Daimler-benz Ag

Bruno Beeskow

Gunter Worner

Rudolf Hornig

Peter Schrape

Wolfgang Pfundstein

Egon Bauer

A pressure relief valve for the working pressure of a servo-steering mechanism of a vehicle, with a pressure medium connection between a high pressure connection adapted to be placed under a working pressure and a zero connection adapted to be placed under a lower pressure, whose valve-adjusting member is retained in a normal rest position closing off the pressure medium connection during normal conditions by a control device operating as a function of an operating magnitude of the servo-steering mechanism and which upon exceeding a critical value of the operating magnitude is adapted to be displaced into a by-pass position more or less opening up the pressure medium connection; the control device thereby operates in dependence on the load of the servo-steering mechanism while the by-pass position is independent of the angle of rotation of the steering shaft of the servo-steering mechanism.

Pressure relief valve for the working pressure of a servo-steering system

An installation for damping vibrations of a drive axle, especially of a rear axle, of motor vehicles, in which the driving pinion of the differential gear which meshingly engages with the spur bevel gear, is driven by way of a universal joint shaft and in which the output from the differential gear onto the axle half-shafts takes place by way of one synchronizing joint each; for purposes of changing the resonant frequency of the system, additional annular parts constructed of shell-shape are clamped onto that part of the synchronizing joint which is connected with the output of the differential gear.

Installation for vibration damping of a drive axle, especially of a rear

An elastic shaft coupling, especially a cardan shaft coupling for motor vehicles, which is equipped with a disk-shaped elastic base body, in which are arranged about the center axis of the base body an even number of connecting elements having parallel axes; of these connecting elements, successive ones are coordinated to opposite sides and are connected by way of at least one band loop that is supported on at least one of the respective connecting elements by way of an elastic intermediate member.

Elastic shaft coupling

An installation for damping vibrations in the drive connection of motor vehicles with the aid of a vibration absorber whose absorber mass is constructed as annular body and is connected with at least one driving part of the drive connection by means of an elastic member of rubber or analogous material; the connection between the transmission output shaft and the universal joint shaft is thereby split up from a vibrational point of view by an elastic coupling soft in the radial direction while the vibration absorber is coordinated to the input of the universal joint shaft.

Installation for vibration damping in drive connection of motor vehicles

An installation for damping vibrations in the drive connection of vehicles, especially of motor vehicles, with the aid of a vibration damper whose vibrating mass is constructed as annular body and is connected with a driving part of the drive connection by means of an elastic body; the damper thereby serves for damping the torsional vibrations of the drive connection and also the bending vibrations of the drive shaft while the elastic body is delimited, on the one hand, by a cylinder surface and, on the other, by a polygonal surface.

Installation for vibration damping in drive connections of motor vehicles

A clutch disk for motor vehicle main clutches which is equipped with a disk member carrying the friction linings and torsionally elastically arranged with respect to a hub member, whereby for a multistage torsional elasticity, several springs or spring sets with different characteristics are arranged in windows of one of a hub flange or of the disk member and of a lateral sheet metal member rigidly connected thereto, which cooperate with correspondingly larger windows in the respective other part; friction damping devices are thereby coordinated to the springs, whereby one of the friction damping devices is operable in the idling range and the others are operable in the operating range and the start of operation thereof are determined by control means engaging in the corresponding windows or cooperating with the corresponding spring ends; at least three spring stages of continuously harder characteristics, one friction device for the idling range and two separate main friction devices with control members for the operating range are thereby provided in the clutch disk according to this invention, whereby the control members are so constructed and arranged that the friction disk for the idling range is coordinated to the control member for the first main friction device so that with the beginning of the second spring stage, in lieu of the idling friction device, the effect of the first main friction device commences and the effect of the second main friction device commences still within the range of the second spring stage in such a manner that its damping action starts in addition to the damping action of the first friction device already within the range of the second spring stage by a corresponding dimension of the control member with respect to the windows or spring ends of the third stage.

Clutch plate with multiple spring and friction dampers

A clutch disk for motor vehicle main clutches which includes a disk member carrying the friction linings and torsionally elastically arranged with respect to a hub member whereby for purposes of achieving a multi-stage torsional elasticity, several springs or spring sets with different characteristics are provided in windows of a hub flange or of the disk member and of a lateral member rigidly connected therewith which cooperate with correspondingly larger windows in the other of these two parts; friction damping means are thereby coordinated to these springs whose start of operation are determined by control means which engage into the corresponding windows or cooperate with the spring ends; only the friction of the friction device which has been engaged last, is thereby effective in the operating range whereby two friction devices are provided, of which the first friction device is operatively connected by means of its control spring with the hub flange while the second friction device is operatively connected by means of its control spring with the lateral members; the two control members are thereby connected with each other by a drag-type connection which becomes effective only after the angular path provided for the idling range has been traversed.

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Bietigheim, Germany

Bruno Beeskow