EP3420249A1 - Dispositif de transmission à courroie et système de direction - Google Patents

Dispositif de transmission à courroie et système de direction

Info

Publication number
EP3420249A1
EP3420249A1 EP16805855.0A EP16805855A EP3420249A1 EP 3420249 A1 EP3420249 A1 EP 3420249A1 EP 16805855 A EP16805855 A EP 16805855A EP 3420249 A1 EP3420249 A1 EP 3420249A1
Authority
EP
European Patent Office
Prior art keywords
belt
drive
wheel
belts
tensioning wheel
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.)
Withdrawn
Application number
EP16805855.0A
Other languages
German (de)
English (en)
Inventor
Artur Kirschenmann
Gerd Speidel
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.)
Robert Bosch Automotive Steering GmbH
Original Assignee
Robert Bosch Automotive Steering 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 Robert Bosch Automotive Steering GmbH filed Critical Robert Bosch Automotive Steering GmbH
Publication of EP3420249A1 publication Critical patent/EP3420249A1/fr
Withdrawn legal-status Critical Current

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
    • B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
    • B62D5/0421—Electric motor acting on or near steering gear
    • B62D5/0424—Electric motor acting on or near steering gear the axes of motor and final driven element of steering gear, e.g. rack, being parallel
    • B62D5/0427—Electric motor acting on or near steering gear the axes of motor and final driven element of steering gear, e.g. rack, being parallel the axes being coaxial
    • 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
    • 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
    • F16H2007/0825—Actuators for final output members influenced by other actuators of output members

Definitions

  • the invention relates to a belt transmission and a steering system with such a belt transmission.
  • a belt transmission is used, for example, in an electric power steering system to drive power of an example designed as an electric motor drive motor, which supports a torque transmitted from an operator via a steering handle and in particular a steering wheel to a steering shaft, on the steering shaft or a Transfer handlebar.
  • Timing belts are often used in such power steering systems in order to transmit a given torque with sufficient reliability even with relatively small belt tensions and wrap angles (and thus diameters of the drive and driven wheels).
  • a power steering system in which a flat belt for transmitting the
  • a disadvantage of the known from EP 1 777 140 A1 belt transmission is that the angle of the wrap of the drive and the driven gear is relatively small by the local arrangement of the tensioning wheel as a result of the mutually directed impingement of backbone and Lasttrum the angle of the drive transferable drive power is reduced accordingly. This is in particular in the case of the use of the belt drive provided in EP 1 777 140 A1 as well
  • the present invention seeks to provide a belt transmission, which is particularly intended for use in a steering system for a motor vehicle, which allows for relatively small dimensions transmission relatively high power ratings.
  • the belt transmission to be specified should also be characterized by a quietest possible operation.
  • a belt drive comprises at least one drive wheel, a driven wheel and a tensioning wheel (disposed between the drive wheel and the driven wheel) and is further characterized by at least two belts which drive the drive wheel, the driven wheel and one (between the drive wheel and the driven wheel) Each strand entraining the tensioning wheel partially, wherein a first belt, the tensioning wheel with the associated, in one direction, for example from the drive wheel to the output gear, extending strand in a circumferential direction and a second belt with the associated, in the same Direction, ie, in turn, for example, from the drive wheel to the driven wheel, extending strand wraps around the tensioning wheel in the other circumferential direction.
  • a particularly relevant advantage of this type of looping of the tensioning wheel through the belt is that due to geometric reasons, the looping of both the drive wheel and the driven gear considerably compared to a conventional belt transmission with an immersed from the outside in the backbone of a belt tensioning wheel and more Compared to the known from EP 1 777 140 A1 belt transmission is increased, whereby in a corresponding extent, the transferable by means of the belt drive power can be increased without having to increase the diameter of the drive and driven wheels.
  • toothless belt and in particular flat belt can be provided.
  • other toothless belts in particular V-belts, V-ribbed belts and / or round belts may also be used.
  • the tensioning wheel is therefore supported exclusively by the belts.
  • An additional support for the tensioning wheel can be dispensed with in particular if the belt drive according to the invention comprises at least two first belts and one or more second belts, wherein two first belts surround the second belt or belts with respect to the longitudinal direction (direction of the axis of rotation) of the tensioning wheel, ie arranged on both sides of the outside of these. In this way, a compensation of the tilting moments (by one with respect to the
  • Contact areas are proportional to the forces exerted by the belt on the tensioning wheel, radially directed forces and thus also to the optionally caused by these forces overturning moments.
  • Belt drive according to the invention can also be advantageous in terms of uniform elongation of the belt during operation and the transmission of equal drive power in the two directions of rotation.
  • Drive wheel coupled drive motor to be used, which is intended for operation in both directions.
  • a steering system according to the invention which is provided in particular for a motor vehicle, comprises at least one steering rod which is provided with one or more connecting elements (in particular tie rod ends) for a (preferably rotatable) connection with (in each case) a wheel steering lever of a steerable wheel (of the motor vehicle ) are provided, and further comprising a directly or indirectly acting on the handlebar steering drive having a drive motor, in particular electric motor (possibly also hydraulic motor), and a belt transmission according to the invention.
  • a drive motor in particular electric motor (possibly also hydraulic motor)
  • the steering system according to the invention may preferably be a
  • Power steering system act in which the drive power of the steering drive supportive to a manual by an operator of the steering system on the
  • Steering rod exerted steering force acts.
  • the steering system can also be designed such that the drive power generated by the steering drive
  • the steering system according to the invention may further preferably comprise a steering shaft, which is connected via a transmission with the handlebar, that a rotation of the steering shaft leads to a longitudinal axial translation of the handlebar.
  • a steering system may preferably be designed as a power steering system, when in addition to the steering shaft, a steering handle, in particular a steering wheel is rotatably connected. Alternatively or additionally, it may also be provided to let the steering drive or an additional steering drive interact with the steering shaft. If the comprehensive steering mechanism according to the invention a belt drive acts on the steering shaft, this acts indirectly on the handlebar.
  • a directly acting on the handlebar steering drive for example, additionally serving as a driven gear of the belt drive according to the invention
  • (Ball) comprise spindle nut, which cooperates with a helical groove in the handlebar to translate caused by the drive motor and the belt transmission rotation of the (ball) spindle nut in a longitudinal axial translation of the handlebar.
  • FIG. 1 shows a steering system according to the invention in a side view
  • Fig. 4 a section through the tensioning wheel and this partially wrapped
  • Fig. 5 a possible embodiment of the tensioning wheel in a perspective
  • Fig. 6 an alternative embodiment of the tensioning wheel in a perspective
  • the steering system illustrated in FIG. 1 represents an electric power steering system for, for example, a passenger car, not shown, moreover.
  • This comprises a steering rod 1, which is formed in a section as a rack.
  • steering pinion With the teeth (not visible) of the handlebar 1 meshes (not visible) steering pinion, which is rotatably connected to a steering shaft 2.
  • the steering shaft 2 in turn serves the rotationally fixed connection with a steering shaft, not shown, and the associated steering wheel of the passenger car.
  • tie rod ends 3 are arranged, which are for connection with
  • Wheel steering (not shown) are provided.
  • a longitudinal axial translation of the handlebar 1 is translated into a pivoting movement of the steered wheels (not shown) of the passenger car.
  • the steering system further comprises a steering drive 5 based on an electric motor 4. In dependence on the steering torque, which is a driver of the vehicle
  • This auxiliary steering torque or the rotational movement of a rotor (not visible) of the electric motor 4 provided for this purpose is (not visible) by means of a belt drive 7 according to the invention and another transmission, for example a
  • Ball screw transmission in which the handlebar 1 is provided with a spiral groove, engage in the balls of serving as a driven gear of the belt 7 or connected to such a driven spindle spindle nut, reduced to the handlebar 1.
  • FIG. 2 and 3 show in a simplified representation a section through the belt transmission 7 of the steering system according to FIG. 1, wherein the representations with respect to the direction of rotation of a drive wheel 8 (ie a non-rotatably connected to the rotor of the electric pinion) and thus of the overall
  • the belt transmission 7 arranged within a housing 9 of the steering system comprises, in addition to the drive wheel 8 and the axis-parallel thereto
  • Output gear 10 (spindle nut of the ball screw gear) nor a arranged between the drive wheel 8 and the output gear 10 tensioning wheel 1 1 and two the drive wheel 8, the driven gear 10 and the tensioning wheel 1 1 partially wrapped belt 12a, 12b, which are formed in the present embodiment as a flat belt , whereby a particularly quiet operation for the steering system can be realized.
  • three belts 12a, 12b are provided in the present embodiment, two of which as the first belt 12a with one of their dreams and with respect to an extension direction, for example from the
  • the tension wheel 1 1 in one of its circumferential directions wrap around, while a single belt, as the second belt 12b, also with one of his dreams (the respect of the tensioning wheel 1 1 wrapping Trume the first belt 12a, the drive wheel and the driven gear on the respect to the
  • Rotary axes 13, 14 of these wheels 8, 10 opposite side connects based on the same direction of extent, that is also coming from the drive wheel 8 and leading to the output gear 10, the tensioning wheel 1 1 in the other circumferential direction (counterclockwise in Figs and 3) wraps around. Due to the opposite looping of the arranged between the drive wheel 8 and the output gear 10 tensioning wheel 1 1 through the belt 12a, 12b is achieved on the one hand, that the individual belt 12a, 12b the drive wheel 8 and the output gear 10 each have a relatively large wrap angle of approx 270 °, whereby in each case a correspondingly large contact area between the belts 12a, 12b on the one hand and the drive wheel 8 and the
  • Output gear 10 is realized on the other hand, resulting in a purely non-positively acting flat belt transmission to a correspondingly larger transmittable torque.
  • the inventive guide the belt 12a, 12b a looping of the tensioning wheel 1 1 by the belt 12a, 12b achieved in combination of about 360 °, so this can be safely stored by exclusively the belt 12a, 12b, without the need for a additional storage on, for example, the housing 9 of the steering system would be required.
  • Fig. 2 shows a rotation of the drive wheel 8 and thus also the output gear 10 in the counterclockwise direction, whereby those dreams of all belts 12 a, 12 b, the with respect to the axes of rotation 13, 14 of the drive wheel 8 and the driven wheel 10 in FIG. 2 on the upper side connecting the drive wheel 8 and the output gear 10, load trays 16a, 16b representing the driving force generated by the
  • Electric motor 4 is transmitted in the form of a torque to the drive wheel 8, primarily transmitted to the output gear 8.
  • This driving force causes a significant tension within these Lasttrume 16a, 16b, whereby the Lasttrum 16b of the second belt 12b, which wraps around the axis of rotation 15, the tensioning wheel 1 1 on the distal of the Lasttrumen 16a of the two first belt 12a side, the tensioning wheel 1 1 in the direction of the Lasttrume 16a of the two first belt 12a (ie in the Fig. 2 upward) acted on, thereby relatively relatively into the tensioning wheel 1 1 with respect to the axis of rotation 15 on the other side looping empty belt 17a of the first belt 12a immersed and thereby these first straps 12a are tensioned.
  • Tensioning wheel 1 1 entrapping dreams (which are located in Fig. 3 with respect to the axes of rotation 13, 14 of the drive wheel 8 and the output gear 10 below) the tensioning wheel 1 1 in the direction of increasing immersion in the slack side 17b of the second belt 12b burden.
  • the belt width of the second belt 12b is approximately twice the individual belt widths of the first two belts 12a, whereby the contact areas on the one hand the two first belts 12a together and on the other hand the second belt 12b with both Drive wheel 8, the
  • Output gear 10 and in the non-operation of the belt transmission 7 with the tensioning wheel 1 1 forms, are substantially equal.
  • FIG 5 and 6 show two possible embodiments of a tensioning wheel 1 1 of a belt transmission 7 according to the invention.
  • the tensioning wheel 1 1 according to FIG. 5 is designed essentially as a simple solid cylinder.
  • two circumferential grooves 18 may be introduced, which is the recording of circumferential
  • boundary walls (not shown) by which the three belts 12a, 12b are kept positioned with respect to the longitudinal extent of the tensioning wheel 1 1. Corresponding boundary walls can also do this at the two
  • a tensioning wheel 1 1 according to FIG. 5 may be formed in a simple manner as a rotary member. For a reduction in the mass of such a tensioning wheel 1 1, this may also be partially or preferably hollow over the entire longitudinal extent and thus tubular.
  • the tensioning wheel 1 1 in contrast, comprises a shaft 19 and a respective roller 20 rotatably mounted on the shaft 19 for each of the belts 12a, 12b.
  • a longitudinal axial securing of the rollers 20 on the shaft 19 can be achieved, for example, by means of circumferential grooves of the shaft 19 engaging snap rings 21, as shown in FIG. 6.
  • a bearing of the rollers 20 on the shaft 19 can be via pivot bearing elements 22, such as roller bearings, done (see Fig .. 4).
  • a longitudinal axial securing of the belt on the individual rollers can again take place by means of end walls (not shown) attached to the individual rollers.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Power Steering Mechanism (AREA)

Abstract

La présente invention concerne un dispositif de transmission à courroie (7) comportant une roue motrice (8), une roue menée (10) et une roue de tension (11), qui est caractérisé par au moins deux courroies (12a, 12b), chacune entourant partiellement la roue motrice (8) et la roue menée (10) et, au moyen d'un brin, la roue de tension (11), une première courroie (12a) entourant la roue de tension (11) au moyen du brin associé, qui s'étend de la roue motrice (8) à la roue menée (10) dans une des directions circonférentielles, et la deuxième courroie (12b) entourant la roue de serrage (11) au moyen du brin associé s'étendant de la roue motrice (8) à la roue menée (10) dans l'autre direction circonférentielle. Une telle transmission à courroie (7) permet d'obtenir un angle d'enroulement relativement grand sur la roue motrice (8) et la roue menée (10) et, en conséquence, une ligne de transmission relativement large. En outre, la présente invention permet un serrage autobloquant indépendant de la direction de rotation des courroies (12a, 12b) obtenu en raison de l'action de l'autre courroie (12a, 12b) respective. Le guidage des courroies (12a, 12b) selon la présente invention permet en outre d'éviter un montage supplémentaire de la roue de serrage (11).
EP16805855.0A 2016-02-24 2016-12-06 Dispositif de transmission à courroie et système de direction Withdrawn EP3420249A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016103197.6A DE102016103197A1 (de) 2016-02-24 2016-02-24 Riemengetriebe und lenksystem
PCT/EP2016/079821 WO2017144134A1 (fr) 2016-02-24 2016-12-06 Dispositif de transmission à courroie et système de direction

Publications (1)

Publication Number Publication Date
EP3420249A1 true EP3420249A1 (fr) 2019-01-02

Family

ID=57482447

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16805855.0A Withdrawn EP3420249A1 (fr) 2016-02-24 2016-12-06 Dispositif de transmission à courroie et système de direction

Country Status (5)

Country Link
US (1) US20190084612A1 (fr)
EP (1) EP3420249A1 (fr)
CN (1) CN108700166B (fr)
DE (1) DE102016103197A1 (fr)
WO (1) WO2017144134A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11181172B2 (en) * 2018-06-14 2021-11-23 Mando Corporation Belt drive mechanism with gear back-up
CN110422227A (zh) * 2019-08-30 2019-11-08 辽宁工业大学 一种主动式可变转向系统及其控制方法

Family Cites Families (22)

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US1220304A (en) * 1916-05-04 1917-03-27 Renold Hans Ltd Belt-gearing attachment for roller-shafts.
US3534634A (en) * 1969-03-05 1970-10-20 Sanko Seisakusho Kk Power transmission device
JPS4934927Y1 (fr) * 1970-05-20 1974-09-21
US3941006A (en) * 1974-11-25 1976-03-02 Xerox Corporation Free floating belt tensioner
JPS5262781U (fr) * 1975-11-04 1977-05-09
EP0014243B1 (fr) * 1979-02-09 1984-06-13 Trützschler GmbH & Co. KG Entraînement pour une pluralité d'éléments tournants d'une carde
DE4114477C2 (de) 1991-05-03 2003-08-28 Claas Kgaa Mbh Keilriemenantrieb mit Spannvorrichtung
JPH0742801A (ja) * 1993-08-03 1995-02-10 Canon Inc 伝達機構
US6179740B1 (en) * 1999-06-02 2001-01-30 Moxee Innovations Corporation Dual-adjustable belt idler
JP2001241525A (ja) * 2000-02-25 2001-09-07 Fuminori Hirose 直線移動装置
DE10052275A1 (de) * 2000-10-20 2002-05-16 Mercedes Benz Lenkungen Gmbh Kraftfahrzeugservolenkung mit elektrischem Servomoto und Zahnriemen
CN1688472A (zh) * 2002-08-22 2005-10-26 日本精工株式会社 电动助力转向装置
WO2006138588A2 (fr) * 2005-06-16 2006-12-28 Moxee Innovations Corporation Dispositif de mise en tension
KR20070042632A (ko) 2005-10-19 2007-04-24 주식회사 만도 벨트식 전동장치 및 이를 구비한 자동차의 전기식 동력보조 조향장치
JP2007131034A (ja) * 2005-11-08 2007-05-31 Toyota Motor Corp 車両の操舵装置
KR100783355B1 (ko) * 2006-02-24 2007-12-10 주식회사 만도 코팅 풀리를 이용한 전동식 파워 스티어링 장치
US20090186726A1 (en) * 2008-01-22 2009-07-23 Gm Global Technology Operations, Inc. Belted alternator starter accessory drive tensioning system
US8182380B2 (en) * 2008-05-21 2012-05-22 Honda Motor Co., Ltd. Power transmission device
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US9700979B2 (en) * 2014-09-08 2017-07-11 Jpw Industries Inc. Belt tensioner for drill press
US20170306836A1 (en) * 2014-10-20 2017-10-26 Litens Automotive Partnership Endless drive arrangement with tensioning system and isolation device
DE102016100509B4 (de) * 2016-01-13 2020-07-02 Kleemann Gmbh Riemenspannvorrichtung

Also Published As

Publication number Publication date
WO2017144134A1 (fr) 2017-08-31
CN108700166B (zh) 2021-11-26
US20190084612A1 (en) 2019-03-21
DE102016103197A1 (de) 2017-08-24
CN108700166A (zh) 2018-10-23

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