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WO1993010996A1 - Unite de suspension pour siege de vehicule - Google Patents

Unite de suspension pour siege de vehicule Download PDF

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Publication number
WO1993010996A1
WO1993010996A1 PCT/AU1992/000647 AU9200647W WO9310996A1 WO 1993010996 A1 WO1993010996 A1 WO 1993010996A1 AU 9200647 W AU9200647 W AU 9200647W WO 9310996 A1 WO9310996 A1 WO 9310996A1
Authority
WO
WIPO (PCT)
Prior art keywords
frames
damping
brake member
seat
braking
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/AU1992/000647
Other languages
English (en)
Inventor
William John Seybourne Bailey
Donald Maxwell Culley
Donald Maxwell Culley, Jr.
Stephen James Ward
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Rosdon Engineering and Manufacturing Pty Ltd
Original Assignee
Rosdon Engineering and Manufacturing Pty Ltd
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 Rosdon Engineering and Manufacturing Pty Ltd filed Critical Rosdon Engineering and Manufacturing Pty Ltd
Publication of WO1993010996A1 publication Critical patent/WO1993010996A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • B60N2/502—Seat suspension devices attached to the base of the seat
    • 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
    • B60N2/505—Adjustable suspension including height adjustment
    • 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
    • B60N2/506—Seat guided by rods
    • B60N2/508—Scissors-like structure
    • 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

Definitions

  • THIS INVENTION relates to a vehicle seat suspension unit.
  • a vehicle operator's comfort and efficiency is dependent on providing a suitable suspension unit for his seat to eliminate, or at least reduce, the shocks and vibration transmitted from the vehicle to the operator via his seat.
  • the shape and geometry of the transfer assembly can be altered to provide desired characteristics of force and deflection to the platform.
  • a vehicle seat suspension unit including: a base frame mountable on a vehicle; a seat support frame to mount a vehicle operator's seat; •10 a scissor arms assembly interconnecting the frames to enable the frames to move relative to each other substantially in parallelism; a transfer assembly pivotally mounted on one of the frames, having at least one arm; 15 spring means mounted at one end on one of the frames and connected to the transfer assembly, the arm of the transfer assembly engaging the other of the frames; and damping means on, or engageable with, the 20 transfer assembly; so arranged that as the frames move relatively towards or away from each other, the spring rate and/or damping is applied at a variable rate.
  • the frames are substantially 25 rectangular in plan view.
  • the base frame incorporates the runners or slides for longitudinal adjustment of the seat in the vehicle.
  • the seat support frame may have the seat bolted to it or the frame may be moulded into the base 30 of the seat, and the seat belts may be anchored on the seat support frame.
  • the scissor arms assembly includes a pair of primary scissor arms and a pair of secondary scissor arms pivotally ⁇ and/or slidably) • 35 connected to the frames and to each other and the second scissor arms may be connected to the frames by pivotal and/or slidable) links. Reinforcing plates or bars may connect the arms in each pair.
  • the transfer assembly may include at least one, but preferably two, transfer levers, in the form of bell cranks, pivotally mounted intermediate their length on one of the frames.
  • One arm of each transfer lever is connected to the spring assembly while the other arm preferably has a roller at its distal end to engage the other frame.
  • damping means are provided on, or integral with, the mounting for the transfer lever(s) .
  • the damping means includes opposed, movable and fixed brake discs, each with braking face sectors separated by relieved portions, wherein at an initial (or neutral) position, the respective face sectors are separated by a "TEFLON" (or like plastic bush) for substantially zero damping, the face sectors coming into contact to provide a damping effect when the two frames are displaced a small distance from the initial preload (or neutral) position, the damping rate increasing with the displacement.
  • TEFLON or like plastic bush
  • the damping means is a "decelerator" with braking faces urged into contact by male and female brake members with complementary ridges (or ribs) and valleys (or grooves) wherein, at an initial preload (or neutral) position, the brake members effectively apply zero damping effect when the two frames are displaced a small distance from the preload (neutral) position. As the displacement increases, the relative rotation of the braking members applies a greater applied load onto the braking faces to increase the effective damping.
  • the ridges/ribs and valleys/grooves are arranged radially on the male and female brake members and are of reducing taper and height and width towards the ⁇ centre thereof.
  • a cast iron brake disc and the male brake member are non-rotatably mounted on a support on one (preferably the bottom) frame and the female brake member is rotated relative thereto by fingers or the like on the transfer levers.
  • Belleville washers, or like spring means apply a preset preload to the braking faces on the cast iron brake disc and the female brake member, and between the male and female brake members.
  • the spring means are mounted on adjustable mounts to enable the operator's weight to be compensated for so that the seat unit can be set at an initial preload or neutral height.
  • the damping means is a
  • a shaft or tubular body is rotatably mounted on one of the frames and is rotatable by the transfer assembly.
  • At least one eccentric is provided on the shaft or tubular body and is received within a bore in a braking member, friction braking material being provided about the eccentric and/or within the bore.
  • the braking member is preferably movably mounted on the one frame and preferably has spring means engageable with the frame, the eccentric being rotated into braking or damping engagement with the brake member by the transfer assembly as the two frames are displaced from the preload (neutral) position.
  • the braking or damping increases as the displacement from the preload (neutral) position increases.
  • a respective pair of eccentrics/ braking members are provided, preferably 180° out of phase relative to the shaft or tubular body, a respective eccentric/braking member providing the braking or damping as the frames move in opposite directions from the preload position.
  • the spring means which may comprise Belleville washers, are adjustable to enable the braking or damping to be adjusted.
  • the present invention resides in a damping means for a vehicle seat suspension unit in accordance with the embodiments hereinbefore described.
  • the present invention resides in an improved seat slide assembly for vehicles including: a fixed slide mountable on a vehicle and having an upstanding flange formed with notches or slots; a movable slide supported by roller and/or ball means movable along the fixed slide; latch means on the movable slide releasably engageable with the notches or slots on the fixed slide; and respective flange means on the slides in overlapping arrangement to prevent disengagement of the slides if the slides undergo a relative twisting action.
  • the latch means are spring loaded towards engagement with the notches or slots, the latch means being movable towards a disengaged position by a release plate pivotally mounted on the movable slide and operable by a linkage from a remote handle.
  • FIGS. 1 and 2 are respective side views of the seat suspension unit at maximum and minimum height respectively; .
  • FIGS. 3 and 4 are respective side views of the transfer assembly and spring assembly at maxi um and minimum height respectively;
  • FIG. 5 is a side view of a modified transfer assembly
  • FIGS. 6 to 8 show respective side, end and sectional views of a fixed brake disc;
  • FIGS. 9 to 11 shows similar view of a bearing housing and movable brake disc;
  • FIG. 12 is a top, part-sectional view of a second embodiment of the damping, or "decelerator” means
  • FIG. 13 an exploded view of some of the components of the decelerator means
  • FIGS. 14 to 16 are respective side, bottom and end views of the transfer levers;
  • FIGS. 17 and 18 are respective part-sectional and side views of the bearing housings on the transfer levers;
  • FIGS. 19 and 20 are side and front views of the braking shaft;
  • FIGS. 21 and 22 are end and side views of the cast iron braking disc;
  • FIGS. 23 to 26 are respective front, side, end and sectional views of the female brake member; and FIGS. 27 to 30 are respective front, side, part-sectional, side and side-sectional views of the male brake member;
  • FIG. 31 is a top plan view of a third embodiment of the damping, or "decelerator” means
  • FIG. 32 is a front elevational view of the tube and eccentrics
  • FIG. 33 is a side view of the tube and transfer levers
  • FIGS. 34 to 35 are sectional end views taken on lines 34-34 and 35-35, respectively, on FIG. 31;
  • FIG. 36 is a sectional end view of a seat slide assembly;
  • FIGS. 37 and 38 are side views of the seat slide latching assembly in the latched and " released positions; and FIG. 39 is a top plan view of a latch.
  • the seat suspension unit 10 has a base frame 11, where the side rails comprise the movable slides 12 of the seat slide assemblies (see FIG. 36) and they are interconnected by front and rear cross tubes 13, 14.
  • the seat support frame 15 is substantially rectangular in plan view and has side rails 16 and front and rear rails 17, 18 of RHS steel.
  • the operator's seat 18 has its frame mounted on, or integral with, the support frame 15 and the seat may have polyurethane or closed cell foam padding.
  • the seat belts may be anchored to the support frame 15 or the base frame 11, the construction of the seat slide assemblies (to be hereinafter described) resisting any twisting loads in a collision.
  • a first scissor assembly 19 has a pair of primary links 20 pivotally mounted on the movable slides 12 by means of a pin and a spherical self-aligning bearing 21.
  • the primary links are joined at the rearward ends by a lateral steel tube section 22, which has moulded inserts of low friction material.
  • a circular rod 23 interconnects the side rails 16 of the seat support frame 15 and has sliding blocks 24 (or rolling elements) received in the inserts in the steel tube 22 to allow relative rotation and sliding movement between the steel tube and the rod 23.
  • the second scissor assembly 25 has a pair of tubular secondary links 26 interconnected at their forward ends by a lateral tubular section 27 mounted on low friction bushes 28 located on a circular rod 29 interconnecting the side rails 16 of the seat support frame 15.
  • mounted inserts 30 have slots 31 which slidably locate blocks 32 (or rolling elements ' ) rotatable on pins 33 on the movable slides 12, the blocks and pins providing relative translation and rotation of the links 26 to the slides.
  • the primary and secondary links 20, 26 of the scissor assemblies are pivotally interconnected intermediate their lengths by pivot pins and self- aligning bearings 34.
  • a pair of parallel coil springs 40 are mounted (in a screw-threaded type engagement) with mounting blocks 41 (see FIG. 5), the latter having a screw-threaded bore to receive a threaded rod 42 mounted at its forward end in a gearbox 43 mounted on the front cross-tube 13.
  • An electric motor (not shown) is operably connected to the threaded rods 42 via suitable gears to rotate the rods 42 to extend, or retract, the springs 40 to enable the seat height to be adjusted to a preset preload (or neutral) height for a wide range of operator l s weights.
  • the rearward ends of the springs 40 are mounted on spring blocks 43 which are pivotally connected via low friction roller bearings to an axle located on the transfer lever 50 to be hereinafter described.
  • the transfer assembly 50 has a pair of bell cranks 51 interconnected in spaced relationship by an axle 52.
  • a lower (shorter) arm 53 on each bell crank is pivotally connected to a respective spring block 43 while the upper, longer arm 54 has a roller 55 at its distal end which bears on a cross-tube or plate 56 on the support frame 15, preferably in the vertical plane of the centre of gravity (C.G.) of the suspension unit 10-
  • the " rollers 55 are kept in engagement with the plate 56 by a loop 57 which engages the axle 58 which rotatably supports the rollers 55 on the arms 54.
  • the axle 52 for the bell cranks 51 has bearings (not shown) for the spring blocks on its outer ends received in recesses 59 in the bush housings 60
  • the outer faces 61 of the bush housings having raised braking sectors 62 which stand proud of the adjacent faces 61.
  • the braking sectors may have an included angle of e.g. 48° ⁇ 05°).
  • a "TEFLON" (trade mark) bush (not shown) is received in a recess 63 in the bush housing and it engages the inner face of an adjacent fixed brake disc 64 (see FIG. 6), each fixed brake disc 64 being mounted on a respective support bracket 65 as the rear cross- tube 14 of the base frame 11. (Nuts and washers on the face ends of the axle 52 bear on the outer faces of the support brackets.)
  • Each fixed brake disc 64 has braking sectors 66 raised above the adjacent inner face portions 67.
  • the braking sectors 66 may have included angles of e.g. 38° ⁇ 05°.
  • the braking sectors 62 of the bush housing 60 lie between the braking sectors 66 of the fixed brake discs 64, with the "TEFLON" washers interposed between the bush housing 60/brake disc 64 pairs.
  • the damping is substantially zero.
  • the braking sectors (of cast iron and steel) come into contact, the degree of contact increasing with increasing displacement.
  • damping is increased by a factor of e.g.
  • the operator may initially adjust the seat unit to the initial preload (neutral) height, while the vehicle is stationary, using a control switch for the electric motor to adjust the spring length. Alternatively, proximity switches on the suspension unit may automatically set the height by operating the electric motor.
  • the overall assembly provides a compact unit, with a relatively low spring rate but with high isolation of vibration due to the low (possibly zero) spring rate and the controlled, selective damping dependent on the displacement of the suspension unit from a preset initial (preload) position.
  • the "decelerator" means 100 may be substituted for the damping means (see FIGS. 6 to 11) to damp the suspension unit 10.
  • a post 101 is mounted on the rear cross-tube
  • a brake shaft 104 (see FIGS. 19 and 20), with an elongate keyway 105, is non-rotatably anchored (via a key not shown) in the post 101 and extends to each side thereof.
  • a respective cast iron brake disc 106 (see FIGS. 21, 22) is keyed to the shaft 104 on each side of the post 101.
  • a female brake member 107 (see FIGS. 23 to 26) has an inner planar braking face 108 to engage the adjacent respective brake disc 106 and a plain bore 109 for rotatable journalling on the shaft 104. Three sectors are relieved to form slots 110 and the sectors are separated by radial valleys 111.
  • Each valley 111 extends radially and is of substantially V-shape in end view (see FIGS. 24 and 25) and is of decreasing width (see FIG. 23) and depth (see FIG. 26) towards the centre of the member.
  • the slots 110 are engaged by respective fingers 112 on bearing housings 113 on the- transfer assembly 103 (see FIGS. 12-18).
  • the male brake members 114 (see FIGS. 27-30) have a tubular body 115 with a slotted bore 116a for keyed, non-rotational mounting on the shaft 104.
  • the end face 116 of a peripheral flange 117 is brought into complementary contact with the face 118 on the female brake member 106 provided with the valleys 111.
  • the end face 116 has three radially directed ribs 119 (see FIG. 27) of decreasing width and height towards the centre, complementary to the valleys 111.
  • Belleville washers 120 on the shaft 104, are preloaded by nuts 121 to apply a preload force on the male brake member 114, female brake member 107 and cast iron brake disc 106.
  • the bearing housings 113 of the transfer and assembly 113 are rotatably journalled on the bodies 115 of the male brake members 114 by bushes or bearings not shown. Rollers (not shown) are provided at the distal ends of the transfer levers 122 and the transfer assembly 104 operates in the manner hereinbefore described for transfer assembly 50, which it replaces.
  • the ribs 119 on the male brake member 114 lie within the complementary valleys 111 of the female brake member 107 and the braking face 108 of the latter is pressed against the cast iron braking ring 106, the washers 120 being adjusted so that there is substantially zero damping for the first one-third of travel or deflection of the suspension unit from the central position.
  • the fingers 112 on the transfer assembly 103 cause the female brake member 107 to rotate relative to the male brake member 114 and the cast iron brake discs 106 non-rotatably mounted on the shaft 104, the fingers extending through slots 123 on the male brake members 114.
  • the valleys 111 are rotatably displaced relative to the ribs 119 and their relative tapered shapes tend to move the brake members apart, which maintains the radial line contact between the ribs 119 and valleys 111. This movement is opposed by the washers 120 and so an increased braking force is generated between the braking face 108 on the female brake member 107 and the brake disc 106.
  • This braking, or damping, force is of a rising rate dependent on the shape and height of the ribs 119/valleys 111 but substantially zero damping occurs within approximately one-third of the preload (neutral) position of the unit 10.
  • the advantages of this arrangement are as hereinbefore described for the damping system of FIGS. 6 to 11.
  • the "decelerator" means 200 may also be substituted for the damping means (see FIGS. 6 to 11) to damp the suspension unit 10.
  • the rear cross-tube 14 is replaced by an inclined cross-bar 201 with end plates 202, 203 bolted to the adjacent movable slides 12 on the base frame 11.
  • a pair of brackets 204, 205 on the cross-bar 201 support a shaft 206, which has a screw-threaded bore at each end to receive studs 207, 208 through the brackets 204, 205.
  • a tube 209 is rotatably journalled at each end on the shaft 206 by bearings 210, 211.
  • An eccentric 212, 213 is formed integrally with, or welded or brazed to, each end of the tube 209, the eccentrics 212, 213 being 180° out of phase (see FIGS. 32, 34, 35).
  • Transfer levers 214, 215 extend in parallel, substantially tangentially to the tube 209 and their distal ends are interconnected by an axle 216 on which are rotatably journalled rollers 217, 218 which, engage the plate 56 on the support frame 15, preferably in the vertical plane of the centre of gravity (C.G.) of the suspension unit 10.
  • a plate 219 braces the transfer levers 214, 215 intermediate their length.
  • the springs 40 are connected to a pair of brackets 220, 221 depending from the tube 209.
  • Each eccentric 212, 213 is received within the bore 222, 223 of a brake member 224, 225 lined with a ring of friction braking material 226, 227.
  • Each braking member 224, 225 is movably mounted on the cross- bar 201 by a stud 228, 229 provided with a locking nut 230, 231 and Belleville spring(s) 232, 233.
  • the eccentric 212 will engage the rings 226 and cause the brake member 224 to move in the direction X 1 (see FIG. 34) (and away from cross-bar 201) and the Belleville spring 232 will start to be compressed.
  • the damping force generated between the eccentric 212 and rings 226 will be increased.
  • the eccentric 213 will move the brake member 225 in the direction opposite to arrow Y (see FIG. 35) and the clearance between the brake member 225 and the cross-bar 201 will not cause the eccentric 213 to frictionally engage its rings 227.
  • the transfer levers 214, 215 move in the direction of arrow Y (see FIG. 35), the eccentric 213 moves the brake member 225 in the direction of arrow Y 1 and increasing displacement increases the damping force generated between the eccentric 213 and ring 227 (with no damping force between eccentric 212 and its ring 224) .
  • Each eccentric 212, 213 only generates a damping force when it pulls on its respective brake members 224, 225, the brake members 224, 225 having a clearance which allows them to "float" relative to the cross-bar 201 when pushed by their eccentrics 212, 213. It will be noted that when the suspension unit is in the preload (neutral) position, the bores 222, 223 of the brake members 224, 225 are co-axial with the eccentrics 212, 213 and the rollers 217, 218 engage the plate 56 at substantially the vertical plane of the centre of gravity of the suspension unit. Referring now to FIGS. 36 to 39, the suspension unit 10 (of FIGS.
  • the fixed slide 71 has a base web 72 which can be bolted to the vehicle floor and on which rolls a plurality of rollers 73 (with spacers not shown) which support the initial web 74 of the movable slide 12.
  • Opposed pairs of hook-like flanges 75, 76 and 77, 78 on the fixed and movable slides 71, 12 respectively are spaced by low-friction balls 78a (provided with spacers not shown, to control their longitudinal separation) which provide stability and smooth operation for the slides.
  • An upwardly directed flange 79 on the movable slide lies within a downwardly directed recess 80 in the fixed slide 71. Should the suspension unit be placed under a tipping load e.g. during a vehicle collision, the flange 79 engages and -locks in the recess to lock the slides 71, 12 against separation. This enables the seat belt anchors to be mounted on the seat or seat support frame 15.
  • the two -slide assemblies 70 are independently latched against longitudinal movement although only one assembly need be latched to restrain the seat 18 against fore-and-aft movement.
  • a latch unit 81 (see FIG. 39) is provided for each movable slide 12 and is pivotally mounted on a pin 82 interconnecting the upstanding side flanges 83, 84 of the slide 12.
  • a loop 85 on one side of the latch unit releasably engages an adjacent pair of notches 86 on the locking flange 87 on the fixed slide 71, the latch unit 81 being urged into locking engagement by a spring (not shown) .
  • a release plate 88 also mounted on the pin 82, has a nose 89 which engages an extension 90 on the loop 85 and is operated by a link 91 to a bell crank 92 attached to one end of the seat adjustment handle 93 which interconnects the two bell cranks 92 so that the latch units 81 are released in unison.
  • the seat slide assemblies are also suitable for vehicles, e.g. automobiles, where a seat suspension unit is not employed but efficient mountings are required for the vehicle seats.

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  • Engineering & Computer Science (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Seats For Vehicles (AREA)

Abstract

Unité de suspension pour siège de véhicule possédant une structure de base (11) et une structure de support de siège (15) reliées par un ensemble de bras articulés en parallélogramme afin de permettre aux structures (11, 15) de se déplacer l'une par rapport à l'autre en parallélisme. Un ensemble de transfert (50) monté pivotant sur la structure de base (11) possède une paire de leviers de transfert (54) montés coulissants et reliés à la structure de support de siège (15), et un ensemble à ressort réglable (40) relié à la structure de base (11) et à l'ensemble de transfert (50), afin de fixer l'unité de suspension à une hauteur initiale. Un décélérateur ou ensemble amortisseur à disque de frein (centré sur l'axe (52)) assure un amortissement nul lors des faibles déplacements des structures (11, 15), mais un amortissement accru à mesure que les déplacements prennent de l'ampleur. On a également prévu un système permettant au siège de coulisser et comportant des glissières fixe et mobile, des éléments de verrouillage destinés à les maintenir en position, et des brides chevauchantes formées sur les deux glissières pour en empêcher la séparation lors d'un accident.
PCT/AU1992/000647 1991-12-02 1992-12-02 Unite de suspension pour siege de vehicule Ceased WO1993010996A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AUPK979991 1991-12-02
AUPK9799 1991-12-02
AUPL4167 1992-08-18
AUPL416792 1992-08-18

Publications (1)

Publication Number Publication Date
WO1993010996A1 true WO1993010996A1 (fr) 1993-06-10

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ID=25644169

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AU1992/000647 Ceased WO1993010996A1 (fr) 1991-12-02 1992-12-02 Unite de suspension pour siege de vehicule

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WO (1) WO1993010996A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1994021487A1 (fr) * 1993-03-17 1994-09-29 Rosdon Engineering & Manufacturing Pty. Ltd. Organe de suspension de siege d'automobile
WO2004045900A3 (fr) * 2002-11-15 2004-07-29 Milsco Mfg Company Suspension de siege de vehicule et procede
DE102005051228A1 (de) * 2005-10-26 2007-05-03 Grammer Ag Vorrichtung und Verfahren zur schwingungsdämpfenden Höheneinstellung eines Fahrzeugsitzes
EP3106570A4 (fr) * 2014-02-12 2017-11-22 Daedong Engineering Co. Ltd. Dispositif d'arrêt de vibrations sous charge élevée
CN114312510A (zh) * 2021-12-29 2022-04-12 盐城同环机电科技有限公司 一种带有减振器的汽车座椅骨架

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2335816A1 (de) * 1973-07-13 1975-02-06 Ernst Wanschura Fahrzeugsitz mit einer durch eine torsionsfeder abgefederten tragschere
AU7212274A (en) * 1973-08-13 1976-02-12 Brown Brothers Engineering Limited Slide mechanism
DE2559653A1 (de) * 1975-10-13 1977-06-30 Hammerstein Gmbh C Rob Feststelleinrichtung fuer eine laengsverstelleinrichtung fuer fahrzeugsitze
DE2717416A1 (de) * 1977-04-20 1978-11-02 Keiper Automobiltechnik Gmbh Bremsfederkupplung fuer stellgetriebe, insbesondere von sitzstellvorrichtungen, vorzugsweise in kraftfahrzeugen
AU3395178A (en) * 1977-03-24 1979-09-13 Brown Bros Eng Vehicle seat slides
AU3428678A (en) * 1977-03-18 1979-09-27 General Motors Corporation Vehicle seat
DE3146289A1 (de) * 1981-11-23 1983-05-26 Keiper Automobiltechnik Gmbh & Co Kg, 5630 Remscheid Bremsfederkupplung fuer stellgetriebe, insbesondere von sitzstellvorrichtungen
EP0209615A1 (fr) * 1984-03-23 1987-01-28 Fuji Kiko Company, Limited Dispositif de glissière de siège pour siège de véhicule automobile
GB2221245A (en) * 1988-07-28 1990-01-31 Ikeda Bussan Co Seat slide device
EP0368735A1 (fr) * 1988-11-10 1990-05-16 A. & M. COUSIN Etablissements COUSIN FRERES Profil de glissières permettant la réalisation de glissières à verrou flottant

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2335816A1 (de) * 1973-07-13 1975-02-06 Ernst Wanschura Fahrzeugsitz mit einer durch eine torsionsfeder abgefederten tragschere
AU7212274A (en) * 1973-08-13 1976-02-12 Brown Brothers Engineering Limited Slide mechanism
DE2559653A1 (de) * 1975-10-13 1977-06-30 Hammerstein Gmbh C Rob Feststelleinrichtung fuer eine laengsverstelleinrichtung fuer fahrzeugsitze
AU3428678A (en) * 1977-03-18 1979-09-27 General Motors Corporation Vehicle seat
AU3395178A (en) * 1977-03-24 1979-09-13 Brown Bros Eng Vehicle seat slides
DE2717416A1 (de) * 1977-04-20 1978-11-02 Keiper Automobiltechnik Gmbh Bremsfederkupplung fuer stellgetriebe, insbesondere von sitzstellvorrichtungen, vorzugsweise in kraftfahrzeugen
DE3146289A1 (de) * 1981-11-23 1983-05-26 Keiper Automobiltechnik Gmbh & Co Kg, 5630 Remscheid Bremsfederkupplung fuer stellgetriebe, insbesondere von sitzstellvorrichtungen
EP0209615A1 (fr) * 1984-03-23 1987-01-28 Fuji Kiko Company, Limited Dispositif de glissière de siège pour siège de véhicule automobile
GB2221245A (en) * 1988-07-28 1990-01-31 Ikeda Bussan Co Seat slide device
EP0368735A1 (fr) * 1988-11-10 1990-05-16 A. & M. COUSIN Etablissements COUSIN FRERES Profil de glissières permettant la réalisation de glissières à verrou flottant

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1994021487A1 (fr) * 1993-03-17 1994-09-29 Rosdon Engineering & Manufacturing Pty. Ltd. Organe de suspension de siege d'automobile
WO2004045900A3 (fr) * 2002-11-15 2004-07-29 Milsco Mfg Company Suspension de siege de vehicule et procede
US7185867B2 (en) 2002-11-15 2007-03-06 Milsco Manufacturing Company, A Unit Of Jason Incorporated Vehicle seat suspension and method
DE102005051228A1 (de) * 2005-10-26 2007-05-03 Grammer Ag Vorrichtung und Verfahren zur schwingungsdämpfenden Höheneinstellung eines Fahrzeugsitzes
DE102005051228B4 (de) * 2005-10-26 2007-08-09 Grammer Ag Vorrichtung und Verfahren zur schwingungsdämpfenden Höheneinstellung eines Fahrzeugsitzes
EP3106570A4 (fr) * 2014-02-12 2017-11-22 Daedong Engineering Co. Ltd. Dispositif d'arrêt de vibrations sous charge élevée
CN114312510A (zh) * 2021-12-29 2022-04-12 盐城同环机电科技有限公司 一种带有减振器的汽车座椅骨架
CN114312510B (zh) * 2021-12-29 2023-01-06 盐城同环机电科技有限公司 一种带有减振器的汽车座椅骨架

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