einbaulage formschlüssig in eine zugehörige Aussparung 39 des Kurbelzapfens 21 eingreift. Zur Aufnahme der Wälzlager 29, 30 ist jeder Kurbelzapfen 21 , 22 mit einem zylindrischen Passsitz 40, 41 versehen. Zur Bil- dung der Nabe 23 ist der Kurbelzapfen 21 mit einem zylindrischen Führungszapfen 42 versehen, der in der Einbaulage von der Gleitlagerbuchse 32 umschlossen wird, wobei deren Borde 33a, 33b mit den Ringflanschen 34, 35 der Kurbelzapfen 21, 22 zusammenwirken.FIGS. 4a and 4b each show the crank pins 21, 22 in an individual part drawing. The separate illustration of the crank pins 21, 22 illustrates, for example, the offset arrangement of the threaded bores 27, 28 in the crank pin characterized by the eccentricity “ei” and “e 2 ” 21 which at the same time defines the offset of the tensioning rollers 14a, 14b in the installed position. The crank pins 21, 22 are non-positively connected to one another by means of the hexagon screw 26, these components being supported via the end faces 36, 37. An axially projecting pin 38 on the end face 37 of the crank pin 22, or an eccentric recess which or which in the installed position engages in an associated recess 39 of the crank pin 21, is used, for example, to ensure that the crank pins 21, 22 are secured against rotation. To accommodate the roller bearings 29, 30, each crank pin 21, 22 is provided with a cylindrical fit 40, 41. For picture Extension of the hub 23, the crank pin 21 is provided with a cylindrical guide pin 42, which is enclosed in the installed position by the slide bearing bush 32, the rims 33a, 33b of which cooperate with the ring flanges 34, 35 of the crank pin 21, 22.

Die Figur 5 zeigt das Spannsystem 13b, das viele mit dem in Figur 3 abgebildeten Spannsystem 13a übereinstimmende Bauteile umfasst. Die nachfolgende Beschreibung beschränkt sich auf die Unterschiedsteile. Ansteile von zwei getrennten Kurbelzapfen umfasst das Spannsystem 13b eine einteilige, bei- spielsweise als ein Gussteil gestaltete Kurbelscheibe 43, die zwei Kurbelzapfen 44, 45 einschließt, zwischen denen die Nabe angeordnet ist. Zur Montage der Kurbelscheibe 43, wird die Nabe in die Aufnahme 24 des Stellhebels 16 eingesetzt, wobei der Aufnahme 24 eine Halbschale 46 zugeordnet ist, welche mittels einer Verschraubung 47 an dem Stellhebel 16 befestigt ist. Diese Befes- tigungsart der Kurbelscheibe 43 ermöglicht gleichzeitig eine einfache Handhabung und Montage der Gleitlagerbuchse 32. Die Kurbelzapfen 44, 45 weisen voneinander abweichende Exzentrizitäten zwischen der Drehachse 31 der Kurbelscheibe 43 und den Mittelachsen 15a, 15b der Spannrollen 14a, 14b auf. Die Exzentrizität „βi" von dem Kurbelzapfen 45 übertrifft dabei die Exzentrizität „e2" des Kurbelzapfens 44.FIG. 5 shows the clamping system 13b, which comprises many components that match the clamping system 13a shown in FIG. The following description is limited to the different parts. Instead of two separate crank pins, the clamping system 13b comprises a one-piece crank disk 43, for example designed as a cast part, which includes two crank pins 44, 45, between which the hub is arranged. To mount the crank disk 43, the hub is inserted into the receptacle 24 of the actuating lever 16, the receptacle 24 being assigned a half-shell 46 which is fastened to the actuating lever 16 by means of a screw connection 47. This type of attachment of the crank disk 43 simultaneously enables simple handling and assembly of the slide bearing bush 32. The crank pins 44, 45 have eccentricities that differ from one another between the axis of rotation 31 of the crank disk 43 and the central axes 15a, 15b of the tensioning rollers 14a, 14b. The eccentricity "βi" of the crank pin 45 exceeds the eccentricity "e 2 " of the crank pin 44.

Die Figur 6 zeigt das Spannsystem 13a, das abweichend zu Figur 2 mit zwei parallel angeordneten Kraftmitteln 18 versehen ist. Der Stellhebel 16 bildet dazu ein T-förmig gestaltetes Endstück, den Anlenkpunkt 19b, an dem beide Kraftmittel 18 gelenkig mit dem Stellhebel 16 verbunden sind. Bezugszahlen a Zugmitteltrieb 27 Gewindebohrungb Zugmitteltrieb 28 Gewindebohrung Klimakompressor 29 Wälzlager Lenkhilfspumpe 30 Wälzlager Wasserpumpe 31 Drehachse Zugmittel 32 Gleitlagerbuchse Kurbelwelle 33a Bord Riemenscheibe 33b Bord Umlenkrolle 34 Ringflansch Startergenerator 35 Ringflansch0 Zugmittel 36 Stirnfläche1 Riemenscheibe 37 Stirnfläche2 Umlenkrolle 38 Zapfen3a Spannsystem 39 Aussparung3b Spannsystem 40 Passsitz4a Spannrolle 41 Passsitz4b Spannrolle 42 Führungszapfen5a Mittelachse 43 Kurbelscheibe5b Mittelachse 44 Kurbelzapfen6 Stellhebel 45 Kurbelzapfen7 Drehpunkt 46 Halbschale8 Kraftmittel 47 Verschraubung9a Anlenkpunkt 48a Mittelachse9b Anlenkpunkt 48b Mittelachse0 Werkzeugaufnahme1 Kurbelzapfen2 Kurbelzapfen3 Nabe4 Aufnahme5 Sechskantschraube6 Gewindebohrung FIG. 6 shows the clamping system 13a, which, in contrast to FIG. 2, is provided with two force means 18 arranged in parallel. For this purpose, the adjusting lever 16 forms a T-shaped end piece, the articulation point 19b, at which both power means 18 are articulatedly connected to the adjusting lever 16. Reference numbers a traction drive 27 threaded hole b traction drive 28 threaded hole air conditioning compressor 29 roller bearing power steering pump 30 roller bearing water pump 31 rotary axis traction element 32 plain bearing bushing crankshaft 33a onboard pulley 33b onboard deflection roller 34 ring flange on starter generator 35 ring flange0 traction element 36 face surface1 pulley 37 end face3 tensioning pulley system 39 fitting seat 41 recessed seat 43 lock seat 40 fitting seat 41 out of 4 tensioning system 39 fitting seat 41 out of position 41 Tension pulley 42 Guide pin5a Center axis 43 Crank disc5b Center axis 44 Crank pin6 Adjusting lever 45 Crank pin7 Pivotal point 46 Half shell8 Power means 47 Screw connection9a Link point 48a Center axis9b Link point 48b Center axis0 Tool holder1 Crank pin2 Crank pin3 Hub4 Holder5 Hexagon bolt6 Tapped hole

Claims

Patentansprüche claims 1. Spannsystem für zumindest zwei getrennte Zugmitteltriebe (1a, 1b) einer Brennkraftmaschine, das parallel versetzt zueinander angeordnete Spannrollen (14a, 14b) umfasst, die übereinstimmend an einem Ende eines um einen Drehpunkt (17) schwenkbaren, mit einem Kraftmittel (18) zusammenwirken Stellhebels (16) angeordnet sind, dadurch gekennzeichnet, dass die Spannrollen (14a, 14b) jeweils mittels eines Kurbelzapfens (21, 22; 44, 45) zueinander exzentrisch positioniert zugeordnet sind, wobei die Kurbelzapfen (21 , 22; 44, 45) über eine drehbar in dem Stellhebel (16) eingesetzte Nabe (23) verbunden sind.1. Tensioning system for at least two separate traction mechanism drives (1a, 1b) of an internal combustion engine, which comprises tensioning rollers (14a, 14b) arranged offset parallel to one another, which cooperate with a power means (18) at one end of a pivotable about a pivot point (17) Adjusting lever (16) are arranged, characterized in that the tensioning rollers (14a, 14b) are each positioned eccentrically relative to one another by means of a crank pin (21, 22; 44, 45), the crank pins (21, 22; 44, 45) over a hub (23) rotatably inserted in the adjusting lever (16) is connected. 2. Spannsystem nach Anspruch 1, deren Kurbelzapfen (21 , 22; 44, 45) so zusammengefügt sind, dass sich ein maximaler exzentrischer Versatz der Spannrollen (14a, 14b) zueinander einstellt.2. Clamping system according to claim 1, the crank pin (21, 22; 44, 45) are assembled so that a maximum eccentric offset of the tensioning rollers (14a, 14b) to each other. 3. Spannsystem nach Anspruch 1 , wobei die Kurbelzapfen (21 , 22) mittels einer kraftschlüssigen und/oder formschlüssigen Verbindung zusammengefügt sind.3. Clamping system according to claim 1, wherein the crank pin (21, 22) are joined together by means of a non-positive and / or positive connection. 4. Spannsystem nach Anspruch 1 , bei dem die Kurbelzapfen (44, 45) in Verbindung mit der Nabe (23) einstückig miteinander verbunden sind zur Bildung einer Kurbelscheibe (43), die drehbar in dem Stellhebel (16) eingesetzt ist.4. Clamping system according to claim 1, wherein the crank pins (44, 45) in connection with the hub (23) are integrally connected to one another to form a crank disc (43) which is rotatably inserted in the adjusting lever (16). 5. Spannsystem nach Anspruch 1, wobei die Kurbelzapfen (21, 22; 44, 45) übereinstimmende oder voneinander abweichende Hebelarmlängen aufweisen, die ein Abstandsmaß zwischen einer Drehachse der Nabe (23) und einer Mittenachse (15a, 15b) der Spannrollen (14a, 14b) definieren, zur Erzielung einer übereinstimmenden oder abweichenden Exzentrizität „eϊ „e2".5. Clamping system according to claim 1, wherein the crank pins (21, 22; 44, 45) have matching or differing lever arm lengths which have a distance between a rotational axis of the hub (23) and a central axis (15a, 15b) of the tensioning rollers (14a, 14b) define "eϊ" e 2 "to achieve a matching or different eccentricity. 6. Spannsystem nach Anspruch 1, wobei die Spannrollen (14a, 14b) übereinstimmende oder zueinander abweichende Durchmesser „di", „02 aufweisen.6. Clamping system according to claim 1, wherein the tensioning rollers (14a, 14b) have identical or different diameters “di”, “02”. 7. Spannsystem nach Anspruch 1, deren zylindrisch gestaltete, zwischen den Kurbelzapfen (21 , 22; 44, 45) angeordnete Nabe (23) seit- lieh von Ringflanschen (34, 35) begrenzt, drehbar in einer Aufnahme (24) des Stellhebels (16) gelagert ist.7. Clamping system according to claim 1, whose cylindrically shaped hub (23) arranged between the crank pins (21, 22; 44, 45) is limited by ring flanges (34, 35), rotatable in a receptacle (24) of the adjusting lever ( 16) is stored. 8. Spannsystem nach Anspruch 6, wobei die Nabe (23) über eine Gleitlagerbuchse (32) in der Aufnahme (24) des Stellhebels (16) gelagert ist.8. Clamping system according to claim 6, wherein the hub (23) is mounted on a slide bearing bush (32) in the receptacle (24) of the adjusting lever (16). 9. Spannsystem nach Anspruch 1, wobei der Drehpunkt (17) um den der Stellhebel (16) schwenkbar ist, zwischen einem Anlenkpunkt (19b) des Kraftmittels (18) und der für die Nabe (23) bestimmten Aufnahme (24) vorgesehen ist.9. Clamping system according to claim 1, wherein the fulcrum (17) about which the adjusting lever (16) is pivotable is provided between a pivot point (19b) of the power means (18) and the receptacle (24) intended for the hub (23). 10. Spannsystem nach Anspruch 1, bei dem der als Kniehebel gestaltete Stellhebel (16) über einen ersten Schenkel mit dem Kraftmittel (18) verbunden ist und endseitig des zweiten Schenkels die Aufnahme (24) für die Nabe (23) vorgesehen ist.10. Clamping system according to claim 1, wherein the toggle lever (16) is connected via a first leg to the power means (18) and the end of the second leg is provided with the receptacle (24) for the hub (23). 11. Spannsystem nach Anspruch 1 , bei dem die Kurbelzapfen (21 , 22; 44, 45) gemeinsam mit den zugehörigen Spannrollen (14a, 14b) im Betriebszustand der Brennkraftmaschine selbsttätig verstellbar bzw. einstellbar sind. 11. Clamping system according to claim 1, wherein the crank pins (21, 22; 44, 45) together with the associated tensioning rollers (14a, 14b) are automatically adjustable or adjustable in the operating state of the internal combustion engine. 12. Spannsystem nach Anspruch 1, wobei das Kraftmittel (18) zwischen der für die Nabe (23) bestimmten Aufnahme (24) und dem Drehpunkt (17) des Stellhebels (16) angelenkt ist.12. Clamping system according to claim 1, wherein the force means (18) is articulated between the receptacle (24) intended for the hub (23) and the pivot point (17) of the actuating lever (16). 13. Spannsystem nach Anspruch 1, die als Kraftmittel (18) ein Hydraulikelement, einen Hydraulikzylinder einschließt, das mit einem Ende ortsfest über den Anlenkpunkt (19a) abgestützt ist und mit einem weiteren Anlenkpunkt (19b) mit dem Stellhebel (16) verbunden ist.13. Clamping system according to claim 1, which includes as the force means (18) a hydraulic element, a hydraulic cylinder, which is supported at one end in a stationary manner via the articulation point (19a) and is connected to the actuating lever (16) with a further articulation point (19b). 14. Spannsystem nach Anspruch 1, wobei als Kraftmittel (18) eine Feder, insbesondere eine Schraubenfeder eingesetzt ist.14. Clamping system according to claim 1, wherein a spring, in particular a helical spring, is used as the force means (18). 15. Spannsystem nach Anspruch 1, das einen elektrisch ansteuerbaren Aktuator, beispielsweise einen Kugelgewindetrieb als Kraftmittel (18) umfasst.15. Clamping system according to claim 1, which comprises an electrically controllable actuator, for example a ball screw as a power means (18). 16. Spannvorrichtung nach Anspruch 1, die zwei axial versetzt zueinander angeordnete, dem Stellhebel (16) zugeordnete Kraftmittel (18) einschließt.16. Clamping device according to claim 1, which includes two axially offset, the actuating lever (16) associated force means (18). 17. Spannsystem nach Anspruch 1, deren Aufbau drei axial zueinander versetzte Spannrollen umfasst, die jeweils unterschiedlichen Zugmitteltrieben zugeordnet sind. 17. Tensioning system according to claim 1, the structure of which comprises three axially offset tensioning rollers, each of which is assigned to different traction mechanism drives.
PCT/EP2005/002044 2004-04-01 2005-02-26 Tensioning system for a belt drive Ceased WO2005106287A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200410015952 DE102004015952A1 (en) 2004-04-01 2004-04-01 Clamping system for a traction drive
DE102004015952.1 2004-04-01

Publications (1)

Publication Number Publication Date
WO2005106287A1 true WO2005106287A1 (en) 2005-11-10

Family

ID=34961501

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2005/002044 Ceased WO2005106287A1 (en) 2004-04-01 2005-02-26 Tensioning system for a belt drive

Country Status (2)

Country Link
DE (1) DE102004015952A1 (en)
WO (1) WO2005106287A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1607657A3 (en) * 2004-06-19 2007-04-25 DaimlerChrysler AG Belt tensioning device and belt transmission with a belt tensioning device
US9341243B2 (en) 2012-03-29 2016-05-17 Litens Automotive Partnership Tensioner and endless drive arrangement
US11174921B2 (en) 2016-09-13 2021-11-16 Litens Automotive Partnership V tensioner and endless drive arrangement

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006031518A1 (en) * 2006-07-07 2008-01-10 Schaeffler Kg Tightening device for a belt drive on an internal combustion engine has a lever arm to rotate in bearings on a base plate by means of an arrangement of bearings with a shock-absorbing mechanism

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1072041B (en) * 1957-09-26 1959-12-24 Diipl.-Inig. Dr. techn. Hans List, Graz (Osterreich) Clamping device for several flexible traction devices running next to one another in parallel planes
US3216266A (en) * 1963-04-12 1965-11-09 Sunnen Joseph Change speed device
US3362243A (en) * 1967-02-14 1968-01-09 Hunt Foods And Ind Inc Engine cooling fan assembly
DE3021092A1 (en) * 1979-06-27 1981-12-10 Klöckner-Humboldt-Deutz AG, 5000 Köln Two-belt drive with jockey pulleys - has pulleys on separate parallel spindles turning on lever spindle
JPS63285228A (en) * 1987-05-15 1988-11-22 Honda Motor Co Ltd Belt tension adjusting device in engine
US4798564A (en) * 1987-09-08 1989-01-17 General Motors Corporation Double belt tensioner
JPH01203748A (en) 1988-02-05 1989-08-16 Iseki & Co Ltd Power transmission equipment in mobile work vehicles
JPH05248508A (en) 1992-03-06 1993-09-24 Kubota Corp Travel transmission structure of working vehicle
EP0565041A1 (en) * 1992-04-10 1993-10-13 FIAT AUTO S.p.A. A unit for driving two endless belts, for an internal combustion engine
JPH06174020A (en) * 1992-12-14 1994-06-21 Toyota Motor Corp Tension regulating device for twin-belt hanging belt

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4696661A (en) * 1986-12-22 1987-09-29 Weber Rehlander Forward-reverse belt transmission
DE3814525A1 (en) * 1987-05-05 1988-11-17 Volkswagen Ag Tensioning system
AUPM816594A0 (en) * 1994-09-15 1994-10-13 Garvin, Robert Arnold Glass shaping machine
DE10258240A1 (en) * 2002-12-13 2004-06-24 Ina-Schaeffler Kg Tensioning device for 2 belt or chain drives associated with IC engine using 2 tensioning rollers at ends or 2 pivoted tensioning arms mounted on engine housing

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1072041B (en) * 1957-09-26 1959-12-24 Diipl.-Inig. Dr. techn. Hans List, Graz (Osterreich) Clamping device for several flexible traction devices running next to one another in parallel planes
US3216266A (en) * 1963-04-12 1965-11-09 Sunnen Joseph Change speed device
US3362243A (en) * 1967-02-14 1968-01-09 Hunt Foods And Ind Inc Engine cooling fan assembly
DE3021092A1 (en) * 1979-06-27 1981-12-10 Klöckner-Humboldt-Deutz AG, 5000 Köln Two-belt drive with jockey pulleys - has pulleys on separate parallel spindles turning on lever spindle
JPS63285228A (en) * 1987-05-15 1988-11-22 Honda Motor Co Ltd Belt tension adjusting device in engine
US4798564A (en) * 1987-09-08 1989-01-17 General Motors Corporation Double belt tensioner
JPH01203748A (en) 1988-02-05 1989-08-16 Iseki & Co Ltd Power transmission equipment in mobile work vehicles
JPH05248508A (en) 1992-03-06 1993-09-24 Kubota Corp Travel transmission structure of working vehicle
EP0565041A1 (en) * 1992-04-10 1993-10-13 FIAT AUTO S.p.A. A unit for driving two endless belts, for an internal combustion engine
JPH06174020A (en) * 1992-12-14 1994-06-21 Toyota Motor Corp Tension regulating device for twin-belt hanging belt

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 013, no. 090 (M - 803) 2 March 1989 (1989-03-02) *
PATENT ABSTRACTS OF JAPAN vol. 018, no. 512 (M - 1679) 27 September 1994 (1994-09-27) *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1607657A3 (en) * 2004-06-19 2007-04-25 DaimlerChrysler AG Belt tensioning device and belt transmission with a belt tensioning device
US9341243B2 (en) 2012-03-29 2016-05-17 Litens Automotive Partnership Tensioner and endless drive arrangement
US11174921B2 (en) 2016-09-13 2021-11-16 Litens Automotive Partnership V tensioner and endless drive arrangement

Also Published As

Publication number Publication date
DE102004015952A1 (en) 2005-10-20

Similar Documents

Publication Publication Date Title
EP2612053B1 (en) Eccentric idler pulley
EP2778472B1 (en) Spring, belt tensioner and machine assembly
EP3601845B1 (en) Clamping device having adjustment mechanism and method for adjusting the torque of the clamping device
EP2627929B1 (en) Tensioning device for a traction mechanism drive of an internal combustion engine
DE10146612A1 (en) jig
EP3477154B1 (en) Clamping device
WO2005106287A1 (en) Tensioning system for a belt drive
WO2012143219A1 (en) Belt tensioner
EP1781913B1 (en) Centre of rotation support for an assembly
DE102004003327A1 (en) Variable valve lift device for internal combustion engine, has rotatable eccentric shaft having eccentrics contours positioned within circle formed by external diameter of bearings of eccentric shaft
EP1604130B1 (en) Power transmission belt drive
DE102011088213A1 (en) Instep arrangement for traction drive of accessory drive unit of internal combustion engine, has clamping unit to bias clamping elements through lever against traction unit, that is pivoted on associated end of lever
WO2005061927A1 (en) Tensioning system for a flexible drive
DE10359162A1 (en) jig
DE10328900A1 (en) Clamping system with a Drechstab as spring means
WO2001084014A1 (en) Tensing system with directed damping
DE102014012506B3 (en) Method for operating a multi-link crank drive for an internal combustion engine and corresponding multi-joint crank drive
EP1654479A1 (en) Clamping device
WO2007009564A1 (en) Chain tensioning device
DE10230188A1 (en) Clamping system for a traction mechanism drive
WO2005080770A2 (en) Flexible drive of an internal combustion engine
DE10159073A1 (en) Belt drive tensioner for a starter-generator of an IC engine, has locking system for locking tensioning element in an engine operating mode; locking system is directly connected to pivot arm, follows arm control movements
EP3748193A2 (en) Tensioning assembly with tensioning roller and device for adjusting a tensioning assembly
EP1688643B1 (en) Linear tensioning device
DE102004006907A1 (en) Tensioning system for power transmission drive in e.g. motor vehicle, includes tensioning part with opposite ends connected to lever arm and force transducer

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BW BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NA NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SM SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): GM KE LS MW MZ NA SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LT LU MC NL PL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG

121 Ep: the epo has been informed by wipo that ep was designated in this application
NENP Non-entry into the national phase

Ref country code: DE

WWW Wipo information: withdrawn in national office

Country of ref document: DE

122 Ep: pct application non-entry in european phase