WO2007058572A1 - Dispositif de suspension pour composant de vehicule - Google Patents

Dispositif de suspension pour composant de vehicule Download PDF

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Publication number
WO2007058572A1
WO2007058572A1 PCT/SE2005/001741 SE2005001741W WO2007058572A1 WO 2007058572 A1 WO2007058572 A1 WO 2007058572A1 SE 2005001741 W SE2005001741 W SE 2005001741W WO 2007058572 A1 WO2007058572 A1 WO 2007058572A1
Authority
WO
WIPO (PCT)
Prior art keywords
suspension device
support structure
link
vehicle
link mechanism
Prior art date
Application number
PCT/SE2005/001741
Other languages
English (en)
Inventor
Göran ELIASSON
Original Assignee
Volvo Construction Equipment Holding Sweden Ab
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 Construction Equipment Holding Sweden Ab filed Critical Volvo Construction Equipment Holding Sweden Ab
Priority to PCT/SE2005/001741 priority Critical patent/WO2007058572A1/fr
Publication of WO2007058572A1 publication Critical patent/WO2007058572A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D33/00—Superstructures for load-carrying vehicles
    • B62D33/08—Superstructures for load-carrying vehicles comprising adjustable means
    • B62D33/10—Superstructures for load-carrying vehicles comprising adjustable means comprising means for the suspension of the superstructure on the frame
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
    • B60N2/24—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles for particular purposes or particular vehicles
    • B60N2/38—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles for particular purposes or particular vehicles specially constructed for use on tractors or like off-road vehicles
    • B60N2/39—Seats tiltable to compensate for roll inclination of vehicles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
    • B60N2/50—Seat suspension devices
    • B60N2/506—Seat guided by rods
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
    • B60N2/50—Seat suspension devices
    • B60N2/54—Seat suspension devices using mechanical springs
    • B60N2/544—Compression or tension springs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D33/00—Superstructures for load-carrying vehicles
    • B62D33/06—Drivers' cabs
    • B62D33/0604—Cabs insulated against vibrations or noise, e.g. with elastic suspension

Definitions

  • the present invention relates to a suspension device for suspending a vehicle component above a vehicle frame, wherein the suspension device comprises at least one link mechanism adapted to connect an upper support structure of the vehicle component to a lower support structure, which is connected to the vehicle frame, in such a manner that the upper support structure is permitted to pivot relative to the lower support structure.
  • the vehicle component may be formed by a driver seat or a cab.
  • the suspension device is primarily directed to a suspension device for a vehicle operating in difficult terrain on an uneven ground.
  • Such vehicles are commonly referred to as work vehicles.
  • the term work vehicle comprises different types of material handling vehicles like construction machines, such as an articulated hauler, a wheel loader, a backhoe loader, a motor grader and an excavator.
  • the suspension should be capable of reducing/eliminating relatively powerful vibrations, shocks, side accelerations etc during operation.
  • the invention may also be applied in other types of off-the-road type of vehicles like industrial tractors and trucks.
  • the invention will below be discussed for an articulated hauler. This should be regarded as a non-limiting example.
  • articulated haulers also called dumpers
  • Such vehicles may be operated with large and heavy loads in areas where there are no roads, for example for transports in connection with road or tunnel building, sand pits, mines and similar environments.
  • EP 0 542 618 discloses a vehicle seat suspension.
  • a compression spring is arranged between an upper support structure, on which an operator seat is mounted, and a lower support structure.
  • the compression spring transmits a load from the weight of the operator seat to the lower support structure.
  • Front and rear link arms pivotally connect the upper support structure and the lower support structure for guiding a movement of the seat along an arcuate path.
  • the seat suspension is designed for a floating movement of the seat in the fore-to-aft direction.
  • a purpose of the invention is to provide a suspension device which improves the conditions for a driver during operation in difficult terrain.
  • suspension device for suspending a vehicle component above a vehicle frame
  • the suspension device comprises at least one link mechanism adapted to connect an upper support structure of the vehicle component to a lower support structure, which is connected to the vehicle frame, in such a manner that the upper support structure is permitted to pivot relative to the lower support structure
  • the link mechanism is designed such that the vehicle component is permitted to pivot back and forth in a lateral direction of the vehicle frame.
  • the vehicle component is permitted to pivot back and forth in a direction perpendicular to a lengthwise direction of the vehicle frame.
  • This design creates conditions for carrying loads transferred to the vehicle component as a result of side accelerations arising during operation in difficult terrain, especially on an uneven ground.
  • the link mechanism is adapted so that the upper support structure is located in a base position relative to the lower support structure, and that the vehicle component is permitted to pivot along an arcuate path through the base position in the lateral direction.
  • the vehicle component is located in the base position when the vehicle is substantially not subjected to loads with regard to side accelerations. Such a situation occurs when the vehicle is at rest, ie not moving, or moving on an even ground. Further, the vehicle component will pivot along said arcuate path defined by the link mechanism when the vehicle is subjected to side loads.
  • the link mechanism is preferably configured so that a potential energy of the vehicle component is increased when the upper support structure is moved from the base position along said arcuate path.
  • the base position forms a lowest possible position for the vehicle component relative to the lower support structure. When the vehicle component is subjected to the side loads, it will swing/rock sideways and upwards along the arcuate path and then return to the base position again.
  • the link mechanism is designed such that the vehicle component is also permitted to pivot back and forth in a lengthwise direction of the vehicle frame.
  • the link mechanism for taking care of the movements in the longitudinal direction is preferably designed with link members in a similar way as the link members for taking care of the movements in the lateral direction. In this way, the vehicle component is permitted to pivot both sideways and for-to-aft during operation.
  • the link mechanism is adapted to transmit a load from the weight of the vehicle component to the lower support structure.
  • the link mechanism is adapted to transfer the load from the weight of the vehicle component.
  • a link member of the link mechanism is arranged to be subjected to a tensile force from said weight load.
  • FIG 1 discloses an articulated hauler in a perspective front view
  • FIG 2 schematically discloses driver seat suspension in a front view according to a first embodiment
  • FIG 3 schematically discloses a driver seat suspension in a front view according to a second embodiment
  • FIG 4 schematically discloses a driver seat suspension in a side view according to a third embodiment
  • FIG 5 schematically discloses a driver seat suspension in a front view according to a fourth embodiment
  • FIG 6 discloses the driver seat suspension of figure 5 in a side view
  • FIG 7 discloses the driver seat suspension of figure 5 and 6 in an exploded, perspective view
  • FIG 8 discloses a driver seat suspension in an exploded, perspective view according to a fifth embodiment
  • FIG 9 discloses a vehicle cab suspension in an exploded view according to a first embodiment.
  • Figure 1 discloses a frame-steered work vehicle in the form of an articulated hauler 1 in a perspective front view.
  • the articulated hauler 1 comprises a forward vehicle section 2, a so-called engine unit, which in turn comprises a forward frame and an engine.
  • the articulated hauler 1 further comprises a rear vehicle section 3, a so-called load-carrying unit, which in turn comprises a rear frame and a tiltably arranged container 4 for carrying loads.
  • the frame of the engine unit 2 is connected to the frame of the load-carrying unit 3 by means of a special articulation joint allowing the engine unit and the load-carrying unit to pivot in relation to each other about an imaginary longitudinal axis, i.e an axis extending in the longitudinal direction of the vehicle.
  • the articulated hauler 1 travels over an uneven ground and the engine unit 2 is accordingly pivoted with regard to the load- carrying unit 3.
  • the frame of the engine unit 2 is connected to the frame of the load-carrying unit 3 by means of a further articulation joint which allows pivoting about a vertical axis for steering the vehicle by means of hydraulic cylinders (not shown) .
  • FIG. 2 discloses a working principle of a driver seat suspension device 5.
  • the suspension device 5 comprises a left and right link mechanism 6, 7 adapted to connect an upper support structure 8 of a vehicle seat 9 to a lower support structure 10, which is connected to a vehicle frame (not shown) , in such a manner that the upper support structure 8 is permitted to pivot relative to the lower support structure 10.
  • the driver seat 9 is rigidly mounted to the upper support structure 8.
  • the link mechanisms 6,7 are designed such that the driver seat 9 is permitted to pivot back and forth in a lateral direction of the vehicle frame.
  • said link mechanisms 6, 7 are arranged at a distance from each other in the lateral direction.
  • each link mechanism 6, 7 forms a pivot arrangement .
  • Each link mechanism 6, 7 comprises a first link member 11,12 rigidly connected to the upper support structure 8, a second link member 13,14 rigidly connected to the lower support structure 10 and an intermediate link member 15,16 pivotably connecting the first and second connection member 11, 12 and 13, 14, respectively. More specifically, the intermediate link member 15, 16 is connected to the first and second link member 15, 16, respectively, via a hinge joint.
  • the link members
  • the intermediate link member 15, 16 is arranged to be subjected to a tensile force from a weight load of the driver seat (and the weight of the driver) .
  • the intermediate link members 15, 16 are arranged substantially at right angles with regard to the upper and lower support structures 8,10, ie substantially vertically.
  • the driver seat 9 will thereby be maintained in an upright position when the link mechanism is pivoted (compare with the design of figure 3) . in other words, the driver seat will be maintained in a position at right angles with the lower support structure 10.
  • a pivot joint 17, 18 of the first link member 11, 12 is positioned below a pivot joint 19, 20 of the second link member 13, 14.
  • Said intermediate link member 15, 16 is pivotably connected at a first end to the first link member 11, 12 and at a second end to the second link member 13, 14.
  • the link mechanisms 6, 7 are adapted so that the upper support structure 8 (and thereby also the seat 9) is located in a set base position, see figure 2, relative to the lower support structure 10 when the driver is located in the seat and the vehicle is at rest.
  • the base position defines a normal driving position for the driver seat 9.
  • the set base position is at a set distance from the lower support structure 10.
  • the base position is further independent of a weight of the vehicle seat and any vertical load exerted on the seat from the driver.
  • the vehicle seat 9 is permitted to pivot along an arcuate path, see arrows 21, 22, through the base position in the lateral direction.
  • the link mechanisms 6, 7 are configured so that a potential energy of the vehicle seat (and driver) is increased when the upper support structure 8 is moved from the base position along said arcuate path.
  • the link mechanism is designed such that the base position coincides with the position closest to the lower support structure along the arcuate path. In other words, the base position forms a lowest possible position from which the seat is permitted to rock sideways and upwards along the arcuate path.
  • the link mechanisms 6, 7 form a type of cradle for the driver seat 9 in the lateral direction.
  • the length of the link arms 11, 13, 15 with regard to each other in each link mechanism may have a different relation than the one exemplified in figure 2. With different such designs, a force for returning the seat to the initial, upright postion can be varied. Thus, the link mechanisms may be designed differently for different type of vehicles and/or applications. Short link arms will give a large return force due to that the seat 9 has to be moved a relatively long distance for a small lateral movement. Long link arms will have an opposite effect.
  • Figure 3 shows an alternative embodiment of a driver seat suspension 105 to the one shown in figure 2.
  • the intermediate link members 115, 116 are arranged in an inclined, oblique, position with regard to the upper and lower support structures 8,10, ie non-vertically.
  • the driver seat 9 will thereby be inclined from its upright position when the link mechanism is pivoted (compare with the design of figure 2) .
  • the driver seat will be inclined, ie oblique, with regard to the lower support structure 10 during operation.
  • the base position does not coincide with the lowest possible position along the arcuate path. Instead, the link mechanism is designed such that the base position is at a distance sideways from the lowest possible position along the arcuate path.
  • the link mechanism is designed such that the base position is at a distance from the position closest to the lower support structure along the arcuate path.
  • the base position of the left link mechanism 106 is to the left of the lowest possible position along the arcuate path and the right link mechanism 107 is to the right of the lowest possible position along the arcuate path.
  • FIG. 4 discloses a further working principle of a driver seat suspension device 205.
  • the suspension device 205 comprises a rear and forward link mechanism 206, 207 adapted to connect the upper support structure 8 to the lower support structure 10.
  • the link mechanisms 206, 207 are designed such that the driver seat 9 is permitted to pivot back and forth in a longitudinal direction (ie backwards/forwards) of the vehicle frame (not shown) .
  • said link mechanisms 206, 207 are arranged at a distance from each other in the longitudinal direction of the vehicle.
  • the link mechanisms 206, 207 have a similar design as the one shown in figure 3.
  • the intermediate link members 215, 216 are arranged in an inclined, oblique, position with regard to the upper and lower support structures 8,10, ie non-vertically.
  • the driver seat 9 will thereby be inclined from its upright position when the link mechanism is pivoted (see dashed lines) .
  • the driver seat will be inclined, ie oblique, with regard to the lower support structure 10 during operation.
  • the base position does not coincide with the lowest possible position along the arcuate path. Instead, the link mechanism is designed such that the base position is at a distance in the longitudinal direction from the lowest possible position along the arcuate path.
  • the link mechanism 206, 207 is designed such that the base position is at a distance from the position closest to the lower support structure 10 along the arcuate path.
  • the link mechanisms 206, 207 form a type of cradle for the driver seat 9 in the forwards direction.
  • the base position of the rear link mechanism 206 is rearwards of the lowest possible position along the arcuate path and the forward link mechanism 207 is forwards of the lowest possible position along the arcuate path.
  • a driver seat suspension 305 according to a fourth embodiment is shown.
  • the suspensions 105 and 205 of figure 3 and 4 are combined so that both the function of rocking back and forth in the lateral direction and in the longitudinal direction are achieved.
  • the suspension 105 permitting movement in the lateral direction and the suspension 205 permitting movement in the longitudinal direction are arranged on top of each other.
  • An intermediate support structure 23 forms a lower support structure for the upper suspension 105 and an upper support structure for the lower suspension.
  • a centering spring 24, 25, 26, 27 is arranged for returning the link mechanism to its base position.
  • the centering spring 24, 25 is connected to the first connection member 111, 112 and the intermediate support structure 23.
  • the centering spring 26, 27 is connected to the first connection member 211, 212 and the lower support structure 10.
  • a dampener 28, 29, 30, 31 is arranged for dampening the 5 motion of the link mechanism.
  • the dampener 28, 29 is connected to the first connection member 111, 112 and the intermediate support structure 23.
  • the dampener 30, 31 is connected to the first connection member 211, 212 and the lower support structure 10.
  • a pair of one centering spring and one dampener is 5 arranged in parallel to each other between each one of the link members and one of the support structures.
  • FIG 7 the suspension 305 of figures 5 and 6 is illustrated in a schematic, exploded view.
  • a frame 32 0 comprising two parallel frame rails 33, 34 is shown.
  • a cab floor 35 is connected to the frame 32.
  • the suspension 305 is adapted to be mounted on top of the cab floor 35, see fasteners 36.
  • the upper support structure 8 is adapted to be rigidly connected to a -5 lower portion of the seat 9, see fasteners 37.
  • the suspension 105 permitting movement in the lateral direction comprises four link mechanisms, one at each corner of the driver seat 9.
  • the 0 suspension 205 permitting movement in the longitudinal direction comprises four link mechanisms, one at each corner of the driver seat 9.
  • a driver seat suspension 405 in an according to a fifth embodiment is disclosed in an exploded view.
  • the suspension 405 comprises four link mechanisms, one at each corner of the driver seat 9.
  • a single link mechanism 406,407 of the driver seat suspension 405 is configured to allow both pivoting back and forth in a lengthwise direction of the vehicle frame 32 and back and forth in a lateral direction of the vehicle frame 32.
  • each link mechanism comprises two ball joints, see enlarged portion.
  • the intermediate link member is connected to the ball of each ball joint.
  • a cab suspension 505 is disclosed.
  • the cab suspension 505 comprises the same parts as the driver seat suspension 405 discussed above with regard to figure 8.
  • a cab 38 is connected to the upper support structure 8.
  • the lower support structure 10 is connected to the frame 38.
  • suspension 505 for the cab 38, shown in figure 9, comprising the ball joints may be replaced by the two suspensions on top of each other shown in figure 5-7.

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  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Seats For Vehicles (AREA)

Abstract

Cette invention concerne un dispositif de suspension destiné à suspendre un composant de véhicule (9) au-dessus d’un châssis de véhicule. Le dispositif de suspension comprend au moins un mécanisme de liaison (106, 107) conçu pour raccorder une structure de support supérieure (8) du composant à une structure de support inférieure (10), qui est solidaire du châssis, de sorte que la structure de support supérieure puisse pivoter par rapport à celle inférieure. Le mécanisme de liaison (106, 107) est conçu pour permettre au composant de véhicule (9) de pivoter vers l’avant et l’arrière dans un sens latéral.
PCT/SE2005/001741 2005-11-18 2005-11-18 Dispositif de suspension pour composant de vehicule WO2007058572A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/SE2005/001741 WO2007058572A1 (fr) 2005-11-18 2005-11-18 Dispositif de suspension pour composant de vehicule

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/SE2005/001741 WO2007058572A1 (fr) 2005-11-18 2005-11-18 Dispositif de suspension pour composant de vehicule

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WO2007058572A1 true WO2007058572A1 (fr) 2007-05-24

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WO (1) WO2007058572A1 (fr)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2420404A1 (fr) * 2010-08-18 2012-02-22 Grammer Ag Dispositif d'oscillation de véhicule pour sièges de véhicule ou cabines de véhicule
DE102010053752A1 (de) * 2010-12-08 2012-06-14 Grammer Aktiengesellschaft Fahrzeugschwingungsvorrichtung für Fahrzeugsitze oder Fahrzeugkabinen
DE102011013122A1 (de) * 2011-03-04 2012-09-06 Grammer Aktiengesellschaft Hebelmechanismus für Dämpferverstellung für Horizontalfederung
DE102012102574A1 (de) * 2012-03-26 2013-09-26 Dornier Technologie Gmbh & Co. Kg Lagerungsvorrichtung
WO2014176130A1 (fr) * 2013-04-23 2014-10-30 Bose Corporation Système de siège pour un véhicule
US8926012B2 (en) 2010-08-31 2015-01-06 Grammer Ag Vehicle seats for vehicles
US8960802B2 (en) 2010-11-29 2015-02-24 Grammer Ag Vehicle seat with guided scissor arms
US8973967B2 (en) 2011-09-15 2015-03-10 Grammer Ag Vehicle seat, motor vehicle and method for spring-mounting a vehicle seat
US9376042B2 (en) 2010-08-04 2016-06-28 Grammer Ag Horizontal springing device for vehicle seats with elastomer spring element with progressive spring characteristic curve
DE102015121765A1 (de) * 2015-12-14 2017-06-14 Grammer Ag Fahrzeugschwingungsvorrichtung
EP3181396A1 (fr) * 2015-12-14 2017-06-21 Grammer Ag Dispositif de vibration de véhicule
US10065541B2 (en) 2015-08-10 2018-09-04 Grammer Ag Horizontal vibration device for a vehicle seat
FR3066723A1 (fr) * 2017-05-24 2018-11-30 Patrick Edouard Sajous Vehicule muni d'un systeme mobile afin d'ameliorer la stabilite de l'ensemble vehicule et charge
DE102019134244A1 (de) * 2019-12-13 2021-06-17 Grammer Aktiengesellschaft Fahrzeugsitz mit Scherengestellanordnung
US11279271B2 (en) 2019-12-13 2022-03-22 Grammer Ag Vehicle seat having a suspension unit for cushioning rolling and vertical suspension movements
US11285846B2 (en) 2019-12-13 2022-03-29 Grammer Ag Vehicle seat with scissor frame arrangement
US12005821B2 (en) 2019-12-13 2024-06-11 Grammer Ag Cushioning rolling and vertical suspension movements

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US3882956A (en) * 1970-06-18 1975-05-13 Chausson Usines Sa Suspension device for vehicle drivers cab
GB1432614A (en) * 1972-04-12 1976-04-22 Alden L A G Parallelsyst Seats for tractors and other vehicles
US5437494A (en) * 1992-10-29 1995-08-01 Life Force Associates, L.P. Rearward moving seat
US5449218A (en) * 1988-01-07 1995-09-12 Life Force, Inc. Vehicle safety device
US5950489A (en) * 1996-10-02 1999-09-14 Neway Anchorlok International, Inc. Variable geometry linkage configuration

Patent Citations (5)

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Publication number Priority date Publication date Assignee Title
US3882956A (en) * 1970-06-18 1975-05-13 Chausson Usines Sa Suspension device for vehicle drivers cab
GB1432614A (en) * 1972-04-12 1976-04-22 Alden L A G Parallelsyst Seats for tractors and other vehicles
US5449218A (en) * 1988-01-07 1995-09-12 Life Force, Inc. Vehicle safety device
US5437494A (en) * 1992-10-29 1995-08-01 Life Force Associates, L.P. Rearward moving seat
US5950489A (en) * 1996-10-02 1999-09-14 Neway Anchorlok International, Inc. Variable geometry linkage configuration

Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9376042B2 (en) 2010-08-04 2016-06-28 Grammer Ag Horizontal springing device for vehicle seats with elastomer spring element with progressive spring characteristic curve
EP2420404A1 (fr) * 2010-08-18 2012-02-22 Grammer Ag Dispositif d'oscillation de véhicule pour sièges de véhicule ou cabines de véhicule
DE102010034857B4 (de) * 2010-08-18 2021-01-28 Grammer Aktiengesellschaft Fahrzeugschwingungsvorrichtung für Fahrzeugsitze
US8607910B2 (en) 2010-08-18 2013-12-17 Grammer Ag Vehicle suspension device for vehicle seats or vehicle cabs
US8926012B2 (en) 2010-08-31 2015-01-06 Grammer Ag Vehicle seats for vehicles
US8960802B2 (en) 2010-11-29 2015-02-24 Grammer Ag Vehicle seat with guided scissor arms
DE102010053752A1 (de) * 2010-12-08 2012-06-14 Grammer Aktiengesellschaft Fahrzeugschwingungsvorrichtung für Fahrzeugsitze oder Fahrzeugkabinen
EP2463146A3 (fr) * 2010-12-08 2013-01-23 Grammer Ag Dispositif d'oscillation de véhicule pour sièges de véhicule ou cabines de véhicule
US9266452B2 (en) 2010-12-08 2016-02-23 Grammer Ag Vehicle vibration device for vehicle seats or vehicle cabs
EP2495126A3 (fr) * 2011-03-04 2013-07-03 Grammer Ag Mécanisme de levier pour réglage de la vapeur pour suspension horizontale
US8960691B2 (en) 2011-03-04 2015-02-24 Grammer Ag Apparatus and method for damper adjustments for a horizontal suspension
CN102673451B (zh) * 2011-03-04 2015-11-25 格拉默股份公司 一种车辆振动装置
CN102673451A (zh) * 2011-03-04 2012-09-19 格拉默股份公司 一种用于调节水平减震的减震器的杠杆机构
DE102011013122A1 (de) * 2011-03-04 2012-09-06 Grammer Aktiengesellschaft Hebelmechanismus für Dämpferverstellung für Horizontalfederung
US8973967B2 (en) 2011-09-15 2015-03-10 Grammer Ag Vehicle seat, motor vehicle and method for spring-mounting a vehicle seat
DE102012102574A1 (de) * 2012-03-26 2013-09-26 Dornier Technologie Gmbh & Co. Kg Lagerungsvorrichtung
WO2014176130A1 (fr) * 2013-04-23 2014-10-30 Bose Corporation Système de siège pour un véhicule
CN105246737A (zh) * 2013-04-23 2016-01-13 伯斯有限公司 用于车辆的座位系统
US10046677B2 (en) 2013-04-23 2018-08-14 Clearmotion Acquisition I Llc Seat system for a vehicle
CN109606216A (zh) * 2013-04-23 2019-04-12 伯斯有限公司 用于车辆的座位系统
US10245984B2 (en) 2013-04-23 2019-04-02 ClearMotion Acquisition LLC Seat system for a vehicle
US10065541B2 (en) 2015-08-10 2018-09-04 Grammer Ag Horizontal vibration device for a vehicle seat
EP3181397A1 (fr) * 2015-12-14 2017-06-21 Grammer Ag Dispositif de vibration de véhicule
EP3181396A1 (fr) * 2015-12-14 2017-06-21 Grammer Ag Dispositif de vibration de véhicule
US10017081B2 (en) 2015-12-14 2018-07-10 Grammer Ag Vehicle vibration device
DE102015121764A1 (de) * 2015-12-14 2017-08-10 Grammer Ag Fahrzeugschwingungsvorrichtung
CN107009929A (zh) * 2015-12-14 2017-08-04 格拉默公司 车辆振动装置
DE102015121764B4 (de) 2015-12-14 2023-08-31 Grammer Aktiengesellschaft Fahrzeugschwingungsvorrichtung
CN106965722A (zh) * 2015-12-14 2017-07-21 格拉默公司 车辆振动装置
US10012286B2 (en) 2015-12-14 2018-07-03 Grammer Ag Vehicle vibration device
DE102015121765A1 (de) * 2015-12-14 2017-06-14 Grammer Ag Fahrzeugschwingungsvorrichtung
FR3066723A1 (fr) * 2017-05-24 2018-11-30 Patrick Edouard Sajous Vehicule muni d'un systeme mobile afin d'ameliorer la stabilite de l'ensemble vehicule et charge
DE102019134244A1 (de) * 2019-12-13 2021-06-17 Grammer Aktiengesellschaft Fahrzeugsitz mit Scherengestellanordnung
US11279271B2 (en) 2019-12-13 2022-03-22 Grammer Ag Vehicle seat having a suspension unit for cushioning rolling and vertical suspension movements
US11285846B2 (en) 2019-12-13 2022-03-29 Grammer Ag Vehicle seat with scissor frame arrangement
US11685298B2 (en) 2019-12-13 2023-06-27 Grammer Ag Vehicle seat with scissor frame arrangement
US12005821B2 (en) 2019-12-13 2024-06-11 Grammer Ag Cushioning rolling and vertical suspension movements

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