WO2015054760A1 - Liaison anti-vibration pour timonerie de direction à deux essieux directeurs - Google Patents

Liaison anti-vibration pour timonerie de direction à deux essieux directeurs Download PDF

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Publication number
WO2015054760A1
WO2015054760A1 PCT/BR2013/000570 BR2013000570W WO2015054760A1 WO 2015054760 A1 WO2015054760 A1 WO 2015054760A1 BR 2013000570 W BR2013000570 W BR 2013000570W WO 2015054760 A1 WO2015054760 A1 WO 2015054760A1
Authority
WO
WIPO (PCT)
Prior art keywords
steering
arm
linking rod
axle
rod
Prior art date
Application number
PCT/BR2013/000570
Other languages
English (en)
Inventor
Luis Fernando de Mello WELIN
Original Assignee
Volvo Do Brasil Veículos Ltda.
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 Volvo Do Brasil Veículos Ltda. filed Critical Volvo Do Brasil Veículos Ltda.
Priority to BR112016008551-5A priority Critical patent/BR112016008551B1/pt
Publication of WO2015054760A1 publication Critical patent/WO2015054760A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D7/00—Steering linkage; Stub axles or their mountings
    • B62D7/22—Arrangements for reducing or eliminating reaction, e.g. vibration, from parts, e.g. wheels, of the steering system
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D7/00—Steering linkage; Stub axles or their mountings
    • B62D7/06—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins
    • B62D7/14—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering
    • B62D7/142—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering specially adapted for particular vehicles, e.g. tractors, carts, earth-moving vehicles, trucks
    • B62D7/144—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering specially adapted for particular vehicles, e.g. tractors, carts, earth-moving vehicles, trucks for vehicles with more than two axles

Definitions

  • This disclosure relates to a dual steer axle arrangement. More particularly this disclosure relates to an anti-vibration link for a linking rod connecting a steering mechanism associated with a forward steer axle to a steering mechanism associated with a rearward steer axle.
  • Some trucks are equipped with dual or twin front axles 5, 10, each carrying steerable front wheels.
  • a forward steer axle 5 is shown at the front end of the vehicle under the cab 3 and a rearward steer axle 10 is rearward of the forward steer axle, forward and rearward being relative to the vehicle.
  • the illustrated truck has a rear tandem axle arrangement 15, in which one or both of the axles are drive axles.
  • Twin front axles increase the load capacity of the truck and improve the weight distribution of the loaded truck between the front axles and the rear axles.
  • the forward steer axle 5 and rearward steer axle 10 include steerable wheels.
  • the steering system includes a steering mechanism, including a steering gear 20, a pitman arm 24, that converts a steering input from the steering wheel (not illustrated) into a force to move a steering linkage.
  • the forward axle 5 has associate with it a forward axle linking rod (also called a drag link) 33 that is moved by the pitman arm 24 and transmits that steering input to a forward axle steering arm 36.
  • An intermediate linking rod 32 is also connected to the pitman arm 24 to transmit movement to the rearward steer axle 10, by connection to a steering intermediate arm 28 that is supported on the vehicle frame 100.
  • the steering intermediate arm 28 shown in Figure 2 is a downward depending link that pivots on a horizontal axis 29 to transmit the steering input to the rearward axle steering mechanism, which includes a rearward axle linking rod 34 and a rearward axle steering arm 37.
  • a power assist piston 40 Extending rearward of the steering intermediate arm 28 and mounted to the frame 100 is a power assist piston 40 that uses hydraulics to assist the pivoting motion of the steering intermediate arm 28.
  • Figure 3 shows a dual steer axle steering arrangement with an alternative steering intermediate arm 200, as disclosed in PCT/BR2012/000544, filed December 28, 2012, and owned in common with the present application.
  • Figure 3 shows a steering gear 20, pitman arm 24, and forward axle drag link 33 that are the same as those elements shown in Figure 2.
  • the steering intermediate arm 200 of Figure 3 is arranged to pivot on a vertical axis 30 and includes an upper arm 205 that connects to the intermediate link 160 and a lower arm 210 that connects to a rear axle linking rod 180.
  • the linking arm 160 has a somewhat different bend pattern to accommodate the steering intermediate arm 200, but is otherwise similar to the linking arm 32 of Figure 2 and is subject to the similar vibrational issues.
  • the intermediate linking rod 32, 160 connecting the pitman arm 24, 140 with the steering intermediate arm 28, 200 is relatively long and has bends to allow it to connect between the pitman arm and steering intermediate arm and to fit into the allowed space.
  • the length results in reduced stiffness, subjecting the linking rod 32, 160 to undesirable vibrations, including vibrations caused by rotational movement around its axis defined by the end joints.
  • Current solutions include a small stop located at the ends of the intermediate linking rod.
  • the proposed design is the installation of an addition link to carry the lateral loads that act on the linking rod.
  • the invention is useful for steering arrangements as depicted in Figure 2 and 3, and also for other arrangements having a relatively long link connecting the forward axle steering mechanism to a rearward axle steering mechanism.
  • an additional link connects the linking rod and the frame so that lateral forces are transferred from the linking rod through the anti-vibration link to the frame rail.
  • the anti-vibration link may be a rigid rod connected to a first bracket mounted on the frame rail and connected to the linking rod by a second bracket.
  • the anti-vibration link is pivotably connected to the first bracket and second bracket by, for example, ball joints to allow horizontal and vertical pivoting movement.
  • the anti-vibration link is located as far as possible from an axis formed between the ball joints connecting the linking rod to the pitman arm and intermediate arm at opposite ends of the steering link.
  • a steering system for a vehicle having twin front steering axles supported on a vehicle frame includes a steering gear having a pitman arm for transmitting a steering input to linking rods, a first linking rod connecting the pitman arm and to a first axle steering arm, an intermediate linking rod connecting the pitman arm an intermediate steering arm mounted to the vehicle frame, a second linking rod connecting the intermediate steering arm to a second axle steering arm, and, an anti-vibration rod connected to the intermediate linking rod between the pitman arm and the intermediate steering arm and connected to the vehicle frame.
  • the anti-vibration rod is connected to the intermediate linking rod and the frame by ball joints.
  • the anti-vibration rod is connected to the second linking rod at a point distant from an axis defined by an end of the second link connecting to the pitman arm and an end of the second link connecting to the intermediate steering arm.
  • the anti-vibration rod is connected to the intermediate linking rod may include a damper element, such as resilient bushings in the joints.
  • the invention may be incorporated in a truck including a frame supporting a first front axle with steerable wheels and a second front axle with steerable wheels, an intermediate steering arm pivotably attached to the frame between the first front axle and the second front axle, a linking rod pivotally connected to the intermediate arm and extending toward the first axle, and, a link pivotally connected to the linking rod and to the frame.
  • the truck according to the invention may further include a second front axle linking rod pivotally connected to the intermediate arm and extending toward the second front axle.
  • Figure I is a prior art exemplary truck equipped with dual front steering axles
  • Figure 2 is a prior art steering system used in trucks with dual front steering axles
  • Figure 3 is a steering system for trucks with dual front steering axles showing an alternative intermediate arm
  • Figure 4 is simplified perspective view of a steering system of the present invention as attached to a truck frame rail
  • Figure 5 is an exemplary sectioned view of the steering system of the present invention, simplified and enlarged to show detail.
  • Figures 4 and 5 show a simplified steering system of the invention in relation to the underbody or frame of the truck.
  • the truck can include a set of frame rails (one frame rail 100 is illustrated) for supporting a truck body.
  • Figures 4 and 5 illustrate a steering intermediate arm 200 as shown in Figure 3, but it should be understood that the invention may be used with an arrangement as shown in Figure 2 or on any truck or similar vehicle with twin steer axles having an intermediate linking rod.
  • an axis substantially parallel to the longitudinal axis of the frame rail 100 defines the longitudinal or X-axis.
  • An axis substantially parallel with the wheel axles and orthogonal to the X-axis defines the transverse or Y-axis.
  • An axis which is substantially perpendicular to both the X-axis and the Y-axis defines the vertical or Z-axis.
  • FIG 4 a simplified view of the steering system is shown.
  • the pitman arm 24 is shown in space without the steering gear.
  • the intermediate linking rod 160 is connected at a forward end to the pitman arm 24 by a ball joint 165 or other connection allowing pivotal movement.
  • the intermediate linking rod 160 is connected at a rearward end to the steering intermediate arm 200 by a ball joint 205 or other connection allowing pivotal movement. Because of the bends in the steering intermediate arm 200 needed to accommodate the space available, it may be seen that the steering intermediate arm deviates from an axis 1 70 defined by the forward joint 165 and the rearward joint 205. Acceleration inputs from the ground surface as the vehicle moves produce vibration in the steering intermediate arm 200, which is undesirable.
  • an additional link 300 connects the intermediate linking rod 160 to the frame rail 100.
  • the additional link or anti-vibration link 300 is supported on the frame rail 100 by a bracket 310 and extends laterally, in a substantially horizontal plane, to the intermediate linking rod 160.
  • the anti-vibration link 300 may be connected to the intermediate linking rod 160 by a bracket 320. This arrangement positions the anti-vibration link 300 to counter vibrational loads on the intermediate linking rod 160.
  • the anti-vibration link 300 is connected to the frame bracket 310 and the intermediate linking rod bracket 320 by ball joints 3 1 5, 325.
  • Ball joints 3 15, 325 are advantageous as allowing pivoting movement in the horizontal plane and limited pivoting movement in the vertical plane.
  • a pin arrangement may be used if vertical movement is not necessary or is undesirable.
  • the anti-vibration rod 300 is connected to the intermediate linking rod 160 at a location spaced from the axis 170 defined by the forward ball joint 165 and rearward ball joint 205. More preferably, the anti-vibration rod 300 is connected to the intermediate linking rod 160 at a point that is furthest from the axis 1 70.
  • the anti-vibration rod 300 as illustrated is a rigid bar shaped at its ends to accommodate the ball joints 315, 325.
  • Other shapes may be used, including tubular members, cylindrical members

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Steering-Linkage Mechanisms And Four-Wheel Steering (AREA)

Abstract

Dispositif de direction pour deux essieux directeurs avant, comprenant une tige de liaison montée entre un levier de direction et un bras de direction intermédiaire. Un élément de liaison relie la tige de liaison au châssis du véhicule de façon à réduire les vibrations et mouvements indésirables dans la tige de liaison.
PCT/BR2013/000570 2013-10-17 2013-12-17 Liaison anti-vibration pour timonerie de direction à deux essieux directeurs WO2015054760A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
BR112016008551-5A BR112016008551B1 (pt) 2013-10-17 2013-12-17 Sistema de direção para um veículo

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201361892049P 2013-10-17 2013-10-17
US61/892,049 2013-10-17

Publications (1)

Publication Number Publication Date
WO2015054760A1 true WO2015054760A1 (fr) 2015-04-23

Family

ID=52827480

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/BR2013/000570 WO2015054760A1 (fr) 2013-10-17 2013-12-17 Liaison anti-vibration pour timonerie de direction à deux essieux directeurs

Country Status (2)

Country Link
BR (1) BR112016008551B1 (fr)
WO (1) WO2015054760A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106043423A (zh) * 2016-08-18 2016-10-26 安徽江淮汽车股份有限公司 一种双前桥汽车转向系统
CN106080762A (zh) * 2016-08-18 2016-11-09 安徽江淮汽车股份有限公司 一种双前桥汽车转向系统
CN106080768A (zh) * 2016-08-18 2016-11-09 安徽江淮汽车股份有限公司 一种双前桥汽车转向系统
EP3135563A1 (fr) * 2015-08-13 2017-03-01 Anadolu Isuzu Otomotiv sanayi ve Ticaret Anonim Sirketi Configuration de double barre intermédiaire de traction pour véhicules
CN107140015A (zh) * 2017-05-22 2017-09-08 安徽江淮汽车集团股份有限公司 一种双前桥汽车转向系统
CN108711290A (zh) * 2018-05-29 2018-10-26 广东泓胜科技股份有限公司 一种车辆超载非现场执法系统
EP3838718A1 (fr) * 2019-12-20 2021-06-23 Bombardier Transportation GmbH Système de direction pour un véhicule autonome

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3481620A (en) * 1967-11-14 1969-12-02 Hubert L Mccoy Four wheel steering arrangement for land vehicles
US4279428A (en) * 1979-08-14 1981-07-21 Toyota Jidosha Kogyo Kabushiki Kaisha Vibration absorbing device for motor vehicle
CN2753646Y (zh) * 2004-11-29 2006-01-25 东风汽车有限公司 一种双前桥汽车转向系统
WO2009072937A1 (fr) * 2007-12-06 2009-06-11 Volvo Lastvagnar Ab Dispositif de répartition de charge
US20110000735A1 (en) * 2008-02-29 2011-01-06 Peter Karlsson Steering linkage
EP2338764A1 (fr) * 2009-12-22 2011-06-29 Astra Veicoli Industriali S.p.A. Système de commande de direction pour véhicules avec un ou deux essieux directeurs

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3481620A (en) * 1967-11-14 1969-12-02 Hubert L Mccoy Four wheel steering arrangement for land vehicles
US4279428A (en) * 1979-08-14 1981-07-21 Toyota Jidosha Kogyo Kabushiki Kaisha Vibration absorbing device for motor vehicle
CN2753646Y (zh) * 2004-11-29 2006-01-25 东风汽车有限公司 一种双前桥汽车转向系统
WO2009072937A1 (fr) * 2007-12-06 2009-06-11 Volvo Lastvagnar Ab Dispositif de répartition de charge
US20110000735A1 (en) * 2008-02-29 2011-01-06 Peter Karlsson Steering linkage
EP2338764A1 (fr) * 2009-12-22 2011-06-29 Astra Veicoli Industriali S.p.A. Système de commande de direction pour véhicules avec un ou deux essieux directeurs

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3135563A1 (fr) * 2015-08-13 2017-03-01 Anadolu Isuzu Otomotiv sanayi ve Ticaret Anonim Sirketi Configuration de double barre intermédiaire de traction pour véhicules
CN106043423A (zh) * 2016-08-18 2016-10-26 安徽江淮汽车股份有限公司 一种双前桥汽车转向系统
CN106080762A (zh) * 2016-08-18 2016-11-09 安徽江淮汽车股份有限公司 一种双前桥汽车转向系统
CN106080768A (zh) * 2016-08-18 2016-11-09 安徽江淮汽车股份有限公司 一种双前桥汽车转向系统
CN107140015A (zh) * 2017-05-22 2017-09-08 安徽江淮汽车集团股份有限公司 一种双前桥汽车转向系统
CN108711290A (zh) * 2018-05-29 2018-10-26 广东泓胜科技股份有限公司 一种车辆超载非现场执法系统
CN108711290B (zh) * 2018-05-29 2021-02-02 广东泓胜科技股份有限公司 一种车辆超载非现场执法系统
EP3838718A1 (fr) * 2019-12-20 2021-06-23 Bombardier Transportation GmbH Système de direction pour un véhicule autonome

Also Published As

Publication number Publication date
BR112016008551A2 (fr) 2017-08-01
BR112016008551B1 (pt) 2021-08-31

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