EP2129538A1 - Ensemble ressort à rigidité de suspension variable et jambe de force dotée d'un ensemble ressort de ce type - Google Patents

Ensemble ressort à rigidité de suspension variable et jambe de force dotée d'un ensemble ressort de ce type

Info

Publication number
EP2129538A1
EP2129538A1 EP08716448A EP08716448A EP2129538A1 EP 2129538 A1 EP2129538 A1 EP 2129538A1 EP 08716448 A EP08716448 A EP 08716448A EP 08716448 A EP08716448 A EP 08716448A EP 2129538 A1 EP2129538 A1 EP 2129538A1
Authority
EP
European Patent Office
Prior art keywords
spring
hydraulic
hydraulic fluid
piston
hydraulic chamber
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.)
Withdrawn
Application number
EP08716448A
Other languages
German (de)
English (en)
Inventor
Daniel Prieto-Doerfel
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke AG
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 Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP2129538A1 publication Critical patent/EP2129538A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G15/00—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type
    • B60G15/02—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring
    • B60G15/06—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper
    • B60G15/062—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper the spring being arranged around the damper
    • B60G15/065—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper the spring being arranged around the damper characterised by the use of a combination of springs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
    • B60G17/021—Spring characteristics, e.g. mechanical springs and mechanical adjusting means the mechanical spring being a coil spring
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
    • B60G17/027—Mechanical springs regulated by fluid means
    • B60G17/0272—Mechanical springs regulated by fluid means the mechanical spring being a coil spring
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
    • B60G17/033—Spring characteristics, e.g. mechanical springs and mechanical adjusting means characterised by regulating means acting on more than one spring
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/10—Type of spring
    • B60G2202/12—Wound spring
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/30—Spring/Damper and/or actuator Units
    • B60G2202/31—Spring/Damper and/or actuator Units with the spring arranged around the damper, e.g. MacPherson strut
    • B60G2202/312—The spring being a wound spring
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/40—Type of actuator
    • B60G2202/41—Fluid actuator
    • B60G2202/413—Hydraulic actuator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/10—Mounting of suspension elements
    • B60G2204/12—Mounting of springs or dampers
    • B60G2204/124—Mounting of coil springs
    • B60G2204/1242—Mounting of coil springs on a damper, e.g. MacPerson strut
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2500/00—Indexing codes relating to the regulated action or device
    • B60G2500/20—Spring action or springs

Definitions

  • the invention relates to a spring arrangement with variable spring rate and a strut which is adapted to be suitable for a motor vehicle and having the spring arrangement.
  • the strut has a coil spring and a hydraulic shock absorber disposed within the coil spring.
  • the coil spring and the shock absorber are connected in parallel, so that the shock absorber has in its change in length both an elastic characteristic and an attenuation characteristic.
  • the wheel is fixed with its axis and the other end of the strut is fixed to the body, so that the body is supported by the strut.
  • the yielding of the strut depends on the one hand on the ride on the vehicle via the wheel on the strut introduced shocks and on the other hand on the weight of the body or its payload.
  • the manner of yielding of the strut and thus the characteristic of the mounting of the body is determined in particular by the spring rate of the coil spring. If the coil spring of the suspension strut has a high spring rate, then the body is cushioned hard, whereas the body is cushioned soft when the coil spring of the shock absorber has a low spring rate.
  • the strut Due to different conditions when driving the vehicle, in particular different unevenness in the ground, which is caused by the suspension strut and different high body loadings, it is desirable for the strut to be adaptable. In particular, it is desirable if the spring rate of the strut is variable, so that the type of mounting of the body can be adjusted depending on the driving conditions.
  • a soft storage of the body would be preferred with low payload and flat road during slow travel, whereas a hard storage of the body would be preferable with high payload and rough road during fast driving.
  • spring systems which have a plurality of springs and in which the KrafWund motion transmission is accomplished via hydraulic lines. During compression of the assembly, hydraulic oil flows in certain circuit states.
  • the springs are connected to each other in series and / or in parallel and optionally activated or shutdown. The activation and the decommissioning of selected springs can be accomplished by means of actuators and / or valves.
  • the object of the invention is to provide a spring arrangement and a suspension strut having this spring arrangement whose spring rate is simple, quick and precisely adjustable.
  • the spring arrangement according to the invention has a main spring, a
  • a slider, a stopper and at least one auxiliary spring which is connected in series with the main spring and having a first end, on which the stopper is fixed, and a second end facing away from the first end, with respect to which the slider is fixable, the position of which is adjustable so that when springing the spring assembly, the auxiliary spring has overcome a predetermined compression travel, the stop abuts the slider and thereby further compression of the auxiliary spring is prevented.
  • the spring assembly If the spring assembly is unloaded, it is fully extended. If the spring assembly pressed together, so shorten both the main spring and the auxiliary spring. The spring rate of the spring arrangement results from the series connection of the main spring and the auxiliary spring. If the spring assembly further compressed and reaches the current compression travel of the auxiliary spring the predetermined compression travel, the stop abuts the slide. As a result, further shortening of the additional spring is prevented when the spring arrangement is subjected to further compression. Once the stop abuts the slide, the additional spring is no longer resilient, so that the spring rate of the spring assembly is determined by the main spring.
  • the spring rate of the spring assembly is determined by both the main spring and the auxiliary spring, whereas the spring rate of the spring assembly is determined by the abutment of the stop to the slider only of the main spring.
  • the spring rate of the spring assembly is smaller than before after the abutment of the stop to the slider. It follows that the spring rate of the spring assembly is smaller for small compression travel than for large compression travel, in which the predetermined compression travel of the auxiliary spring is exceeded.
  • the shock absorber according to the invention for a motor vehicle has the spring arrangement according to the invention.
  • the suspension strut has a spring characteristic such that the motor vehicle is cushioned softly with small compression travel, whereas in the case of long compression travel in which the actual compression travel of the additional spring has reached the predetermined compression travel, the motor vehicle is resiliently spring-loaded.
  • the motor vehicle in which the strut is provided a high ride comfort.
  • the likelihood is reduced that the motor vehicle undesirably touches when driving over heavy bumps in the road, whereby the safety of the motor vehicle is increased.
  • the predetermined compression travel of the auxiliary spring is adjustable by adjusting the position of the slider.
  • the position of the slider can be set so that the stopper abuts the slider when the spring assembly is still stretched as good as unloaded.
  • the spring rate of the spring assembly is determined only by the main spring, whereby the shock absorber bounces the vehicle hard in the entire compression range.
  • the position of the slide can be adjusted such that when the spring assembly is completely compressed, the stop only then hits the slide.
  • the spring arrangement comprises a hydraulic chamber and the slide as a hydraulic piston arranged in the hydraulic chamber which is displaceable away from the second end by means of a hydraulic fluid when it is introduced into the hydraulic chamber so that the predetermined compression travel is shortened, and displaceable toward the second end by means of the hydraulic fluid when it is discharged from the hydraulic chamber is such that the predetermined compression travel is extended, and which is supported by the hydraulic fluid, when the hydraulic chamber is tightly sealed, at the second end positionally immovable.
  • the hydraulic piston can be displaced from the stop into the hydraulic chamber when the stop exerts a corresponding force on the hydraulic piston.
  • the slide in the form of the hydraulic piston by means of the hydraulic fluid is continuously displaceable and durable in any position.
  • the adjustability of the spring assembly is flexible and versatile.
  • the spring arrangement preferably has a hydraulic fluid reservoir and a hydraulic line which connects the hydraulic fluid reservoir to a hydraulic chamber in a hydraulic fluid-conducting manner and which has a switching arrangement which includes a non-return check valve from the hydraulic chamber to the hydraulic fluid reservoir, a non-return valve from the hydraulic fluid reservoir to the hydraulic chamber and a non-return valve Having shut-off, wherein the check valves and the shut-off device can be selectively switched into the hydraulic line.
  • the hydraulic piston When the non-return check valve is switched from the hydraulic chamber to the hydraulic fluid reservoir into the hydraulic line, the hydraulic piston can be urged toward the second end by means of the hydraulic fluid. Both the additional spring and the main spring are compressed during compression of the spring arrangement, whereby the spring arrangement has a small spring rate. Since the hydraulic fluid from the Hydraulic fluid reservoir flows, the pressure in the Hydraulikfluid- reservoir increases.
  • the hydraulic piston can follow the stop when the spring arrangement rebounds. If a high pressure prevails in the hydraulic fluid reservoir, this causes the hydraulic piston to extend. When springing the spring arrangement, however, the outflow of hydraulic fluid from the hydraulic chamber is blocked, so that only the main spring is compressible when the predetermined compression travel of the auxiliary spring is reached, whereby the spring rate of the spring assembly is high.
  • the current position of the hydraulic piston determines the predetermined compression travel of the auxiliary spring.
  • the position of the hydraulic piston is determined. This can be done either directly on the piston or directly or indirectly via the Hydraulikfiuidreservoir by particular detecting the pressure in the Hydraulikfiuidreservoir.
  • the hydraulic fluid from the Hydraulikfiuidreservoir is conveyed out by means of a conveyor, whereby the hydraulic piston can be additionally extended when the additional spring has length.
  • the spring arrangement is additionally extended.
  • the auxiliary spring is to be fixed at its first and its second end, so that they can not move unintentionally by contracting from their position.
  • the spring arrangement comprises a hydraulic line and a hydraulic fluid reservoir which is hydraulically fluidically connected to the hydraulic chamber via the hydraulic line and which has an actuating piston and an actuating piston drive with which the actuating piston is displaceable in such a way that the hydraulic fluid is displaced by means of the actuating piston Hydraulic chamber can be brought into it.
  • the hydraulic piston is displaceable away from the second end of the additional spring and thus can be changed in its position.
  • This displacement of the hydraulic piston can also be done against the resistance of the main spring via the stop.
  • the actuator piston drive is a manual drive or a servomotor with a spindle or an eccentric.
  • the actuating piston is arranged freely displaceable in the hydraulic fluid reservoir and the actuating piston drive is designed as a displaceable actuating piston stop which limits the movement of the actuating piston when the hydraulic fluid is discharged from the hydraulic chamber and can displace the actuating piston in such a way that the hydraulic fluid enters the hydraulic chamber can be brought.
  • the abutment abuts against the hydraulic piston during compression of the suspension strut, it is moved by the abutment in the direction of the first end, so that the hydraulic fluid escapes from the hydraulic chamber and is transported into the hydraulic fluid reservoir, as a result of which the adjustment piston is displaced accordingly.
  • the displacement of the actuating piston is limited by the position of the actuating piston stop.
  • control piston stop is displaceable, the end position of the actuating piston and thus the end position of the hydraulic piston by means of the actuating piston can be fixed. If the adjusting piston stop is adjusted by means of the actuating piston drive moves out of the end position to the front, when the actuating piston abuts the control piston stop, so the hydraulic fluid is pressed out of the Hydraulikfluidreservoir out back into the hydraulic chamber by means of the actuating piston, whereby the hydraulic piston moves away from the second end of the auxiliary spring.
  • the spring assembly comprises an intermediate piece on which the stopper is formed and which has a first shoulder, on which the auxiliary spring is supported with its second end, and a second shoulder, on which the main spring is supported.
  • the spring arrangement comprises a hydraulic cylinder which forms the hydraulic chamber and is supported relative to the second end of the auxiliary spring.
  • the spring arrangement comprises a plurality of auxiliary springs, which are connected in series or in parallel with the main spring.
  • the spring rate of the spring arrangement can be adjusted by a corresponding actuation of the stops of the additional springs.
  • An inventive alternative to the spring arrangement according to the invention comprises a main spring, a slider, a stopper and at least one additional spring, which is arranged parallel to the main spring and a first in the direction of compression of the spring assembly displaceable, free end on which the stopper is fixed, and a on the first end remote from the second end, with respect to which the slider is fixable, the position of which is adjustable such that when the spring has overcome the first end of a predetermined compression travel during compression of the spring assembly, the stop abuts the slide and thereby the auxiliary spring is connected in parallel with the main spring.
  • the alternative spring arrangement comprises a hydraulic chamber and the spool as a hydraulic piston arranged in the hydraulic chamber, which is displaceable by means of a hydraulic fluid when it is introduced into the hydraulic chamber to the second end, so that the predetermined compression travel is shortened, and by means of the hydraulic fluid, as it is discharged from the hydraulic chamber, is displaceable away from the second end, so that the predetermined compression travel is extended, and which is supported by the hydraulic fluid, when the hydraulic chamber is tightly sealed, at the second end positionally immovable.
  • the alternative spring arrangement on an intermediate piece on which the stopper is formed and which has a first shoulder on which the auxiliary spring is supported with its first end.
  • the intermediate piece on a pressure spring and a second shoulder on which the pressure spring is supported, so that the intermediate piece is fixed to the first end.
  • 1 shows a longitudinal section of a first embodiment of the strut according to the invention, which is in a first operating state
  • 2 shows a longitudinal section of the first embodiment of the strut according to the invention, which is in a second operating state
  • FIG. 3 is a longitudinal section of the first embodiment of the strut according to the invention, which is in a third operating state
  • FIG. 8 is a longitudinal section of a second embodiment of the strut according to the invention, which is in a first operating state
  • FIG. 9 shows a longitudinal section of the second embodiment of the strut according to the invention, which is in a second operating state
  • 10 is a longitudinal section of the second embodiment of the strut according to the invention, which is in a third operating state
  • 11 is a longitudinal section of the second embodiment of the strut according to the invention, which is in a fourth operating state
  • Fig. 12 is a longitudinal section of the second embodiment of the strut according to the invention, which is in a fifth operating state.
  • a shock absorber 10 has a shock absorber 12. At the shock absorber 12, a bearing eye 14 is provided, to which a body of a motor vehicle (not shown) can be stored. Further, the strut 10 has a main spring 16 and an auxiliary spring 18.
  • the main spring 16 is connected in series with the auxiliary spring 18, which has a first end 18 a, which faces the main spring 16, and a second end 18 b, which faces away from the main spring 16.
  • the main spring 16 is rotationally symmetrical and the additional spring 18 is formed as a helical spring, wherein the main spring 16 and the auxiliary spring 18 are together with the shock absorber on a common axis.
  • an auxiliary spring base 20 is fixed, on which the second end 18 b of the auxiliary spring 18 is supported.
  • the strut 10 has an intermediate piece 22 which is located between the main spring 16 and the auxiliary spring 18.
  • the intermediate piece 22 has a first shoulder 24, which is arranged facing the auxiliary spring base 20 and on which the second end 18 b of the auxiliary spring 18 is supported.
  • the intermediate piece 22 has a second shoulder 26, on which the main spring 16 is supported.
  • the auxiliary spring 18 has a radial extent which is greater than that of the main spring 16.
  • the first shoulder 24 and the second shoulder 26 of the intermediate piece 22 are arranged offset in the direction of the common axis, so that the main spring 16 behind the first end 18a of the auxiliary spring 18 attacks.
  • a hydraulic cylinder 28 is provided which defines an annular hydraulic chamber 29.
  • a hydraulic piston 30 is arranged, which is displaceable along the common axis.
  • the suspension strut 10 has a hydraulic fluid reservoir 34 and a hydraulic line 32 which connect the hydraulic chamber 29 and the hydraulic fluid reservoir 34 in a fluid-conducting manner.
  • the hydraulic chamber 29, the hydraulic line 32 and the hydraulic fluid reservoir 34 are filled with a hydraulic fluid.
  • the intermediate piece 22 has a stop which extends from the main spring 16 in the direction of the second end 18 b of the auxiliary spring 18.
  • the stopper 31 is arranged in the direction of displacement of the hydraulic piston 30 in alignment therewith. As shown in Figs. 1 and 2, the stopper 31 has a free end abutting the hydraulic cylinder 28.
  • the first embodiment of the strut 10 has in the hydraulic line to a first check valve 36, a second check valve 38 and a shut-off device 40. Both the first check valve 36, and the second check valve 38 and the shut-off device 40 are selectively switchable in the hydraulic line 32.
  • the first check valve 36 has a flow direction that points from the hydraulic fluid reservoir 34 to the hydraulic chamber 29.
  • the second check valve 38 has a flow direction that points from the hydraulic chamber 29 to the hydraulic fluid reservoir 34.
  • the first check valve 36 is connected in the hydraulic line 32. Thereby, the hydraulic fluid, which is located in the hydraulic fluid reservoir 34, the first check valve 36 passing into the hydraulic chamber 29 to flow. This is particularly the case when the pressure of the hydraulic fluid in the hydraulic fluid reservoir 34 is higher than the pressure of the hydraulic fluid in the hydraulic chamber
  • Hydraulic fluid is prevented from the hydraulic chamber 29, so that the hydraulic piston 30 remains in its position. This is the circuit "hard spring”.
  • shut-off device 40 If the shut-off device 40 is switched into the hydraulic line 32 (see FIG. 6), then the flow of the hydraulic fluid through the hydraulic line 32 is blocked so that the change of the spring characteristic from "soft spring” to "hard spring” results.
  • the strut 10 has in the hydraulic fluid reservoir 34 a freely displaceable actuating piston 42 and arranged in the hydraulic fluid reservoir 34 control piston stop 44, which is driven by a control piston drive 46. If the actuating piston 42 is pressed from right to left by the actuating piston stop 44 and the actuating piston drive 46 in FIG. 7, the hydraulic fluid in the hydraulic fluid reservoir 34 is introduced into the hydraulic chamber 29 through the hydraulic line 32. As a result, the hydraulic cylinder 30 is pressed down in Fig. 2 against the stop 31. During rebound of the shock absorber 10, the hydraulic piston 30 can follow the stop 31.
  • the actuating piston 42 is freely displaceable in the direction of the actuating piston stop 44 in the hydraulic fluid reservoir 34.
  • the hydraulic booster 30 is pressed into the hydraulic cylinder 28 by the stop 31 during compression of the strut 10
  • the hydraulic fluid is transported from the hydraulic chamber 29 through the hydraulic line 32 into the hydraulic fluid reservoir 34.
  • the adjusting piston 42 moves in an analogous manner to the hydraulic piston 30 in Fig. 2 seen to the right until it abuts the control piston stopper 34.
  • both the range of movement of the actuating piston 42 and of the hydraulic piston 30 is limited by means of the actuating piston stop 34.
  • the actuating piston drive 46 is set up such that the actuating piston stop 44 can be brought into a first end position and into a second end position. At the first end position, the actuating piston stop 44 extends less into the hydraulic fluid reservoir 34 than at the second end position.
  • the strut 10 has a soft spring characteristic, since both the main spring 16 and the additional spring 18 are pressed in during compression. If, with the aid of the actuating piston drive 46, the adjusting piston 42 is moved from the first end position in the direction of the second end position, the hydraulic piston 30 moves away from the second end 18b of the auxiliary spring 18 in an analogous manner to the adjusting piston 42. As a result, the strut 10 moves during compression a soft spring characteristic until the stop 31 abuts the hydraulic piston 30. Then the strut 10 has a hard spring characteristic with further compression.
  • Additional spring 18 in the unloaded state has.
  • the additional spring 18 during compression of the strut 10 is no longer compressible, so that when compression of the strut 10, only the main spring 16 is compressed.
  • the strut 10 has a hard spring characteristic.
  • a second exemplary embodiment of a suspension strut has 50 parts which have the same designation as corresponding parts of the strut 10 according to FIGS. 1 to 3. The identically named parts are comparable.
  • the strut 50 has the main spring 16 and the auxiliary spring 18, which are connected in parallel.
  • the main spring 16 is disposed concentrically within the main spring 18.
  • the strut 50 has a main spring base 52 which is fixedly secured to the shock absorber 12 and to which the main spring base 16 is firmly supported with its one end.
  • the main spring base 52 By means of the main spring base 52, the main spring 16 is connected in the strut 50 such that the main spring 16 is compressed and springs in accordance with all spring movements of the shock absorber 50.
  • the first end 18 a of the auxiliary spring 18 is supported on the first shoulder 24 of the intermediate piece 22. At the side facing away from the additional spring 18 side of the intermediate piece 22 of the stop 31 is settled, which is provided on the second shoulder 26.
  • the hydraulic piston 30 can be applied to the stop 31 when the hydraulic piston 30 is brought into the corresponding position relative to the intermediate piece 22. Furthermore, the intermediate piece 22 with the second shoulder 26 on the main spring base 52 in the longitudinal direction of the shock absorber 12 can be supported.
  • the intermediate piece 22 is slidably disposed parallel to the longitudinal direction of the shock absorber 12 and disposed between the hydraulic piston 30 and the main spring base 52 in the longitudinal direction of the shock absorber 12, so that the hydraulic piston 30 is a displacement of the intermediate piece 22 in one direction and the main spring base 52 a displacement of the intermediate piece 22 in the other direction limit.
  • the hydraulic piston 30 is arranged such that the intermediate piece 22 between the hydraulic piston 30 and the main spring base 52 is clamped.
  • the main spring 16 and the auxiliary spring 18 are connected in parallel, so that upon compression of the strut 50 both the main spring 16 and the auxiliary spring 18 yield and the strut 50 has a stiff spring characteristic.
  • the intermediate piece 22 is displaceable in the direction of the hydraulic piston 30 in the longitudinal direction of the shock absorber 12. If the strut 50 springs in, the main spring 16 is compressed, whereas the additional spring 18 remains in its original length, since the first end 18a of the additional spring 18 can move with the intermediate piece 22 in the direction of the hydraulic piston 30.
  • the strut 50 has a pressure spring 54 which is supported on the additional piece 22 and this presses in the direction of the auxiliary spring 18. There- it is achieved that in each operating state of the strut 50, the intermediate piece 22 rests with the first shoulder 24 at the first end 18a of the auxiliary spring 18. Thus, it is prevented that the first end 18a of the auxiliary spring 18 lifts from the shoulder 24 of the intermediate piece 22 and thereby causes a noise, such as rattling or rattling.
  • the strut 50 is subjected to a tensile load.
  • the main spring 16 is pulled apart.
  • the strut 50 is configured such that under the tensile load, the auxiliary spring 18 is not pulled apart. This is achieved by designing the spacer 22 to be slidable over the main spring base 52. As a result, the intermediate piece 22 is moved over the main spring base 52 by the pressure spring 54, wherein the intermediate piece 22 is pressed against the first end 18a of the auxiliary spring 18 and so when pulling the main spring 18, the first end 18a is tracked.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

L'invention concerne un ensemble ressort (10) comportant un ressort principal (16), un coulisseau (30), une butée (31) et au moins un ressort additionnel (18) monté en série avec le ressort principal (16) et comportant une première extrémité (18a) sur laquelle est fixée la butée (31) ainsi qu'une deuxième extrémité (18b) à l'opposé de la première extrémité (18 a), le poussoir (30) pouvant être fixé relativement à cette deuxième extrémité. La position du poussoir est réglable de manière à ce que, lorsque le ressort additionnel (18), lors de la compression de l'ensemble ressort (10), a dépassé une course de compression déterminée, la butée (31) appuie contre le coulisseau (30), empêchant ainsi une plus grande compression du ressort additionnel (18). L'invention porte également sur une jambe de force d'un véhicule à moteur dotée de cet ensemble ressort (10). Sur un autre ensemble ressort (50), le ressort additionnel (18) est parallèle au ressort principal (16) et la première extrémité (18a) est mobile librement dans le sens de compression de l'ensemble ressort (50), la position du coulisseau (30) étant réglable de manière à ce que la première extrémité (18a), lors de la compression de l'ensemble ressort (50), a dépassé une course de compression déterminée, la butée (31) appuie contre le coulisseau (30), le ressort additionnel (18) étant alors couplé en parallèle au ressort principal.
EP08716448A 2007-04-02 2008-03-12 Ensemble ressort à rigidité de suspension variable et jambe de force dotée d'un ensemble ressort de ce type Withdrawn EP2129538A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007015888A DE102007015888A1 (de) 2007-04-02 2007-04-02 Federanordnung mit verstellbarer Federrate und Federbein
PCT/EP2008/001941 WO2008119443A1 (fr) 2007-04-02 2008-03-12 Ensemble ressort à rigidité de suspension variable et jambe de force dotée d'un ensemble ressort de ce type

Publications (1)

Publication Number Publication Date
EP2129538A1 true EP2129538A1 (fr) 2009-12-09

Family

ID=39338256

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08716448A Withdrawn EP2129538A1 (fr) 2007-04-02 2008-03-12 Ensemble ressort à rigidité de suspension variable et jambe de force dotée d'un ensemble ressort de ce type

Country Status (4)

Country Link
US (1) US20090302559A1 (fr)
EP (1) EP2129538A1 (fr)
DE (1) DE102007015888A1 (fr)
WO (1) WO2008119443A1 (fr)

Families Citing this family (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007044538A1 (de) * 2007-09-11 2009-03-12 Wohlfarth, Klaus Einrichtung zur Höhenverstellung
DE102008006087A1 (de) * 2008-01-25 2009-07-30 Thyssenkrupp Bilstein Suspension Gmbh Federbein mit verstellbarem Federteller
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