WO2022179664A1 - Belt tensioner - Google Patents

Belt tensioner Download PDF

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Publication number
WO2022179664A1
WO2022179664A1 PCT/DE2022/100142 DE2022100142W WO2022179664A1 WO 2022179664 A1 WO2022179664 A1 WO 2022179664A1 DE 2022100142 W DE2022100142 W DE 2022100142W WO 2022179664 A1 WO2022179664 A1 WO 2022179664A1
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WO
WIPO (PCT)
Prior art keywords
rotation
axis
tensioning
base
spring
Prior art date
Application number
PCT/DE2022/100142
Other languages
German (de)
French (fr)
Inventor
Susanne MÖNIUS
Markus WEISSHEIMER
Christian Groh
Original Assignee
Schaeffler Technologies AG & Co. KG
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Publication of WO2022179664A1 publication Critical patent/WO2022179664A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1254—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means
    • F16H7/1281—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means where the axis of the pulley moves along a substantially circular path
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0806—Compression coil springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0863—Finally actuated members, e.g. constructional details thereof
    • F16H2007/0865—Pulleys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0863—Finally actuated members, e.g. constructional details thereof
    • F16H2007/0874—Two or more finally actuated members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0889—Path of movement of the finally actuated member
    • F16H2007/0893—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
    • F16H2007/0889—Path of movement of the finally actuated member
    • F16H2007/0897—External to internal direction

Definitions

  • the invention relates to a belt tensioner for a starter generator belt drive of an internal combustion engine, comprising:
  • Such a belt tensioner is known from the respective generic US 2019/0 285 149 A1, US 9 759 293 B2 and DE 103 48 878 A1.
  • the kinematic design of these so-called two-arm clamps is often based on the goal that the spring force acting on the tension rollers - independent of the mutual deflection of the clamping levers and consequently independent of the spring deflection of the helical compression spring - is as unchangeable as possible and ideally constant. In principle, this goal can be achieved with a comparatively small spring rate. Another goal is to ensure that the belt tensioner operates with as little vibration as possible. In principle, this further goal can be achieved with a comparatively high spring natural frequency and consequently high spring rate. Both goals are in conflict with each other.
  • US 2004/0 043 854 A1 discloses a belt tensioner for an electric vehicle steering system.
  • the present invention is based on the object of defusing this conflict of objectives.
  • the helical compression spring should have a spring rate c>20 N/mm, with the following relationships applying to its longitudinal natural frequency f e and its transverse natural frequency f q : i) 220 Hz ⁇ f e ⁇ 260 Hz ii) 190 Hz ⁇ f q ⁇ 240 Hz iii) 1 ⁇ f e /fq ⁇ 1.2 and the clamping levers should have the following lever arm ratios: i) L1S/L1 ⁇ 0.5 ii) L2S/L2 ⁇ 0.5 with:
  • L1S Distance between the axis of rotation of the spring plate of one clamping lever and its axis of rotation on the base;
  • L1 Distance from the axis of rotation of the tensioning roller of one tensioning lever to its axis of rotation on the base;
  • L2S Distance from the axis of rotation of the spring plate of the other clamping lever to its axis of rotation on the base;
  • L2 Distance from the axis of rotation of the tensioning roller of the other tensioning lever to its axis of rotation on the base.
  • the high spring natural frequency associated with the comparatively high spring rate prevents the spring from resonating within the operating speed range of the internal combustion engine.
  • the vibration behavior of the spring is improved not only in its longitudinal direction, but also in its transverse direction.
  • a resonance-free vibration behavior of the helical compression spring in the transverse direction is achieved through the aforementioned relationships for the longitudinal natural frequency f e and the transverse natural frequency f q of the spring.
  • FIG. 1 shows the belt tensioner known from the prior art cited at the outset;
  • Figure 2 shows the belt tensioner according to the invention in plan view.
  • FIG. 1 shows a starter generator belt drive of an internal combustion engine with a known belt tensioner 1 .
  • This comprises a base 3 fastened to the starter generator 2 and two clamping levers 4 and 5 rotatably mounted thereon, on the levers of which a respective clamping roller 6 or 7 on the one hand and a spring plate 8 or 9 on the other are rotatably mounted.
  • the pivot bearing of the clamping lever 4, 5 on the base 3 are located between the spring plates 8 and 9 and the tension roller 6 and 7, respectively, with the axes of rotation 10 and 11 of the clamping lever 4, 5 on the base 3 from each other and from the Rotational axis 12 of the starter generator 2 are different.
  • the pretensioning of the belt 14 that wraps around the generator pulley 13, the tensioning rollers 6, 7 and (at least) one crankshaft pulley 16 is generated by a helical compression spring 15, which is clamped between the spring plates 8, 9 and whose spring force forces the tensioning rollers 6, 7 towards one another .
  • the starter generator operating mode starting the internal combustion engine or generator operation
  • the current slack side of the belt 14 is pretensioned.
  • the lever arms shown are the following distances:
  • L1S Distance between the axis of rotation 17 of the spring plate 8 of one clamping lever 4 and its axis of rotation 10 on the base 3
  • L1 Distance between the axis of rotation 18 of the tensioning roller 6 of one tensioning lever 4 and its axis of rotation 10 on the base 3
  • L2S Distance between the axis of rotation 19 of the spring plate 9 of the other clamping lever 5 and its axis of rotation 11 on the base 3
  • the belt tensioner 1 shown in Figure 2 defuses the conflict of objectives between changing the belt pretensioning force as little as possible and operating the helical compression spring 15 with as little vibration as possible. This is achieved by dimensioning the lever arms of the tensioning levers 4, 5 with the following ratios: i) L1S/L1 ⁇ 0 .5 ii) L2S/L2 ⁇ 0.5
  • the spring rate c of the helical compression spring 15 is: 20 N/mm ⁇ c ⁇ 40 N/mm.
  • the vibration behavior in the sense of a resonance-free operation of the helical compression spring is optimized by the above-mentioned relationships for the longitudinal natural frequency f e and the transverse natural frequency f q : i) 220 Hz ⁇ f e ⁇ 260 Hz ii) 190 Hz ⁇ f q ⁇ 240 Hz iii) 1 ⁇ f e /fq ⁇ 1.2

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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

The invention relates to a belt tensioner (1) for a starter generator belt drive of an internal combustion engine, comprising: - a base (3), - two tensioning levers (4, 5), on the respective lever ends of which a tensioning roller (6, 7) on one side, around which the belt (14) is wrapped, and a spring plate (8, 9) on the other side are rotatably mounted, wherein the tensioning levers are each mounted rotatably on the base between the spring plate and the tensioning roller, and the axes of rotation (10, 11) of the tensioning levers on the base differ from each other and from the axis of rotation (12) of the starter generator (2), - and a helical compression spring (15), which is clamped in between the spring plates and loads the tensioning rollers towards one another. The spring rate of the helical compression spring is c > 20 N/mm, and the following lever arm ratios apply: i) L1S/L1 < 0.5; ii) L2S/L2 < 0.5 where: L1S: distance of the axis of rotation (17) of the spring plate (8) of one tensioning lever (4) from its axis of rotation (10) on the base; L1: distance of the axis of rotation (18) of the tensioning roller (6) of one tensioning lever from its axis of rotation on the base; L2S: distance of the axis of rotation (19) of the spring plate (9) of the other tensioning lever (5) from its axis of rotation (11) on the base; L2: distance of the axis of rotation (20) of the tensioning roller (7) of the other tensioning lever from its axis of rotation on the base.

Description

Riemenspanner belt tensioner
Die Erfindung betrifft einen Riemenspanner eines Startergenerator-Riementriebs einer Brennkraftmaschine, umfassend: The invention relates to a belt tensioner for a starter generator belt drive of an internal combustion engine, comprising:
- eine Basis, - One Base,
- zwei Spannhebel, an deren Hebelenden jeweils eine vom Riemen umschlungene Spannrolle einerseits und ein Federteller andererseits drehbar gelagert sind, wobei die Spannhebel jeweils zwischen dem Federteller und der Spannrolle drehbar auf der Basis gelagert sind und die Drehachsen der Spannhebel auf der Basis voneinander und von der Drehachse des Startergenerators verschieden sind, - Two tensioning levers, at the ends of which a tensioning pulley wrapped by the belt on the one hand and a spring plate on the other hand are rotatably mounted, with the tensioning levers being rotatably mounted on the base between the spring plate and the tensioning pulley and the axes of rotation of the tensioning levers on the basis of each other and of the axis of rotation of the starter generator are different,
- und eine zwischen den Federtellern eingespannte Schraubendruckfeder, die die Spann rollen aufeinander zu kraftbeaufschlagt. - and a helical compression spring clamped between the spring plates, which applies force to the tension rollers towards one another.
Ein derartiger Riemenspanner ist aus der jeweils gattungsgemäßen US 2019/ 0 285 149 A1, US 9 759 293 B2 und DE 103 48 878 A1 bekannt. Der kinematischen Konstruktion dieser sogenannten Zweiarm-Spanner liegt oftmals das Ziel zugrunde, dass die auf die Spannrollen wirkende Federkraft - unabhängig von der gegenseitigen Auslenkung der Spannhebel und folglich unabhängig vom Federweg der Schraubendruckfeder - möglichst unveränderlich und idealerweise konstant ist. Dieses Ziel ist prinzipiell mit einer ver gleichsweise kleinen Federrate zu erreichen. Ein weiteres Ziel besteht in einem möglichst schwingungsarmen Betriebsverhalten des Riemenspanners. Dieses weitere Ziel ist prinzi piell mit einer vergleichsweise hohen Federeigenfrequenz und folglich hohen Federrate zu erreichen. Damit stehen beide Ziele in gegenseitigem Konflikt. Such a belt tensioner is known from the respective generic US 2019/0 285 149 A1, US 9 759 293 B2 and DE 103 48 878 A1. The kinematic design of these so-called two-arm clamps is often based on the goal that the spring force acting on the tension rollers - independent of the mutual deflection of the clamping levers and consequently independent of the spring deflection of the helical compression spring - is as unchangeable as possible and ideally constant. In principle, this goal can be achieved with a comparatively small spring rate. Another goal is to ensure that the belt tensioner operates with as little vibration as possible. In principle, this further goal can be achieved with a comparatively high spring natural frequency and consequently high spring rate. Both goals are in conflict with each other.
Die US 2004 / 0 043 854 A1 offenbart einen Riemenspanner einer elektrischen Fahrzeug lenkung. US 2004/0 043 854 A1 discloses a belt tensioner for an electric vehicle steering system.
Der vorliegenden Erfindung liegt die Aufgabe zugrunde, diesen Zielkonflikt zu entschär fen. The present invention is based on the object of defusing this conflict of objectives.
Die Lösung der Aufgabe ergibt sich aus den Merkmalen des Anspruchs 1. Demnach soll die Schraubendruckfeder eine Federrate c > 20 N/mm haben, wobei für deren Längsei genfrequenz fe und deren Quereigenfrequenz fq folgende Beziehungen gelten: i) 220 Hz < fe < 260 Hz ii) 190 Hz < fq < 240 Hz iii) 1 < fe/fq < 1 ,2 und die Spannhebel sollen folgende Hebelarmverhältnisse haben: i) L1S/L1 < 0,5 ii) L2S/L2 < 0,5 mit: The solution to the problem results from the features of claim 1. According to this, the helical compression spring should have a spring rate c>20 N/mm, with the following relationships applying to its longitudinal natural frequency f e and its transverse natural frequency f q : i) 220 Hz <f e < 260 Hz ii) 190 Hz < f q < 240 Hz iii) 1 < f e /fq < 1.2 and the clamping levers should have the following lever arm ratios: i) L1S/L1 < 0.5 ii) L2S/L2 < 0.5 with:
L1S: Abstand der Drehachse des Federtellers des einen Spannhebels zu dessen Dreh achse auf der Basis; L1S: Distance between the axis of rotation of the spring plate of one clamping lever and its axis of rotation on the base;
L1: Abstand der Drehachse der Spannrolle des einen Spannhebels zu dessen Dreh achse auf der Basis; L1: Distance from the axis of rotation of the tensioning roller of one tensioning lever to its axis of rotation on the base;
L2S: Abstand der Drehachse des Federtellers des anderen Spannhebels zu dessen Drehachse auf der Basis; L2S: Distance from the axis of rotation of the spring plate of the other clamping lever to its axis of rotation on the base;
L2: Abstand der Drehachse der Spannrolle des anderen Spannhebels zu dessen Dreh achse auf der Basis. L2: Distance from the axis of rotation of the tensioning roller of the other tensioning lever to its axis of rotation on the base.
Diese erfindungsgemäße Kombination der vergleichsweise kleinen Hebelarmverhältnisse mit der vergleichsweise hohen Federrate löst den eingangs erläuterten Zielkonflikt best möglich auf. Denn Abstandsänderungen der Spannrollen und folglich gegenseitige Aus lenkungen der Spannhebel werden in deutlich kleinere Abstandsänderungen der Federtel ler und folglich kleinere Federwege mit entsprechend kleinen Federkraftänderungen über setzt. This combination according to the invention of the comparatively small lever arm ratios with the comparatively high spring rate resolves the initially explained conflict of objectives in the best possible way. Because changes in the distance between the tension rollers and consequently mutual deflections from the tensioning levers are translated into significantly smaller changes in the distance between the spring plates and consequently smaller spring deflections with correspondingly small changes in spring force.
Die mit der vergleichsweise hohen Federrate einhergehende hohe Federeigenfrequenz verhindert es, dass die Feder innerhalb des betrieblichen Drehzahlbereichs der Brenn kraftmaschine in Resonanz gerät. Das Schwingungsverhalten der Feder wird nicht nur in deren Längsrichtung, sondern auch in deren Querrichtung verbessert. Ein resonanzfreies Schwingungsverhalten der Schraubendruckfeder in Querrichtung wird durch die zuvor genannten Beziehungen für die Längseigenfrequenz fe und die Quereigenfrequenz fq der Feder erzielt. The high spring natural frequency associated with the comparatively high spring rate prevents the spring from resonating within the operating speed range of the internal combustion engine. The vibration behavior of the spring is improved not only in its longitudinal direction, but also in its transverse direction. A resonance-free vibration behavior of the helical compression spring in the transverse direction is achieved through the aforementioned relationships for the longitudinal natural frequency f e and the transverse natural frequency f q of the spring.
Weitere Merkmale der Erfindung ergeben sich aus der nachfolgenden Beschreibung und aus den Zeichnungen mit einem Ausführungsbeispiel eines erfindungsgemäßen Riemen spanners eines Nebenaggregate-Riementriebs einer Brennkraftmaschine. Funktionsglei che Merkmale oder Bauteile sind mit gleichen Bezugszahlen versehen. Es zeigen: Further features of the invention emerge from the following description and from the drawings with an embodiment of a belt tensioner according to the invention of an auxiliary unit belt drive of an internal combustion engine. Functionally equivalent features or components are provided with the same reference numbers. Show it:
Figur 1 den aus dem eingangs zitierten Stand der Technik bekannten Riemenspanner; Figur 2 den erfindungsgemäßen Riemenspanner in der Draufsicht. FIG. 1 shows the belt tensioner known from the prior art cited at the outset; Figure 2 shows the belt tensioner according to the invention in plan view.
In Figur 1 ist ein Startergenerator- Riementrieb einer Brennkraftmaschine mit einem be kannten Riemenspanner 1 dargestellt. Dieser umfasst eine am Startergenerator 2 befes tigte Basis 3 und zwei darauf drehbar gelagerte Spannhebel 4 und 5, an deren Hebelen den jeweils eine Spannrolle 6 bzw. 7 einerseits und ein Federteller 8 bzw. 9 andererseits drehbar gelagert sind. Die Drehlager der Spannhebel 4, 5 auf der Basis 3 befinden sich jeweils zwischen dem Federteller 8 bzw. 9 und der Spannrolle 6 bzw. 7, wobei die Dreh achsen 10 bzw. 11 der Spannhebel 4, 5 auf der Basis 3 voneinander und von der Dreh achse 12 des Startergenerators 2 verschieden sind. Die Vorspannung des die Generator riemenscheibe 13, die Spannrollen 6, 7 und (zumindest) eine Kurbelwellenriemenscheibe 16 umschlingenden Riemens 14 wird durch eine Schraubendruckfeder 15 erzeugt, die zwischen den Federtellern 8, 9 eingespannt ist und deren Federkraft die Spannrollen 6, 7 aufeinander zu kraftbeaufschlagt. Dabei wird in Abhängigkeit des Startergenerator- Betriebsmodus (Starten der Brennkraftmaschine oder Generatorbetrieb) das momentane Leertrum des Riemens 14 vorgespannt. FIG. 1 shows a starter generator belt drive of an internal combustion engine with a known belt tensioner 1 . This comprises a base 3 fastened to the starter generator 2 and two clamping levers 4 and 5 rotatably mounted thereon, on the levers of which a respective clamping roller 6 or 7 on the one hand and a spring plate 8 or 9 on the other are rotatably mounted. The pivot bearing of the clamping lever 4, 5 on the base 3 are located between the spring plates 8 and 9 and the tension roller 6 and 7, respectively, with the axes of rotation 10 and 11 of the clamping lever 4, 5 on the base 3 from each other and from the Rotational axis 12 of the starter generator 2 are different. The pretensioning of the belt 14 that wraps around the generator pulley 13, the tensioning rollers 6, 7 and (at least) one crankshaft pulley 16 is generated by a helical compression spring 15, which is clamped between the spring plates 8, 9 and whose spring force forces the tensioning rollers 6, 7 towards one another . Depending on the starter generator operating mode (starting the internal combustion engine or generator operation), the current slack side of the belt 14 is pretensioned.
Bei den eingezeichneten Hebelarmen handelt es sich um folgende Abstände: The lever arms shown are the following distances:
L1S: Abstand der Drehachse 17 des Federtellers 8 des einen Spannhebels 4 zu dessen Drehachse 10 auf der Basis 3 L1S: Distance between the axis of rotation 17 of the spring plate 8 of one clamping lever 4 and its axis of rotation 10 on the base 3
L1: Abstand der Drehachse 18 der Spannrolle 6 des einen Spannhebels 4 zu dessen Drehachse 10 auf der Basis 3 L1: Distance between the axis of rotation 18 of the tensioning roller 6 of one tensioning lever 4 and its axis of rotation 10 on the base 3
L2S: Abstand der Drehachse 19 des Federtellers 9 des anderen Spannhebels 5 zu des sen Drehachse 11 auf der Basis 3 L2S: Distance between the axis of rotation 19 of the spring plate 9 of the other clamping lever 5 and its axis of rotation 11 on the base 3
L2: Abstand der Drehachse 20 der Spannrolle 7 des anderen Spannhebels 5 zu dessen Drehachse 11 auf der Basis 3 L2: Distance from the axis of rotation 20 of the tensioning roller 7 of the other tensioning lever 5 to its axis of rotation 11 on the base 3
Es ist deutlich erkennbar, dass für die Hebelarmverhältnisse in guter Näherung gilt: It is clearly recognizable that the following applies to the lever arm ratios as a good approximation:
L1S/L1 ~ L2S/L2 ~ 1 L1S/L1 ~ L2S/L2 ~ 1
Das bedeutet, dass die betriebliche Abstandsänderung der Spannrollen 6, 7 zueinander mit einer ähnlich großen Abstandsänderung der Federteller 8, 9 zueinander einhergeht und dass umgekehrt die entsprechend große Federkraftänderung mit einer ähnlich gro ßen Kraftänderung der Spannrollen 7, 8 auf den Riemen 14 einhergeht. Wie eingangs erläutert, ist zum einen die hohe Änderung der Riemenvorspannkraft unerwünscht. Zum anderen beschränkt der hohe Federweg die Höhe der Federrate und folglich die Eigenfre quenz der Schraubendruckfeder 15, die dann innerhalb des betrieblich nutzbaren Dreh zahlbereichs der Brennkraftmaschine in Resonanz zu gelangen droht. This means that the operational change in the distance between the tension rollers 6, 7 to one another is accompanied by a similarly large change in the distance between the spring plates 8, 9 to one another and that, conversely, the correspondingly large change in spring force is accompanied by a similarly large change in force of the tension rollers 7, 8 on the belt 14. As explained at the outset, the high change in the belt pretensioning force is undesirable. On the other hand, the high spring deflection limits the height of the spring rate and consequently the eigenfre frequency of the helical compression spring 15, which then threatens to resonate within the operationally usable speed range of the internal combustion engine.
Der in Figur 2 dargestellte Riemenspanner 1 entschärft den Zielkonflikt zwischen einer möglichst geringen Änderung der Riemenvorspannkraft und einem möglichst schwin gungsarmen Betrieb der Schraubendruckfeder 15. Dies erfolgt durch die Dimensionierung der Hebelarme der Spannhebel 4, 5 mit folgenden Verhältnissen: i) L1S/L1 < 0,5 ii) L2S/L2 < 0,5 The belt tensioner 1 shown in Figure 2 defuses the conflict of objectives between changing the belt pretensioning force as little as possible and operating the helical compression spring 15 with as little vibration as possible. This is achieved by dimensioning the lever arms of the tensioning levers 4, 5 with the following ratios: i) L1S/L1 < 0 .5 ii) L2S/L2 < 0.5
Vorliegend gilt: L1S/L1 = L2S/L2 = 0,49 und folglich gilt auch: iii) L1S/L1 = L2S/L2 Here L1S/L1 = L2S/L2 = 0.49 and consequently also: iii) L1S/L1 = L2S/L2
Die Federrate c der Schraubendruckfeder 15 beträgt: 20 N/mm < c < 40 N/mm. The spring rate c of the helical compression spring 15 is: 20 N/mm<c<40 N/mm.
Das Schwingungsverhalten im Sinne eines resonanzfreien Betriebs der Schraubendruck feder ist durch die eingangs genannten Beziehungen für die Längseigenfrequenz fe und die Quereigenfrequenz fq optimiert: i) 220 Hz < fe < 260 Hz ii) 190 Hz < fq < 240 Hz iii) 1 < fe/fq < 1 ,2 The vibration behavior in the sense of a resonance-free operation of the helical compression spring is optimized by the above-mentioned relationships for the longitudinal natural frequency f e and the transverse natural frequency f q : i) 220 Hz < f e < 260 Hz ii) 190 Hz < f q < 240 Hz iii) 1 < f e /fq < 1.2

Claims

Patentansprüche patent claims
1. Riemenspanner (1) für einen Startergenerator-Riementrieb einer Brennkraftmaschine, umfassend: 1. Belt tensioner (1) for a starter generator belt drive of an internal combustion engine, comprising:
- eine Basis (3), - a base (3),
- zwei Spannhebel (4, 5), an deren Hebelenden jeweils eine vom Riemen (14) um schlungene Spannrolle (6, 7) einerseits und ein Federteller (8, 9) andererseits dreh bar gelagert sind, wobei die Spannhebel (4, 5) jeweils zwischen dem Federteller (8, 9) und der Spannrolle (6, 7) drehbar auf der Basis (3) gelagert sind und die Dreh achsen (10, 11) der Spannhebel (4, 5) auf der Basis (3) voneinander und von der Drehachse (12) des Startergenerators (2) verschieden sind, - Two tensioning levers (4, 5), at the lever ends of which a tensioning roller (6, 7) wound around by the belt (14) on the one hand and a spring plate (8, 9) on the other hand are rotatably mounted, with the tensioning levers (4, 5) are each rotatably mounted on the base (3) between the spring plate (8, 9) and the tensioning roller (6, 7) and the axes of rotation (10, 11) of the tensioning levers (4, 5) on the base (3) from each other and are different from the axis of rotation (12) of the starter generator (2),
- und eine zwischen den Federtellern (8, 9) eingespannte Schraubendruckfeder (15), die die Spannrollen (6, 7) aufeinander zu kraftbeaufschlagt, gekennzeichnet durch die Federrate c > 20 N/mm der Schraubendruckfeder (15), wobei für deren Längseigenfrequenz fe und deren Quereigenfrequenz fq folgende Be ziehungen gelten: i) 220 Hz < fe < 260 Hz ii) 190 Hz < fq < 240 Hz - and a helical compression spring (15) clamped between the spring plates (8, 9) which applies force to the tensioning rollers (6, 7) towards one another, characterized by the spring rate c > 20 N/mm of the helical compression spring (15), where for its longitudinal natural frequency f e and its transverse natural frequency f q the following relationships apply: i) 220 Hz < f e < 260 Hz ii) 190 Hz < f q < 240 Hz
Üi) 1 < fe/fq < 1,2 und folgende Hebelarmverhältnisse: i) L1S/L1 < 0,5 ii) L2S/L2 < 0,5 mit: Üi) 1 < f e /fq < 1.2 and the following lever arm ratios: i) L1S/L1 < 0.5 ii) L2S/L2 < 0.5 with:
L1S: Abstand der Drehachse (17) des Federtellers (8) des einen Spannhebels (4) zu dessen Drehachse (10) auf der Basis (3); L1S: Distance between the axis of rotation (17) of the spring plate (8) of one clamping lever (4) and its axis of rotation (10) on the base (3);
L1: Abstand der Drehachse (18) der Spannrolle (6) des einen Spannhebels (4) zu dessen Drehachse (10) auf der Basis (3); L1: Distance from the axis of rotation (18) of the tensioning roller (6) of one tensioning lever (4) to its axis of rotation (10) on the base (3);
L2S: Abstand der Drehachse (19) des Federtellers (9) des anderen Spannhebels (5) zu dessen Drehachse (11) auf der Basis (3); L2S: Distance between the axis of rotation (19) of the spring plate (9) of the other clamping lever (5) and its axis of rotation (11) on the base (3);
L2: Abstand der Drehachse (20) der Spannrolle (7) des anderen Spannhebels (5) zu dessen Drehachse (11) auf der Basis (3). L2: Distance from the axis of rotation (20) of the tensioning roller (7) of the other tensioning lever (5) to its axis of rotation (11) on the base (3).
2. Riemenspanner (1) nach Anspruch 1, gekennzeichnet durch: L1S/L1 = L2S/L2. 2. Belt tensioner (1) according to claim 1, characterized by: L1S/L1 = L2S/L2.
3. Riemenspanner (1) nach Anspruch 1 oder 2, gekennzeichnet durch: c < 40 N/mm. 3. Belt tensioner (1) according to claim 1 or 2, characterized by: c <40 N/mm.
PCT/DE2022/100142 2021-02-26 2022-02-23 Belt tensioner WO2022179664A1 (en)

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DE102021104655.6A DE102021104655B4 (en) 2021-02-26 2021-02-26 Belt tensioner

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040043854A1 (en) 2002-08-30 2004-03-04 Fraley Richard R. Belt tensioner for electric power steering unit
DE10348878A1 (en) 2002-10-22 2004-05-13 Dana Corp., Toledo Belt tensioning device for internal combustion engines
US20170074375A1 (en) * 2014-10-21 2017-03-16 Litens Automotive Partnership Endless drive arrangement and improved two-armed tensioning system for same
US20190285149A1 (en) 2018-03-16 2019-09-19 Toyota Jidosha Kabushiki Kaisha Belt tensioner

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040043854A1 (en) 2002-08-30 2004-03-04 Fraley Richard R. Belt tensioner for electric power steering unit
DE10348878A1 (en) 2002-10-22 2004-05-13 Dana Corp., Toledo Belt tensioning device for internal combustion engines
US20170074375A1 (en) * 2014-10-21 2017-03-16 Litens Automotive Partnership Endless drive arrangement and improved two-armed tensioning system for same
US9759293B2 (en) 2014-10-21 2017-09-12 Litens Automotive Partnership Endless drive arrangement and improved two-armed tensioning system for same
US20190285149A1 (en) 2018-03-16 2019-09-19 Toyota Jidosha Kabushiki Kaisha Belt tensioner

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