Machine element or mechanism – Control lever and linkage systems – Multiple controlled elements
Utility Patent
1999-01-28
2001-01-02
Herrmann, Allan D. (Department: 3682)
Machine element or mechanism
Control lever and linkage systems
Multiple controlled elements
C074S335000, C074S470000, C074S473290, C403S286000, C403S350000, C403S353000
Utility Patent
active
06167773
ABSTRACT:
BACKGROUND OF THE INVENTION
1. Field of the Invention
The invention relates to an adjusting device in a motor vehicle for the automatic operation of a gear-change device having a shifting shaft with linear drives for introducing a linear movement and a translatory movement to the shafting shaft.
2. Description of the Related Art
An adjusting device in a motor vehicle for the automatic operation of a gear-change device is already known, for example, from DE 43 11 855 A1. In this prior art device, drives are pressurized for the automatic operation of the gear-change device. More specifically, the drives include hydraulic cylinders with piston rods that execute a linear movement when activated, whereby the piston rods form output parts of the drives. At least the cylinder provided for the introduction of a rotational movement of the shifting shaft is connected to the shifting shaft via a ball-and-socket joint connection, as shown in FIG. 25 of this reference. This ball-and-socket joint has an articulated input element with a recess, in which a ball head of an articulated output part is mounted, so that a rotational movement of the shifting shaft results from a translatory deflection of the input part.
A problem with this prior art device is that such articulated connections have play, due to manufacturing tolerances and material fatigue. The play requires that a distance must be traveled by the piston rods of the hydraulic cylinders when the operating direction is changed before the shifting shaft moves in response to the introduced movement.
SUMMARY OF THE INVENTION
The object of the invention is to further develop a gear actuator that precisely positions the shifting shaft so that each introduced movement results in a predetermined movement of the shifting shaft.
The object of the invention is attained by an adjusting device for automatically operating a gear-change having a shifting shaft, includes a first linear drive with a first output part connectable to the shifting shaft for introducing a rotational movement of the shifting shaft via an articulated connection and a second linear drive having a second output part connectable to the shifting shaft for introducing a translatory movement of the shifting shaft. The articulated connection has first and second support elements held relative to teach other by a prestress force and an articulated element held between said first and second supports by said prestress force.
The measure of equipping the gear actuator with an articulated connection for converting a translatory movement introduced by a linear drive into a rotational movement, whereby the articulated connection has at least two support elements, which are prestressed relative to each other in such a way that an articulated element remains in uninterrupted active connection with the support elements in an articulated and force-locking fashion, creates an articulated connection with no play. Manufacturing tolerances may be compensated for by this design. The freedom from play ensures that each movement introduced via the linear drive results in a movement of the shifting shaft. As a result, the shifting shaft can be precisely positioned in a predetermined manner upon precise activation of the linear drive. Dead times, which, if play exists, must be calculated into the transmission path, do not occur. As a result, the reaction speed of the gear actuator is increased. The amount of prestress of the support elements is selected so that a force locking connection is ensured even in the event of plastic deformation of the support elements and/or the articulated output element. Such plastic deformation may result from the prestress force that acts on the support elements and the articulated element to ensure the uninterrupted force lock, as well as from wear due to age.
In an advantageous embodiment, the articulated element is mounted in a rotation-proof fashion and axially movable in the direction of the shifting shaft. For example, the articulated element may be connected to the shifting shaft via a longitudinal toothing. Such rotation-proof connections are smooth-running, so that the transverse force acting on the articulated output element upon a translatory movement of the shifting shaft is negligible. In addition, the work consumed by friction on the toothing is slight and thus negligible.
In another advantageous embodiment, the articulated element is securely connected to the shifting shaft and, in particular, is embodied in one piece with the shifting shaft. In this way, the number of required parts is reduced, which reduces manufacturing costs. Decoupling of the translation and rotational movements of the shifting shaft can be realized via axial mobility of the articulated output element in the axial direction of the shifting shaft relative to the support elements. The connected surfaces of the articulated element and the support element should be embodied as smoothly as possible, so that the work consumed by friction upon relative movements is as low as possible. It can also he advantageous to embody the articulated element and the support elements with reciprocally matching contours, so that the surface supporting the articulated element on the support element is, as needed, as large as possible, in order to attain low area pressure, or as small as possible, in order to attain the smallest friction area possible. With a small support surface, only small partial areas of the support elements need be embodied with a smooth surface to ensure a smoothly-running relative movement of the contacting surfaces.
In another advantageous embodiment, a support element is embodied in one piece with the output part of the linear drive provided for the introduction of the rotational movement of the shifting shaft. This support element is preferably equipped with a connecting element, by means of which a further support element is mounted movably relative to the First support element. Without modifying the basic structure, the support elements may also be embodied in multi-part fashion, or multiple support elements may be associated with the first support element. In the previously described arrangement, final assembly is easy to carry out, in that the second support element is placed on the connecting element. To provide the prestress of the support elements relative to each other, a spring element is preferably provided. If a simple-acting cylinder is used as a linear drive, it has proved advantageous for the return spring associated with the simple-acting cylinder to rest against a stationary part or against the second support element. The effective spring force of the return spring presses the second support element in the direction of the first support element, whereby the two support elements are oriented parallel to the shifting shaft. As a result, a decoupling of the rotational movement from the translatory movement is ensured.
In some applications, the articulated element may be arranged on the drive side, in particular, in one piece with the output part of the linear drive in the form of a projection. In such an embodiment, the support elements are arranged on the shifting shaft side. If a simple-acting cylinder is used as the linear drive, then the prestress of the support elements relative to each other can again be provided by the return spring, which rests against a support element. In this embodiment, the support element on the return spring side can be dipensed with, and the return spring then rests against the articulated element, so that the articulated element and the support element are actively connected in a force-locking manner.
It has proved advantageous to provide at least two support elements so that the return Spring rests against the articulated element and so that no transversal force relative to the spring force of the return spring acts on the return spring. Such a transversal force could result in eccentricity of the return spring, accompanied by a shortened useful life. To prestress the support elements, a separate spring element is provided. The su
Dorfschmid Jens
Ratte Andreas
Cohen & Pontani, Lieberman & Pavane
Herrmann Allan D.
Mannesmann Sachs AG
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