Daimler-benz Ag

Mercedes-benz Aktiengesellschaft

Jurgen Pickard

Hermann Gaus

Gunter Jurgens

Georg Eltze

Helmut Sandner

Klaus Luttge

Wolfgang Zaiser

Heinz Schultz

Josef Helmer

Jurgen Frank

Werner Sell

Hans Rubmann

Walter Robmann

In a toothed-wheel change gear, a gear pump for the conveyance of transmission oil is arranged in a separate gearbox chamber of a gearbox. Leakage oil flowing out at the gear pump is intermediately stored in the gearbox chamber in a controlled manner.

Toothed-wheel change gear pump for conveyance and a gearbox for

In a brakeband, two side bands extend from a connecting portion in one circumferential direction and a middle band located axially between these side bands extends from it in the other circumferential direction. The band ends of the two side bands (located opposite the connecting portion) are widened in the direction of the middle band, while the middle band is narrowed at its circumferentially corresponding band region. This provides a larger cross-section for the welded joint between the respective widened band ends of the two side bands and a circumferentially adjacent thrust piece of the brake actuating device.

Brakeband

A piston for actuating a brake-band end of a transmission band system includes a piston for actuating a band in a transmission. The piston includes a piston body, and an elongated guide shaft having a proximal end fixed to one side of the piston body and a distal end defining a first annular support surface. The guide shaft is formed to include an axial bore having an opening in the first annular support surface. The piston further includes a piston rod having an outer end for engaging the transmission band, an inner end for reception in the axial bore, and a second annular support surface situated to confront the first annular support surface when the inner end of the piston rod is received in the axial bore of the elongated guide shaft. An O-ring is positioned along the inner end of the piston rod, to retain the inner end within the axial bore of the elongated shaft. At least one spacer mean is situated intermediate the first and second annular support surfaces to separate the annular support surfaces to vary the effective length of the piston rod.

Piston of a pressure-medium actuator with a piston rod of adjustable

In a lock-up clutch, an annular piston has a clutch friction disc connected to the annular piston and a seal hub, which is connected to the annular piston and rotatably slipped over a counterseal hub. A damper using a spring and a damper supplying frictional resistance are located on the end face of the annular piston facing towards the casing shell. The dampers are connected, on the drive side, with at least one damper drive part connected to the annular piston and, on the output side, with a radially inner clutch hub positively engaged to a rotor hub connected to the turbine rotor. The pressure surface of the annular piston is designed independently of the dimensions of the dampers because the counterseal hub is fixed on the rotor hub. A front hub protrusion connected rotationally solidly with the clutch hub and facing the rotor hub centers damper discs. An axially small space exists when the counterseal hub is located at a transition between the outer shell and the connecting flange and the hub protrusion facing the rotor hub is located radially inside the counterseal hub.

Lock-up clutch with a front-mounted piston damper module for a

In a multi-disc clutch or brake, several lamellae in the form of annular discs cannot only be fixed essentially non-rotatably, relative to a lamella carrier fixed in terms of rotation in relation to one of the two clutch or brake parts, by means of a releasable positive connection but can also each be supported radially exclusively at an individual point on the lamella carrier, each by means of its own resilient clamping means, the clamping means being retained on the lamella carrier. At least one central annular gap located, in the peripheral direction of the axis of rotation, between two engaging teeth of the positive connection and open in the two directions of the axis of rotation is limited radially in one directions by a cylindrical shell portion of a lamella and in the other direction by a cylindrical shell portion of the lamella carrier. The engagement surface of the clamping means, used for the purpose of support, is located in the annular gap and interacts with the shell portion of the lamella. So that even thinner lamellae can be used, the two clamping means for two lamellae succeeding one another in the directions of the axis of rotation are arranged on different legs of a comb-shaped holder. Each leg of the holder can be inserted into a separate annular gap.

Multi-disc clutch or brake with a resilient clamping means insertable

A change-speed transmission for motor vehicles, with the transmission including a planetary gear transmission arrangement having a pair of sun gears, a pair of ring gears, and a double webbed planetary gear carrier supporting at least one primary planetary gear and at least one secondary planetary gear. The primary planetary gear meshes with one of the sun gears and the secondary planetary gear meshes with the primary planetary gear and the other of the sun gears. One sun gear, acting as a free transmisson member and one ring gear are respectively adapted to be brought into an operative connection by a gear shift brake arrangement. The other sun gear as well as a further transmission member may be placed in a driving connection with the input shaft of the transmission. Both ring gears mesh with the primary planetary gear and one of the ring gears as well as the transmission member acting on the output shaft may be brought into driving connection respectively with one transmission member of a planetary gear coupling transmission. An additional transmission member of the planetary gear coupling transmission is adapted to be connected to the output shaft of the transmission.

Planetary change-speed transmission for automotive vehicles

A vane for a hydraulic vane pump, with the vane being adapted to be inserted, with sliding movement, into a guide slot provided in a rotor so as to be symmetrical and parallel to a central plane of the slot. The plane forms a setting angle at an outer jacket of the rotor together with an axial plane containing the rotor axis so that an opening of the slot located at the outer jacket of the rotor leads the bottom of the slot in a direction of rotation. A convex sliding sealing surface cooperates with inner jacket of the stator and a pressure surface is located in the plane directed toward a bottom of the slot. A crown of the sliding sealing surface is displaced, with respect to the principle plane of the vane, in a direction opposite the rotational direction of the rotor. The sliding sealing surface forms, in a direction of rotation of the rotor, a wedge-shaped transistional area located at a plane which forms a complimentary angle combined with an addendum angle to the principle plane of the vane. The pressure surface forms, with the principle plane of the vane, a complimentary angle and, when combined with a re-setting angle, forms a 90.degree. angle. The angle formed by the pressure surface is such that a pressure which results at the pressure surface includes a balancing pressure component which is directed approximately at right angles to the principle plane of the vane and approximately in a direction opposite to the rotational direction of the rotor.

Vane of a vane pump for hydraulic operating medium

A change-speed transmission which includes an input shaft and an output shaft which are drivingly connected by a forward and rearward planetary gear system. The forward planetary gear system includes two planetary gears one of which meshes merely with a sun gear with the other planetary gear meshing with a further sun gear as well as with a ring gear. The planetary gears are carried by a double carrier which is drivingly connected with one transmission member of the rearward planetary gear system with the ring gear being drivingly connected with another member of the rearward planetary gear system by way of respective torque transmitting coupling trains. A change-speed clutch for producing a direct transmission of the rearward planetary gear system is operatively connected with the double carrier which is also drivable through a gear shifting clutch by way of the input shaft. The sun gear of the planetary gear system which does not mesh with the ring gear is positionally arranged between the other sun gear of the forward planetary gear system and the output shaft with the sun gear being drivable through a further gear shifting clutch by way of the input shaft.

Change-speed transmission

A securing arrangement for planet bolts in planetary gear change-speed transmissions, especially those for motor vehicles, in which all planet bolts are secured against axial displacement on one side by means of a common sheet metal locking plate adapted to be fixed at the planet gear carrier. Each planet bolt is provided on its side facing the locking plate with an annular groove for mounting therein a securing ring while the bores in the planet gear carrier intended for the accommodation of the planet bolts are enlarged on the side facing the locking plate into an axial groove open toward the outside so that after the insertion of the bolts together with the securing rings, the locking plate can be mounted axially over all bolts.

Securing device for planet bolts in planetary gear change-speed

A primary pump drive for automatic motor vehicle transmissions, in which the primary pump is adapted to be driven directly from the input and is arranged with its axis parallel to the input axis. The pump is constructed as an internally toothed pump and its internally toothed wheel is provided with teeth at the external circumference thereof, into which engage the teeth of a gear connected with the input.

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Wernau, Germany

Jurgen Pickard