WO2007058572A1 - Suspension device for a vehicle component - Google Patents

Suspension device for a vehicle component Download PDF

Info

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
French (fr)
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/en
Publication of WO2007058572A1 publication Critical patent/WO2007058572A1/en

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

The invention relates to a suspension device for suspending a vehicle component (9) above a vehicle frame. The suspension device comprises at least one link mechanism (106, 107) adapted to connect an upper support structure (8) of the vehicle component to a lower support structure (10), 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 (106, 107) is designed such that the vehicle component (9) is permitted to pivot back and forth in a lateral direction

Description

Suspension device for a vehicle component
FIELD OF THE INVENTION
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.
Work vehicles place considerable demands on the suspension arrangements in order to make the working environment of the driver comfortable. 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.
In connection with transportation of heavy loads, e.g. in contracting work, articulated haulers (also called dumpers) are frequently used. 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.
PRIOR ART
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.
SUMMARY OF THE INVENTION
A purpose of the invention is to provide a suspension device which improves the conditions for a driver during operation in difficult terrain.
This purpose is achieved by means of a suspension device according to claim 1. Thus, it is achieved by means of 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 characterized in that 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. Thus, 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.
According to a preferred embodiment of the invention, 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. Thus, 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. Thus, 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 need for any centering springs is thereby reduced. Further, any need for regulating the centering force of the centering springs, and also the dampening caharacteristics of dampeners, will be reduced.
According to a further preferred embodiment of the invention, 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.
According to a further preferred embodiment of the invention, the link mechanism is adapted to transmit a load from the weight of the vehicle component to the lower support structure. Thus, in contrast to prior art vehicle seat suspensions, in which the compression spring transmits the load and the link arms only guide a movement of the seat, in the present invention, the link mechanism is adapted to transfer the load from the weight of the vehicle component. Preferably, a link member of the link mechanism is arranged to be subjected to a tensile force from said weight load.
Further preferred embodiments of the invention and advantages connected thereto will be apparent from the following drawings, description and further claims.
BRIEF DESCRIPTION OF THE DRAWINGS
The invention will be explained below, with reference to the embodiments shown on the appended drawings, wherein 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, and
FIG 9 discloses a vehicle cab suspension in an exploded view according to a first embodiment. DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS OF THE
INVENTION
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. In figure 1, 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) .
Figure 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. More specifically, 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. Thus, said link mechanisms 6, 7 are arranged at a distance from each other in the lateral direction.
Thus, 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. Thus, the link members
11, 13, 15 and 12, 14, 16, respectively, in a single link mechanism are arranged to pivot relative to each other in parallel to a plane.
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. More specifically, 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. Thus, 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. Thus, 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) . In other words, the driver seat will be inclined, ie oblique, with regard to the lower support structure 10 during operation. Further, 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. Thus, 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.
Figure 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) . Thus, 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. Thus, 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) . In other words, the driver seat will be inclined, ie oblique, with regard to the lower support structure 10 during operation. Further, 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. Thus, 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. Thus, 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.
In figure 5 and 6, 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. Regarding the suspension 105 for permitting movement in the lateral direction, the centering spring 24, 25 is connected to the first connection member 111, 112 and the intermediate support structure 23. Regarding the suspension 205 for permitting movement in the longitudinal direction, 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. Regarding the suspension 105 for permitting movement in the lateral direction, the dampener 28, 29 is connected to the first connection member 111, 112 and the intermediate support structure 23. Regarding the suspension 205 for permitting movement 0 in the longitudinal direction, the dampener 30, 31 is connected to the first connection member 211, 212 and the lower support structure 10.
Thus, 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.
In figure 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. In the same manner, the 0 suspension 205 permitting movement in the longitudinal direction comprises four link mechanisms, one at each corner of the driver seat 9. In figure 8, 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. For this purpose, each link mechanism comprises two ball joints, see enlarged portion. The intermediate link member is connected to the ball of each ball joint.
In figure 9, 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.
The invention has been described above with regard to the design of the link arrangements for achieving a cradle-like rocking function in different directions. In addition to the described suspension designs, further connection arrangements may be used. With regard to the cab suspension, the suspension should be sufficiently strong to retain the cab on the frame even if the vehicle should overturn. In this context, reference is frequently made to ROPS-protection, where ROPS stands for Roll Over Protection Structure. A plurality of such ROPS-designs are known and will therefore not be discussed further. The invention is not in any way limited to the above described embodiments , instead a number of alternatives and modifications are possible without departing from the scope of the following claims .
According to an alternative to the suspension shown in figure 8, instead of using four link mechanisms, each comprising two ball joints, it would be sufficient to use three link mechanisms .
Further, the 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.

Claims

1. Suspension device for suspending a vehicle component (9,38) above a vehicle frame (32), wherein the suspension device comprises at least one link mechanism
(6, 7,-106, 107,-206, 207,-406, 407) adapted to connect an upper support structure (8) of the vehicle component to a lower support structure (10) , which is connected to the vehicle frame (32), in such a manner that the upper support structure is permitted to pivot relative to the lower support structure c h a r a c t e r i z e d in that the link mechanism (6, 7; 106, 107 ; 406, 407) is designed such that the vehicle component (9,38) is permitted to pivot back and forth in a lateral direction of the vehicle frame .
2. Suspension device according to claim 1, c h a r a c t e r i z e d in that the link mechanism (6, 7; 106, 107,-406, 407) is adapted so that the upper support structure (8) is located in a base position relative to the lower support structure
(10) in a non-operative state, and that the vehicle component (9,38) is permitted to pivot along an arcuate path through the base position in the lateral direction.
3. Suspension device according to claim 2, c h a r a c t e r i z e d in that the link mechanism (6, 7,-106, 107,-406, 407) is configured so that a potential energy of the vehicle component (9,38) is increased when the upper support structure (8) is moved from the base position along said arcuate path.
4. Suspension device according to any preceding claim, c h a r a c t e r i z e d in that the link mechanism (206, 207,-406, 407) is designed such that the vehicle component (9,38) is also permitted to pivot back and forth in a lengthwise direction of the vehicle frame (32) .
5. Suspension device according to any preceding claim, c h a r a c t e r i z e d in that the link mechanism (6, 7; 106, 107;206, 207;406, 407) is adapted to transmit a load from the weight of the vehicle component (9,38) to the lower support structure (10) .
6. Suspension device according to claim 5, c h a r a c t e r i z e d in that a link member (15, 16; 115, 116; 215, 216) of the link mechanism (6, 7; 106, 107;206, 207;406, 407) is arranged to be subjected to a tensile force from said weight load.
7. Suspension device according to any preceding claim, c h a r a c t e r i z e d in that each link mechanism (6, 7; 106, 107;206, 207;406, 407) comprises a first link member (15, 16; 115, 116; 215, 216) adapted to be rigidly connected to the upper support structure (8) , a second link member (13, 14 ,-113,114 ,-213,214) adapted to be rigidly connected to the lower support structure (10) and an intermediate link member (15, 16;115, 116;215, 216) pivotably connecting the first and second connection member.
8. Suspension device according to claim 7, c h a r a c t e r i z e d in that said intermediate link member (15, 16;115, 116;215, 216) is arranged to be subjected to a tensile force from said weight load.
9. Suspension device according to claim 7 or 8, c h a r a c t e r i z e d in that a pivot joint of the first link member (15, 16; 115, 116; 215,216) is positioned below a pivot joint of the second link member (13 , 14; 113 , 114/213 , 214) .
10. Suspension device according to any of claims 7-9, c h a r a c t e r i z e d in that said intermediate link member (15, 16/115, 116/215, 216) is pivotably connected at a first end to the first link member (15, 16; 115, 116; 215, 216) and at a second end to the second link member (13 , 14; 113 , 114/213, 214) .
11. Suspension device according to any preceding claim, c h a r a c t e r i z e d in that the suspension device comprises at least one pair of link mechanisms (6, 7; 106, 107; 206, 207,-406, 407) and that said link mechanisms are arranged at a distance from each other.
12. Suspension device according to claim 11, c h a r a c t e r i z e d in that at least two of said link mechanisms (6, 7; 106, 107,-406 ,407) are arranged at a distance from each other in a lateral direction of the vehicle frame to permit the vehicle component to pivot back and forth in the lateral direction relative to the vehicle frame.
13. Suspension device according to claim 11 or 12, c h a r a c t e r i z e d in that at least two of said link mechanisms (206,207) are arranged at a distance from each other in a lengthwise direction of the vehicle frame (32) to permit the vehicle component to pivot back and forth in the lengthwise direction relative to the vehicle frame.
14. Suspension device according to any preceding claim, c h a r a c t e r i z e d in that at least one of said link mechanisms (6, 7; 106, 107; 206,207) comprises a hinge joint.
15. Suspension device according to any preceding claim, c h a r a c t e r i z e d in that a single link mechanism (406,407) is configured to allow both pivoting back and forth in a lengthwise direction of the vehicle frame and back and forth in a lateral direction of the vehicle frame.
16. Suspension device according to any preceding claim, c h a r a c t e r i z e d in that at least one of said link mechanisms (406,407) comprises at least one ball joint.
17. Suspension device according to any preceding claim, c h a r a c t e r i z e d in that a first of said link mechanisms (6, 7; 106, 107) is configured to allow for pivoting back and forth in a lengthwise direction of the vehicle frame and a second of said link mechanisms (206,207) is configured to allow for pivoting back and forth in the lateral direction of the vehicle frame.
18. Suspension device for suspending a vehicle component
(9,38) above a vehicle frame (32), wherein the suspension device comprises at least one link mechanism (6,7;106,107;206,207;406,407) adapted to connect an upper support structure (8) of the vehicle component to a lower support structure (10) , 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 c h a r a c t e r i z e d in that the link mechanism (6, 7; 106, 107; 406, 407) is adapted to transmit a load from the weight of the vehicle component (9,38) to the lower support structure.
19. Suspension device according to claim 18, c h a r a c t e r i z e d in that the link mechanism (6, 7; 106, 107; 406, 407) is adapted so that the upper support structure (8) is located in a base position relative to the lower support structure
(10) , and that the vehicle component is permitted to pivot along an arcuate path through the base position.
20. Suspension device according to claim 18 or 19, c h a r a c t e r i z e d in that the link mechanism (206, 207 ; 406, 407) is designed such that the vehicle component is permitted to pivot back and forth in a lengthwise direction of the vehicle frame.
21. Suspension device according to any of claims 18-20, c h a r a c t e r i z e d in that the link mechanism (6, 7; 106, 107; 406, 407) is designed such that the vehicle component is permitted to pivot back and forth in a lateral direction of the vehicle frame.
22. Suspension device according to any of claims 18-21, c h a r a c t e r i z e d in that a link member (15, 16,-115, 116,-215, 216) of the link mechanism (6, 7,-106, 107; 206, 207,-406, 407) is arranged to be subjected to a tensile force from said weight load.
23. Suspension device according to any preceding claim, c h a r a c t e r i z e d in that the vehicle component is formed by a driver seat (9) .
24. Suspension device according to any preceding claim, c h a r a c t e r i z e d in that the vehicle component is formed by a cab (38) .
25. A vehicle (1) comprising a suspension device according to any preceding claim.
26. A work vehicle (1) comprising a suspension device according to any of claims 1-24.
PCT/SE2005/001741 2005-11-18 2005-11-18 Suspension device for a vehicle component WO2007058572A1 (en)

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DE102011013122A1 (en) * 2011-03-04 2012-09-06 Grammer Aktiengesellschaft Lever mechanism for damper adjustment for horizontal suspension
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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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EP2420404A1 (en) * 2010-08-18 2012-02-22 Grammer Ag Vehicle vibration device for vehicle seats or vehicle cabins
DE102010034857B4 (en) * 2010-08-18 2021-01-28 Grammer Aktiengesellschaft Vehicle vibration device for vehicle seats
US8607910B2 (en) 2010-08-18 2013-12-17 Grammer Ag Vehicle suspension device for vehicle seats or vehicle cabs
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US9266452B2 (en) 2010-12-08 2016-02-23 Grammer Ag Vehicle vibration device for vehicle seats or vehicle cabs
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US8960691B2 (en) 2011-03-04 2015-02-24 Grammer Ag Apparatus and method for damper adjustments for a horizontal suspension
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CN102673451A (en) * 2011-03-04 2012-09-19 格拉默股份公司 Lever mechanism for damper adjustment for horizontal suspension
DE102011013122A1 (en) * 2011-03-04 2012-09-06 Grammer Aktiengesellschaft Lever mechanism for damper adjustment for horizontal suspension
US8973967B2 (en) 2011-09-15 2015-03-10 Grammer Ag Vehicle seat, motor vehicle and method for spring-mounting a vehicle seat
DE102012102574A1 (en) * 2012-03-26 2013-09-26 Dornier Technologie Gmbh & Co. Kg storage device
WO2014176130A1 (en) * 2013-04-23 2014-10-30 Bose Corporation Seat system for a vehicle
CN105246737A (en) * 2013-04-23 2016-01-13 伯斯有限公司 Seat system for a vehicle
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US10065541B2 (en) 2015-08-10 2018-09-04 Grammer Ag Horizontal vibration device for a vehicle seat
EP3181397A1 (en) * 2015-12-14 2017-06-21 Grammer Ag Vehicle vibration device
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US10017081B2 (en) 2015-12-14 2018-07-10 Grammer Ag Vehicle vibration device
DE102015121764A1 (en) * 2015-12-14 2017-08-10 Grammer Ag Vehicle vibration device
CN107009929A (en) * 2015-12-14 2017-08-04 格拉默公司 Vehicular vibration device
DE102015121764B4 (en) 2015-12-14 2023-08-31 Grammer Aktiengesellschaft vehicle vibration device
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US10012286B2 (en) 2015-12-14 2018-07-03 Grammer Ag Vehicle vibration device
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