WO2003066414A1 - Systeme de direction asservi - Google Patents

Systeme de direction asservi Download PDF

Info

Publication number
WO2003066414A1
WO2003066414A1 PCT/EP2003/001080 EP0301080W WO03066414A1 WO 2003066414 A1 WO2003066414 A1 WO 2003066414A1 EP 0301080 W EP0301080 W EP 0301080W WO 03066414 A1 WO03066414 A1 WO 03066414A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
steering system
power steering
sun
gears
Prior art date
Application number
PCT/EP2003/001080
Other languages
German (de)
English (en)
Inventor
Michael Wiget
Original Assignee
Zf Lenksysteme Gmbh
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 Zf Lenksysteme Gmbh filed Critical Zf Lenksysteme Gmbh
Publication of WO2003066414A1 publication Critical patent/WO2003066414A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/008—Changing the transfer ratio between the steering wheel and the steering gear by variable supply of energy, e.g. by using a superposition gear
    • 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
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H35/008—Gearings or mechanisms with other special functional features for variation of rotational phase relationship, e.g. angular relationship between input and output shaft
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0806—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts
    • F16H37/0826—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one output shaft

Definitions

  • the invention relates to a power steering system, which is particularly intended for a vehicle.
  • a power steering system comprises a superposition gear which has a first input gear element and a second input gear element and an output gear element.
  • the aforementioned transmission members include two sun gears and a planetary gear part, comprising a planet carrier and at least one planet gear rotatably mounted thereon.
  • the first input gear element is coupled to a hand steering wheel, the second input gear element, however, to a servo motor.
  • the output gear member is coupled to a steering gear which, in a known manner, transmits a steering movement to the vehicle wheels.
  • Such a power steering system makes it possible to superimpose on the motion triggered by the hand steering wheel a motion emanating from the servo motor.
  • the superposition gear of a known power steering system (DE 197 23 358 AI) is a spur gear planetary
  • BESTATIGUNGSKOPIE gear trained The two sun gears are arranged one behind the other and coaxially within the planet carrier.
  • This design has the disadvantage that the planetary gear part (planet carrier plus planet gear or plus planet gears) is naturally quite voluminous. As a result, the space requirement for the superimposition gearbox within the vehicle is relatively large; further disadvantages are the high manufacturing costs and a relatively high weight.
  • the object of the invention is therefore to create a power steering system whose superimposed gearboxes - with the same function as before - fulfills as many of the following requirements as possible:
  • the construction volume of the superposition gear is to be reduced compared to previously;
  • the weight of the superposition gear is also to be reduced compared to previously.
  • a superimposed gear is no longer a pure spur gear planetary gear in which the axis of rotation of the planet gear or the planet gears is or are always parallel to the axis of rotation of the planet carrier, but a superimposed gear, in which the axis of rotation (s) of the planet gear or the planet gears forms an angle with the axis of rotation of the planet carrier. This angle is on the order of about 45 ° to 90 °.
  • gears which are designed according to the aforementioned solution principle.
  • bevel gear planetary gear known per se, which has two bevel gear sun gears and one bevel gear planet gear or (preferably) two bevel gear planet gears which mesh with the sun gears.
  • the various designs described in detail below have in common that when used in a power steering system they offer the essential advantage of smaller space requirements, lower manufacturing costs and reduced weight.
  • the sun gears is part of the first input gear member, the planet carrier being part of the output gear member.
  • one of the sun gears is part of the output gear member, the planet carrier being part of the first input gear member.
  • the sun gear is driven as a part of the second input transmission member by means of the servomotor, respectively.
  • Fig. 2 shows an alternative. Bevel superposition gear
  • Fig. 6 schematically shows a complete power steering system.
  • a main part of the power steering system shown in FIG. 6 is a bevel gear superposition gear designated overall by 10.
  • This includes a first input gear element 4, 14, which is connected to a manual steering wheel 11, and a second input gear element 6, which is coupled (for example via a worm gear 7) to a servo motor 12.
  • an output transmission element 1 which is coupled to a steering gear 13.
  • the first input gear element 4, .14 is designed as a planet carrier, composed of a web shaft 4 and a web 14, on which two planet gears 3 are rotatably mounted. Each of these planet gears 3 meshes with two sun gears 2 and 5.
  • the sun gear 2 is part of the output gear element 1, while the other sun gear 5 is part of the second input gear element 6. All gears 2, 3 and 5 are designed as bevel gears. If necessary, the hand steering wheel 11 and the steering gear 13 can be interchanged in the diagram according to FIG. 6. In this case, 1 would be the first input gear element and 4 would be the output gear element.
  • the power steering system shown in FIG. 6 works as follows: if, for example, the servo motor 12 is stationary, the movement of the steering gear 13 is determined exclusively by the hand steering wheel 11. Deviating from this, the power steering system makes it possible to superimpose a movement emanating from the servo motor 12 onto the movement triggered by the hand steering wheel 11. This achieves advantages in terms of driving dynamics, driving safety and / or driving comfort.
  • Fig. 1 the individual parts of the bevel gear planetary gear 10 shown are given the same reference numerals as in Fig. 6.
  • the angle a between the web shaft 4 and the web 14 is 90 ° in this embodiment.
  • the two sun gears 2 and 5 are the same size; more precisely: the toothing diameters of the two sun gears 2 and 5 are the same.
  • the cone angles of all the gear wheels 2, 3 and 5 are 90 °, which is why the planet wheels 3 have the same size as the sun wheels 2 and 5.
  • FIG. 6 can have a smaller toothing diameter than the sun gears 2 and 5.
  • FIG Fig. 1 Schematically indicated in FIG Fig. 1 that the planet gears 3 are pressed with the help of disc springs 15 with their teeth on the teeth of the sun gears 2 and 5. This is a measure to ensure the necessary freedom from play of the superposition gear 10.
  • the bearings of the planet gears 3 are also made to be designed on the web 14 without play. Bearings are preferably provided which, in addition to the freedom from play mentioned, also allow the planet wheels 3 to tilt slightly relative to the web 14.
  • the angle a formed by the axes of rotation of the planet wheels 3 with the axis of rotation of the planet carrier 4, 14 is now approximately 75 °. Accordingly, the sun gear 5 belonging to the second input transmission part has a smaller toothing diameter (and thus a smaller number of teeth) than the other sun gear 2. This can be advantageous in order to achieve different gear ratios compared to FIG. 1.
  • the angle a (as in FIG. 1) is 90 °.
  • the sun gears 2 and 5 are designed as crown gears, and accordingly the planet gears 3 as spur gears.
  • the exemplary embodiment according to FIG. 4 is a "hermaphrodite" with features from FIGS. 2 and 3.
  • the sun gear 5 belonging to the second input transmission element 6 is designed as a relatively small bevel gear, the other sun gear 2 as a crown gear.
  • the planet gears 3 are also designed as bevel gears; whose axes of rotation form an angle a of approximately 60 ° with the axis of rotation of the web shaft 4.
  • the embodiment according to FIG. 5 is similar to that according to FIG. 2 in that the sun gear 5 belonging to the second input transmission element 6 is smaller than the other sun gear 2.
  • Each ' planet gear has an angle a of 90 ° 3 two ring gears with different toothing diameters, one ring gear meshing with one sun gear and the other ring gear meshing with the other sun wheel. It is understood that the different toothings on the one hand of the two sun gears and on the other hand each planet gear have different numbers of teeth.
  • the sun gears 2 and 5 can be designed as crown gears, in which case the planet gears 3 are to be designed as spur gears.
  • the planet carrier 4, 14 can be either the first input gear element or the output gear element. Accordingly, the opposite sun gear 2 is then either part of the transmission output member or part of the first transmission input member.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Gear Transmission (AREA)

Abstract

La présente invention concerne un système de direction asservi destiné à un véhicule, comprenant un engrenage de superposition (10) présentant deux éléments d'engrenage d'entrée (4,6) et un élément d'engrenage de sortie (1), l'engrenage de superposition (10) présentant deux roues solaires (2,5) et un support planétaire (4,14) comportant des roues planétaires (3). L'un des éléments d'engrenage d'entrée (4) est couplé à une roue de direction manuelle (11) et l'autre élément d'engrenage d'entrée (6) est couplé à un servomoteur (12), alors que l'élément d'engrenage de sortie (1) est couplé à un engrenage de direction (13). Les axes de rotation des roues planétaires (3) formant avec l'axe de rotation du support planétaire (4,14) un angle (a) qui vaut de 45° à 90°. De préférence, l'engrenage de superposition (10) se présente sous la forme d'un engrenage planétaire à roues coniques.
PCT/EP2003/001080 2002-02-06 2003-02-04 Systeme de direction asservi WO2003066414A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10204736.7 2002-02-06
DE2002104736 DE10204736A1 (de) 2002-02-06 2002-02-06 Servolenksystem

Publications (1)

Publication Number Publication Date
WO2003066414A1 true WO2003066414A1 (fr) 2003-08-14

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2003/001080 WO2003066414A1 (fr) 2002-02-06 2003-02-04 Systeme de direction asservi

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DE (1) DE10204736A1 (fr)
WO (1) WO2003066414A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1843932B1 (fr) * 2005-02-04 2011-04-06 ThyssenKrupp Presta Aktiengesellschaft Direction dotee d'un dispositif de coussin gonflable et mode de fonctionnement associe
CN103195898A (zh) * 2013-03-27 2013-07-10 东华大学 能实现可调摆幅输出的单向驱动非圆齿轮差动轮系及方法
CN103307243A (zh) * 2013-07-11 2013-09-18 肖福禄 一种双动力输入变速箱
CN104089005A (zh) * 2014-07-16 2014-10-08 重庆市佳南工贸有限公司 电动车变速箱无离合器同步器且实现滑行换挡倒档的装置
WO2019092516A1 (fr) * 2017-11-10 2019-05-16 Same Deutz-Fahr Italia S.P.A. Ensemble de réglage d'un système de direction hydraulique d'un véhicule

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004034099A1 (de) * 2004-07-15 2006-02-16 Zf Friedrichshafen Ag Getriebe für eine Aktivlenkung für Fahrzeuge
JP2006281815A (ja) * 2005-03-31 2006-10-19 Fuji Kiko Co Ltd 可変舵角比操舵装置ガタ詰め構造。
DE102009027342A1 (de) * 2009-06-30 2011-01-05 Zf Friedrichshafen Ag Überlagerungsgetriebe für ein Lenksystem
DE102012009049A1 (de) 2011-05-19 2012-11-22 Volkswagen Aktiengesellschaft Antriebsvorrichtung

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2128356A1 (de) * 1971-06-08 1973-03-01 Volkswagenwerk Ag Lenkeinrichtung fuer fahrzeuge mit ausregelung von seitenkrafteinfluessen
EP0189172A2 (fr) * 1985-01-21 1986-07-30 Nissan Motor Co., Ltd. Système de direction pour véhicule automobile ou équivalent
FR2606480A2 (fr) * 1986-02-06 1988-05-13 Dubreuil Marc Heriard Dispositif a changement de vitesse continu
EP0548854A1 (fr) * 1991-12-20 1993-06-30 CENTRO RICERCHE FIAT Società Consortile per Azioni Système de direction pour le réglage sans retardement de l'engrenate de direction
DE4304664A1 (de) * 1993-02-16 1994-08-18 Daimler Benz Ag Steuervorrichtung, insbesondere Lenkung für Kraftfahrzeuge
DE19541748A1 (de) * 1994-11-22 1996-05-30 Ihc Holland Nv Zahnradkasten für kontinuierlich variables Getriebe
US5957803A (en) * 1995-11-08 1999-09-28 Fini, Jr.; Anthony W. Clutch and continuously variable transmission

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2128356A1 (de) * 1971-06-08 1973-03-01 Volkswagenwerk Ag Lenkeinrichtung fuer fahrzeuge mit ausregelung von seitenkrafteinfluessen
EP0189172A2 (fr) * 1985-01-21 1986-07-30 Nissan Motor Co., Ltd. Système de direction pour véhicule automobile ou équivalent
FR2606480A2 (fr) * 1986-02-06 1988-05-13 Dubreuil Marc Heriard Dispositif a changement de vitesse continu
EP0548854A1 (fr) * 1991-12-20 1993-06-30 CENTRO RICERCHE FIAT Società Consortile per Azioni Système de direction pour le réglage sans retardement de l'engrenate de direction
DE4304664A1 (de) * 1993-02-16 1994-08-18 Daimler Benz Ag Steuervorrichtung, insbesondere Lenkung für Kraftfahrzeuge
DE19541748A1 (de) * 1994-11-22 1996-05-30 Ihc Holland Nv Zahnradkasten für kontinuierlich variables Getriebe
US5957803A (en) * 1995-11-08 1999-09-28 Fini, Jr.; Anthony W. Clutch and continuously variable transmission

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1843932B1 (fr) * 2005-02-04 2011-04-06 ThyssenKrupp Presta Aktiengesellschaft Direction dotee d'un dispositif de coussin gonflable et mode de fonctionnement associe
CN103195898A (zh) * 2013-03-27 2013-07-10 东华大学 能实现可调摆幅输出的单向驱动非圆齿轮差动轮系及方法
CN103307243A (zh) * 2013-07-11 2013-09-18 肖福禄 一种双动力输入变速箱
CN104089005A (zh) * 2014-07-16 2014-10-08 重庆市佳南工贸有限公司 电动车变速箱无离合器同步器且实现滑行换挡倒档的装置
CN104089005B (zh) * 2014-07-16 2018-03-23 重庆市佳南工贸有限公司 电动车变速箱无离合器同步器且实现滑行换挡倒档的装置
WO2019092516A1 (fr) * 2017-11-10 2019-05-16 Same Deutz-Fahr Italia S.P.A. Ensemble de réglage d'un système de direction hydraulique d'un véhicule
CN111315636A (zh) * 2017-11-10 2020-06-19 赛迈道依茨-法尔意大利股份公司 车辆的液压转向系统的调节组件
CN111315636B (zh) * 2017-11-10 2022-02-25 赛迈道依茨-法尔意大利股份公司 车辆的液压转向系统的调节组件
US11459014B2 (en) 2017-11-10 2022-10-04 Same Deutz-Fahr Italia S.P.A. Adjustment assembly of a hydraulic steering system of a vehicle

Also Published As

Publication number Publication date
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