Fichtel & Sachs Ag

Mannesmann Sachs Ag

Otto Samonil

Manfred Grundei

Gunther Handke

Gunther Braun

Andreas Zietsch

Wolfgang Zirk

Sabine Lack

Steffen Kraus

A vibration damper with variable damping force, including a cylinder, in which a piston with a piston rod is arranged in axially movable fashion, whereby an adjustable damping valve is activated in dependence on the deflection distance and the activation of the adjustable damping valve is carried out via a stabilizer. The vibration damper has further damping valves, whose damping effects are independent of activation by the stabilizer. The adjustable damping valve, during equilateral deflection and rebound travel of the piston rod on a vehicle axle or unilateral rebound travel, has a damping force setting that is smaller than the damping force of the further damping valves of the vibration damper.

Vibration damper with variable damping force

A vibration damper includes a pressure tube in which a piston on a piston rod which can move axially is guided by means of a piston rod guide which closes the pressure tube. The piston divides the pressure tube which is filled with damping medium into two working chambers. A piston ring which covers a peripheral area of the piston has an essentially U-shaped cross section with retaining surfaces, whereby the retaining surfaces are supported on the upper and lower side of the piston. On at least one side of the piston, at least a portion of the piston on which the retaining surfaces of the piston ring are engaged has a profiled surface. The profiled surface is configured such that the distance between one side of the piston and a hypothetical reference plane which runs parallel to the piston side is alternately less than and greater than a specified size of fit.

Vibration damper

A motor vehicle suspension system for damping vibrations between, for example, the wheels of the motor vehicle and the body of the motor vehicle, can have a vibration damper unit with two fluid chambers therein and separated from one another by a piston unit. In addition, there can be a fluid bypass connecting the two chambers. A shut-off valve device can be disposed between two portions of the fluid connection to separate a high-pressure section and a low-pressure section, and the latter shut-off valve has a shutoff body which can be adjusted by an external control by means of a magnet armature and a magnet coil between a closed and an open position. The high pressure section empties into a central channel, and a first side of the shut-off valve body which is pressurized by the high pressure section can be elastically pressed against a shut-off valve seat by means of a compression spring, whereby the first side of the shut-off valve body is connected by means of an after-throttle to a second side of the shut-off valve body. Within the fluid connection there can be a segment which provides a pressure reduction by means of at least one throttle point in combination with a baffle device which is connected to the throttle point.

Vibration damper for a motor vehicle suspension

A shock absorber with a check valve device and a check valve device for a shock absorber is disclosed. The check valve device located in the bypass of a shock absorber between a high-pressure segment and a low-pressure segment has a check valve which can be moved by an external control into a standby opening status, in which the actual opening can be performed as a function of the pressure prevailing in the high-pressure segment, when the pressure falls below a predetermined value. By coordinating the stroke distance of a check valve body with a magnet armature, and taking into consideration a control chamber discharge cross section, noises and fluctuations of the damping force characteristic can be eliminated even with a very soft comfort setting of the check valve device.

Shock absorber with a check valve and a check valve for a shock absorber

An oscillation damper is provided with a by-pass that includes a by-pass valve. The by-pass valve is switchable between an open position and a closed position. When the by-pass valve is moved between the open and closed positions, the rate of change of the cross-sectional area of the by-pass valve during the time when the by-pass valve is adjacent the closed position is considerably less than the average rate of change of the cross-sectional area during the entire time that it takes for the by-pass valve to switch between the open and closed positions.

Growing community of inventors

Niederwerrn, Germany

Otto Samonil