WO2019101384A1 - Mecanisme de transmission pour un système de direction - Google Patents

Mecanisme de transmission pour un système de direction Download PDF

Info

Publication number
WO2019101384A1
WO2019101384A1 PCT/EP2018/074771 EP2018074771W WO2019101384A1 WO 2019101384 A1 WO2019101384 A1 WO 2019101384A1 EP 2018074771 W EP2018074771 W EP 2018074771W WO 2019101384 A1 WO2019101384 A1 WO 2019101384A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
transmission
axial direction
bevel
rack
Prior art date
Application number
PCT/EP2018/074771
Other languages
German (de)
English (en)
Inventor
Steffen Schwarzer
Christoph Lauzansky
Original Assignee
Robert Bosch 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 Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2019101384A1 publication Critical patent/WO2019101384A1/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
    • B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
    • B62D5/0409—Electric motor acting on the steering column
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F16H55/18—Special devices for taking up backlash
    • F16H55/20—Special devices for taking up backlash for bevel gears

Definitions

  • the invention relates to a transmission gear for a steering device and such a steering device, which is used in a motor vehicle.
  • a steering device or steering is used in vehicles
  • steering gear which are also referred to as transmission gear, used. These are especially in the
  • transmission or steering gear can be used to transfer from a steering handle, eg. A steering wheel, applied hand torque and applied by a servo motor auxiliary torque on a rack of a rack and pinion steering.
  • Document EP 1 006 040 B1 describes such a steering device which serves to turn steerable wheels of a motor vehicle.
  • This steering device comprises a manually rotatable input member, an output member, a
  • Torsionsstange connecting the input member and the output member, an electric motor and first and second intermeshing gears for
  • the First and second gears which represent the transmission gear, are a spiroid or worm gear set.
  • the transmission described has a first gear and a second gear, which mesh and cooperate for transmitting a torque, the torque to be transmitted can be applied by a driver to a steering handle manual torque and / or a provided by a servo or auxiliary motor auxiliary torque his.
  • This torque is introduced via the first gear, which may be formed as a worm, and transmitted to the second gear, which may be formed as a bevel gear. From this, in turn, the moment becomes a drive pinion for one
  • the second gear or bevel gear is mounted displaceably in the axial direction, wherein additionally at least one element for applying a contact pressure force is provided on the second gear or bevel gear, which acts in the axial direction towards the first gear.
  • the first gear and the second gear are arranged offset in axial direction to each other. Axis offset means that the axis of the first gear, typically the axis of rotation of the first gear, is not aligned with an axis of the second gear. This will be explained in more detail below in connection with FIG.
  • a bevel gear In a bevel gear, the axes do not run parallel to each other, but intersect.
  • the basic form of the bevel gear is a truncated cone whose outer surface is toothed. The teeth run regularly straight in the direction of the generatrices. In the case of the so-called hypoid wheel, however, they are curved.
  • the so-called hypoid gear is a modification of the bevel gear. In this, the axes of drive and ring gear are offset, therefore do not intersect.
  • Bevel gear which are also referred to as an angle gear, are used for transmitting rotational movements and torques.
  • Such bevel gear generally include input and output shafts whose axes usually have a common point of intersection.
  • hypoid gear Axis offset before, so this is referred to as hypoid gear.
  • hypoid bevel gearboxes the associated rolling and sliding movements promote higher gear ratios and thus better efficiencies.
  • Curved bevel gears are, for example, bevel gears and Hypoidkegeltex.
  • the transmission transmission described is characterized by the fact that instead of a worm-gear mesh, a hypoid wheel can be combined with a worm. This has the consequence that a lateral, ie an axial rather than a radial engagement situation of the meshing wheels can be achieved. In addition, a misalignment shift made without correcting the teeth and thus installation space can be saved.
  • Hypoid bevel gears are a form of spiral bevel gears. These are characterized by the fact that the pinion and crown gear axes do not converge in one point. This means that the pinion axis is offset from the wheel axis in height. This offset is referred to as offsetting.
  • the pinion Due to the axial offset, the pinion has a larger spiral angle than the ring gear. The resulting from the larger spiral angle larger
  • Forehead module causes an enlargement of the pitch circle diameter of the hypoid pinion. This results in a higher load capacity of a hypoid gearbox compared to a spiral bevel gear. Therefore, the decrease
  • a worm-gear worm gear is provided with a hypoid gear as a bevel gear in combination with a Anfederungselement as an element for applying a contact force, which presses the hypoid wheel axially to the worm and in this way a
  • the presented steering device has at least one transmission gear described above and is used in particular in a motor vehicle.
  • Hand torque which is applied to a steering handle, and / or a transmission gear for transmitting a servo torque, which is provided by a servo motor may be provided.
  • the presented transmission gear has, at least in some of
  • Figure 1 shows a steering device according to the prior art.
  • FIG. 2 shows a detail from FIG. 1.
  • Figure 3 shows an embodiment of the proposed transmission gear.
  • FIG. 4 shows another embodiment of the transmission gear described.
  • FIG. 5 shows a further embodiment of the transmission gear.
  • Figure 1 shows a known steering device, which is generally designated by the reference numeral 10.
  • the illustration shows a rack 12, a steering shaft 14 leading to a steering handle (not shown), a servomotor 16, and a transmission gear 18.
  • This transmission gear 18 transmits the assist torque provided by the servomotor 16 to the rack 12
  • Transmission gear 18 transmits a rotational movement, which in turn is translated into a translational movement of the rack 12.
  • the transmission gear shown in Figure 1 18 is shown enlarged in Figure 2.
  • the illustration shows a worm 30, via which the moment of the servomotor is initiated.
  • the worm 30 cooperates with a bevel gear 32, which in turn typically translates the rack via a drive pinion.
  • Transmission gear as presented herein, given. This mode of operation is referred to in the transmission transmission presented.
  • the transmission gear 18 of Figure 2 has two compensating elements 34 which serve as springing and on the worm 30 and thus on the element which introduces the force applied by the servo motor or the applied torque in the transmission gear 18, attack.
  • this springing has the disadvantages mentioned above.
  • FIG 3 shows an embodiment of the proposed transmission gear, which is designated overall by the reference numeral 50.
  • This transmission gear 50 can basically be used in a steering device 10, as shown in FIG.
  • the illustration shows a worm 52 which is provided with a bevel gear 54
  • the worm 52 is thus an embodiment of a gear and represents the element or the component, via which a moment, for example.
  • a servo motor or a steering handle applied in the
  • Transmission gear 50 is introduced or introduced.
  • the bevel gear 54 which cooperates with the worm 52, is connected to a drive pinion 56 whose rotary motion in turn is a rack (not shown).
  • This rack causes by their translational movement pivoting of the hinged wheels.
  • the drive pinion 56 is mounted in a housing 58 by means of two bearings 60. These bearings 60 are typically designed as ball bearings.
  • the illustration also shows an element 62 for applying a
  • the element 62 for applying a contact pressure comprises a first spring 64, which is associated with a first damper member 66, and a second spring 68, which is associated with a second damping member 70.
  • the element 62 for applying a contact pressure force can have a spring element to which an attenuation element is assigned. The spring element acts on the path of the bevel gear 54, the
  • Damper acts on the speed of the bevel gear 54.
  • the element 62 acts to apply a contact force on the bevel gear 54 and not on the worm 52.
  • Figure 4 shows a further embodiment of the transmission gear, which is generally designated by the reference numeral 100.
  • the illustration shows a first gear 102, which is formed in this case as a worm, and a second gear 104, which is designed here as a bevel gear.
  • This second gear 104 may be formed as a spiroid, hypoid, globoid, conical or crown wheel.
  • the two gears 102, 104 cooperate, so that an initiated by the first gear 102 torque is transmitted to the second gear 104.
  • the illustration also shows a bearing 106 for an output shaft 108, which is fixedly connected to the second gear 104 and derives the torque transmitted to this second gear 104.
  • a toothing 110 of the second gear 104, springs 112, attenuators 114 and a rack 116 of a steering device can be seen, wherein the rack 116 cooperates with a transmission member 118 of the output shaft 108.
  • the teeth 110 may be arcuate, oblique or straight toothed.
  • An arcuate toothing is provided, for example, in a hypoid wheel.
  • a hypoid wheel as a second gear 104 also allows the use of an axially parallel screw as the first gear 102.
  • the springs 112 which serve as springing, it should be noted that the following applies:
  • F c * s, where F is the force, c the spring constant and s the spring travel, which is also illustrated here with a double arrow 120.
  • the attenuators 114 are here and act parallel to the springs 112.
  • Springs 112 and attenuators 114 may be formed as separate components but also as a combined component.
  • a layer of an elastomeric material can be used, which has both resilient and damping properties.
  • the spring acts on the way, the attenuator on the speed.
  • a rotation axis 130 of the first gear 102 and an axis of rotation 132 of the second gear 104 is shown. Perpendicular to the axis of rotation 132 of the second gear 104 is a longitudinal axis 134 of the second gear 104. It can be seen that the axis of rotation 130 of the first gear does not intersect this longitudinal axis 134 is not in alignment with this, but is offset to this, as with a double arrow 136 is illustrated. The two gears 102 and 104 are thus arranged offset in axial direction to each other.
  • Reference numeral 140 denotes a displacement possibility, for example, a
  • FIG. 5 shows yet another embodiment of the transmission, which is designated overall by the reference numeral 200.
  • the illustration shows a first gear 202, which is formed in this case as a worm, and a second gear 204, which here, for example, as a crown wheel, spiroid or hypoid wheel is formed as.
  • the two gears 202, 204 cooperate, so that an initiated by the first gear 202 torque is transmitted to the second gear 204.
  • the illustration also shows a bearing 206 for an output shaft 208, which is fixedly connected to the second gear 204 and the second
  • Gear 204 derived torque derived. Furthermore, a toothing 210 of the second gear 204, springs 212, attenuators 214 and a rack 216 of a steering device can be seen, wherein the rack 216 with a transmission member 218 of the output shaft 208 cooperates.
  • Reference numeral 240 denotes a displacement possibility, for example a sliding seat.

Abstract

L'invention concerne un mécanisme de transmission comportant une premier engrenage et un deuxième engrenage, qui coopèrent pour transmettre un moment, lequel moment doit être introduit via le premier engrenage et transmis de ce deuxième engrenage à un pignon d'entraînement (56) pour crémaillère, l'axe longitudinal du second engrenage définissant une direction axiale, le second engrenage étant monté coulissant dans le sens axial. Il est prévu en outre au moins un élément (62) pour appliquer une force de contact au second engrenage, qui agit dans le sens axial en direction du premier engrenage et le premier engrenage et le deuxième engrenage sont disposés de manière décalée l'un par rapport à l'autre.
PCT/EP2018/074771 2017-11-23 2018-09-13 Mecanisme de transmission pour un système de direction WO2019101384A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017220951.8A DE102017220951A1 (de) 2017-11-23 2017-11-23 Übertragungsgetriebe für eine Lenkeinrichtung
DE102017220951.8 2017-11-23

Publications (1)

Publication Number Publication Date
WO2019101384A1 true WO2019101384A1 (fr) 2019-05-31

Family

ID=63667882

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2018/074771 WO2019101384A1 (fr) 2017-11-23 2018-09-13 Mecanisme de transmission pour un système de direction

Country Status (2)

Country Link
DE (1) DE102017220951A1 (fr)
WO (1) WO2019101384A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2228461A (en) * 1989-01-30 1990-08-29 Jidosha Kiki Co Electric power steering apparatus
US5165495A (en) * 1990-03-28 1992-11-24 Jidosha Kiki Co., Ltd. Electrically driven power steering apparatus
US5213173A (en) * 1990-10-26 1993-05-25 Jidosha Kiki Co., Ltd. Electric power steering apparatus
EP1006040B1 (fr) 1998-12-04 2004-06-09 TRW Automotive U.S. LLC Direction assistée électrique

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL6607931A (fr) * 1966-06-08 1967-12-11
JPH06257660A (ja) * 1993-03-03 1994-09-16 Nagaoka Haguruma Seisakusho:Kk 歯車伝達機構
JP2001159451A (ja) * 1999-11-30 2001-06-12 Toyota Motor Corp 傘状歯車機構
JP2001165246A (ja) * 1999-12-08 2001-06-19 Asano Gear Co Ltd 歯車減速装置
JP2004340367A (ja) * 2003-04-25 2004-12-02 Thk Co Ltd ハイポイドギア装置
JP2007168613A (ja) * 2005-12-22 2007-07-05 Toyota Motor Corp 電動式パワーステアリング装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2228461A (en) * 1989-01-30 1990-08-29 Jidosha Kiki Co Electric power steering apparatus
US5165495A (en) * 1990-03-28 1992-11-24 Jidosha Kiki Co., Ltd. Electrically driven power steering apparatus
US5213173A (en) * 1990-10-26 1993-05-25 Jidosha Kiki Co., Ltd. Electric power steering apparatus
EP1006040B1 (fr) 1998-12-04 2004-06-09 TRW Automotive U.S. LLC Direction assistée électrique

Also Published As

Publication number Publication date
DE102017220951A1 (de) 2019-05-23

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