FR2774448A1 - Motor vehicle with automatic transmission - Google Patents

Abstract

The motor vehicle has a drive motor, a transmission and a torque transfer system, or coupling, with an arrangement for automated actuation of the transmission with a control unit, and at least one actuator (100) driven by the control unit for automated gear selection. The control unit has a signal connection to at least one sensor. The actuator has a first drive for actuating a transmission element for changing a gear ratio and a second drive for actuating a transmission element for selecting a gear ratio. The first drive (103) actuates a gear changing transmission element via a first transmission, e.g. a worm gear (107,108) with following star wheel gear. The second drive (104) actuates a gear selection transmission element via a second transmission, e.g. a worm gear (121,122) followed by a star wheel which engages a toothed rod and is rotatably mounted on and axially movable, rotatable shaft.

Description

 The present invention relates to a motor vehicle1 generally designated simply by the term vehicle in the following, comprising a drive motor, a gearbox and a torque transmission system, an automatic gearbox control device. , a control unit and at least one actuator which the control unit can control to automatically switch / select a gear reduction of the gearbox, in which the control unit is in signal connection with at least a sensor and possibly other electronic units, the actuator comprises a first drive for maneuvering a gearbox element to select a gear reduction and a second drive for maneuvering a gearbox to select a gear reduction gearbox.

 Vehicles with automatic gearboxes are known, for example with hydraulic actuators.

The hydraulic operation of the internal switching elements of the gearbox, however, turns out to be very bulky and expensive. It is necessary for example, for hydraulic actuators, bulky elements such as pressure accumulators, valves, and so on.

 It is the aim of the present invention to provide a vehicle with an automated gearbox whose number of parts is reduced, which is more economical and which provides at least an improvement in terms of comfort, for example the comfort of switching. It is also the object of the invention to provide a simple system, which can be mounted in a simple manner, and whose structural volume required is small.

These aims are generally achieved according to the invention by the fact that
the first drive operates an element of the gearbox, intended to select the gear reduction, by means of a second mechanism; and
the second drive operates an element of the gearbox intended to switch the gear reduction, by means of a second mechanism.

This general characteristic of the invention allows in particular four other concepts exposed in the following immediately
Indeed, according to a second concept of the invention, these aims can also be achieved by the fact
the first drive maneuver in the peripheral direction, via a first worm mechanism, a gearbox shaft to select the gear reduction and that
the second drive maneuver in the peripheral direction, by means of a second worm gear mechanism, a gearbox shaft for switching the gearbox reduction.

According to a third concept of the invention, these aims can also be achieved by the fact that
the first drive maneuver in the axial direction, via a first worm mechanism, a gearbox shaft to select the gear reduction and that
the second drive maneuver in the peripheral direction, by means of a second worm gear mechanism, a gearbox shaft to switch the gearbox reduction.

According to a fourth concept of the invention, these aims can also be achieved by the fact that
the first drive maneuver in the peripheral direction, via a first worm gear mechanism, a gearbox shaft to select the gear reduction and that
the second drive maneuver in the axial direction, by means of a second worm gear mechanism, a gearbox shaft to switch the gearbox reduction.

According to a fifth concept of the invention, these aims can also be achieved by the fact that
the first drive maneuver in the axial direction, via a first worm mechanism, a gearbox shaft to select the gear reduction and that
the second drive maneuver in the axial direction, via a second worm gear mechanism, a gearbox shaft for switching the gear reduction.

More specifically, the invention realizes, according to a first aspect, a motor vehicle comprising a drive motor, a gearbox and a torque transmission system, for example a clutch, a device for automatic operation of the gearbox, a control unit and at least one actuator that the control unit can control to automatically switch / select a gear reduction of the gearbox, in which
the control unit is connected to signals with at least one sensor;
the actuator comprises a first drive for maneuvering a gearbox element to switch a gearbox reduction and a second drive, for maneuvering a gearbox element to select a gearbox reduction,
characterized in that
the first drive maneuvers a gearbox element, intended to switch the gear reduction, by means of a first mechanism, for example a worm gear mechanism downstream of which is arranged a spur gear mechanism ; and
the second drive operates an element of the gearbox, intended to select the gear reduction, by means of a second mechanism, for example a worm gear mechanism, downstream of which is arranged a spur gear which meshes with a received rack housed in rotation on a rotating shaft and axially movable.

We can then predict that
the shaft can be raised and lowered, i.e. moved, by means of the second drive by means of a worm mechanism and a gear mounted downstream and the rack, and / or that
the shaft can rotate under the effect of the first drive by means of an endless screw and a worm gear and possibly a spur gear mechanism mounted downstream.

In all these cases, we can also foresee that
the shaft can rotate under the effect of the first drive and can be raised and lowered under the effect of the second drive,
the rack being rotatably mounted but axially fixed on the shaft and cannot rotate relative to the gear which meshes with the rack, when the shaft is rotated.

The rack may have a bore or a slot in the axial direction which receives in rotation but axially fixed an area with reduced diameter of the shaft and,
when the shaft has a reduced diameter area which rotates the rack, one can in particular provide that a limit stop which axially blocks the rack is connected to one shaft.

In that case,
the end stop can be made in one piece with the shaft, or
it can be linked in positive engagement to the tree, or
it can be screwed to the shaft by means of a thread.

The rack may have a central recess which extends in the axial direction, for example a bore, and a slot which extends in the axial direction,
the rack comprising deformable elastic faces which limit the slot.

In this case, this slot of the rack can be arranged in a face area opposite the toothing, and / or
the rack and / or the gear which meshes with it can be made of plastic.

According to a second specific aspect, the invention provides a motor vehicle comprising a drive motor, a gearbox and a torque transmission system, for example a clutch, an automatic gearbox operating device, a control unit and at least one actuator which the control unit can control to automatically switch / select a gear reduction of the gearbox, in which
the control unit is connected to signals with at least one sensor;
the actuator comprises a first drive for maneuvering a gearbox element to switch a gearbox reduction and a second drive, for maneuvering a gearbox element to select a gearbox reduction,
characterized in that
the first drive operates an element of the gearbox, intended to switch the gear reduction, by means of a first mechanism, for example a worm gear mechanism downstream of which is arranged a spur gear mechanism ; and
the second drive operates a gearbox element1 intended to select the gear reduction, by means of a second mechanism, for example a worm gear mechanism, downstream of which is arranged a spur gear which s 'meshes with a toothing which is formed, on a rotary shaft and axially movable, by means of teeth arranged concentrically with the axis of the shaft.

 We will now explain some of the specific methods set out above, as well as others which bring particular advantages for certain embodiments.

 It may be advantageous if the first and / or the second mechanisms are mechanisms with one or more reduction gears.

 It may further be suitable for the first and / or the second mechanisms to include a partial mechanism which is configured as a worm mechanism.

 Similarly, according to another concept of the invention, it may be advantageous for the first and / or the second mechanisms to include a partial mechanism which is configured in the form of a spur gear mechanism, bevel gear mechanisms, hypoid mechanism or similar.

 According to one embodiment of the invention, it is advantageous that another mechanism stage is arranged upstream or downstream of the first and / or second worm mechanism, to control an operation of the switching or selection.

 It may further be appropriate that an additional stage of the mechanism is arranged upstream or downstream of the first and / or of the second worm mechanism to control an operation of the switching or selection process.

 It is also suitable to arrange downstream of the worm gear mechanism a gear and toothed sector mechanism produced in the form of a lever, the mechanism being constituted as a spur gear mechanism, bevel gear mechanism, hypoid mechanism or the like.

 It is further appropriate that the toothed sector with lever configuration is connected via a positive engagement link to a gearbox element intended to select or switch the gearbox. It can also be advantageous for the toothed sector with lever configuration to be formed in a single tent with a gearbox element intended for selecting or switching the gearbox.

 According to another concept of the invention, it may be appropriate for the actuator to comprise a housing in which the drives can at least penetrate and in which are arranged at least substantially the transformation mechanisms of at least one actuator movement of operation of the switching or selection process. I1 may likewise be suitable also that the actuator comprises a housing in which are received at least parts of the control and / or power electronics intended for the control of the automated gearbox.

 It may also be appropriate for at least one drive to be carried out in the form of an electric motor, for example a direct current motor, an alternating current motor, a motor designated by the Anglo-Saxon term of Switched Reluctance-Motor, or SR motor, that is to say with reluctance switched and / or stepper motor.

 It may further be advantageous for the drives, for example the motors, to have drive shafts or motor shafts which are oriented essentially parallel to one another.

 It is further advantageous that the drives, for example the motors, comprise drive shafts or motor shafts which are oriented substantially between them at a previously definable angle.

 It can also be advantageous for the shafts of the drive motors to have axes of rotation, and for the worm mechanisms to have worm gears, such as the axis of rotation of the motor shaft of the first drive. forms a first plane with the worm gear of the first endless mechanism and the axis of rotation of the motor shaft of the second drive forms a second plane with the worm gear end of the second worm mechanism, the first plane being substantially identical to the second plane.

 According to another concept of the invention, it may be appropriate that the shafts of the drive motors have axes of rotation, and that the worm mechanisms include worm gears, such as the axis of rotation of the motor shaft of the first drive forms a first plane with the worm gear of the first worm mechanism and that the axis of rotation of the motor shaft of the second drive forms a second plane with the worm gear of the second worm mechanism, the first plane being arranged substantially parallel to the second plane.

 It may be advantageous if the shafts of the drive motors have axes of rotation, and that the worm mechanisms include worm gears, such that the axis of rotation of the motor shaft of the first drive forms a first plane with the worm gear of the first worm mechanism and that the axis of rotation of the motor shaft of the second drive forms a second plane with the worm gear of the second worm mechanism worm, the first plane being arranged substantially at a previously definable angle relative to the second plane.

 It may also be appropriate for at least one drive to be carried out in the form of an electromagnet, for example in the form of a step magnet.

 According to another concept of the invention, in a vehicle in particular conforming to one of the modalities of the present invention, which includes an actuator which can be controlled by a control unit and a drive for operating an operating element, for example a gearbox element or a torque transmission system, and which is such that at least two substantially disc-shaped elements are arranged in the flow of torque which goes from the drive to the maneuverable element and that at least one force accumulator transmits between these disc-shaped elements a torque when a force urges it, and that this results in a relative rotation of the disc-shaped elements due to the stressing of the force, it it may be advantageous for the elements substantially in the form of discs to have, in their radially outer marginal zones, toothing in the form of incremental emitters and that at least one specific sensor ine at least one speed of rotation of the substantially disc-shaped elements. The sensor can in this case be an inductive, optical, or magnetically sensitive sensor, which detects the increments of the displacement, for example of the rotation, and the control unit determines from there the at least single rotation speed.

 It may then be particularly suitable for the control unit to determine a relative rotation of the elements on the basis of the rotational speeds of the elements substantially in the form of discs.

Likewise, according to another concept of the invention which refers to a vehicle in particular conforming to one of the methods of the present invention, which includes an actuator which can be controlled by a control unit and an operating drive of 'a maneuverable element, for example a gearbox element or a torque transmission system, and which is such that at least two substantially disc-shaped elements are arranged in the torque flow between the drive and the maneuverable element and that at least one force accumulator transmits between these disc-shaped elements a torque when a force urges it, and that this results in a relative rotation of the disc-shaped elements due to the stress of the force, it may be advantageous for the elements substantially in the form of discs to have, at their radially outer marginal zones, magnetized zones which comprise, in view along the periphery , a series of magnetic poles and that at least one sensor detects by means of the resulting magnetic field generated by these magnetic poles at least a speed of rotation of the substantially disc-shaped elements and / or a relative rotation of the disc-shaped elements relative to each other
It is further advantageous that the marginal zones of the elements substantially in the form of discs, for example discs, are provided with a magnetization with poles arranged alternately, the orientations of the magnetic poles of the two discs being the same in a state without rotation. relative so that it essentially results in a magnetic field, which has field lines in the plane of the discs / perpendicular to the plane, while it results in a state of relative rotation a magnetic field with field lines also perpendicular to the plane / in the plane of the discs.

 I1 can also be advantageous for at least one sensor to detect a magnetic field component, this magnetic field component disappearing substantially in the absence of any relative rotation and for this magnetic field component to increase at least at the start of relative rotation, the sensor sending a signal representing a relative rotation.

 It is also appropriate that the first substantially disc-shaped element comprises, in its radially outer zone, magnetic poles with alternating magnetization distributed over the periphery, that the second substantially disc-shaped element has tongues of the same magnetization spaced apart on the periphery, which cover the poles with opposite magnetization of the first disc in the state without relative rotation and discover them increasingly at least at the start of the relative rotation, at least one sensor detecting the resulting magnetic field as a function of the relative rotation.

 It is advantageous, according to the concept of the invention, for the tabs of the second substantially disc-shaped element to be arranged between the magnetic blades of the first substantially disc-shaped element and the sensor.

 It is also suitable that the configuration of the tongues is parallel to a plane of one of the disc-shaped elements in the marginal zone of the disc-shaped element and that the magnetic zone of the other disc-shaped element is oriented in this plan.

 It is also appropriate that the configuration of the tongues is substantially perpendicular to a plane of one of the disc-shaped elements at the marginal zone of a first disc-shaped element and that the orientation of the magnetized zone of the another disc-shaped element is substantially perpendicular to this plane, and that the tongues at least partially envelop in the axial direction the marginal zone of the other disc-shaped element.

 It is also appropriate that the magnetized zone of the other disc-shaped element, the orientation of which is substantially perpendicular to a plane of the disc-shaped elements, is the marginal zone erected perpendicular to this plane of a shaped element. disc.

 It is also advantageous for the control unit to determine, by means of at least one characteristic curve of force accumulators, a force stress on the force accumulators arranged between the elements, based on the relative rotation detected or determined. of two elements, and that it thus determines a driving force or a driving torque.

The objects, features and advantages of the invention set out above as well as others will become more apparent from reading the following description of preferred embodiments of the invention, with reference to the drawings in which:
Figure 1 is a schematic representation of a vehicle;
Figure 2 is a cross-sectional view of an actuator according to the invention;
Figure 2a shows a switching slide of a gearbox;
Figure 3 is a cross-sectional view of an actuator according to the invention;
Figure 4 is a cross-sectional view of an actuator according to the invention;
Figure 5a is a cross-sectional view of an actuator according to the invention;
Figure 5b is a cross-sectional view of an actuator according to the invention;
Figure 5c is a cross-sectional view of an actuator;
Figure Ga shows a force accumulator element;
Figure 6b shows a force accumulator element;
Figure 7 shows an actuator and part of a gearbox;
Figure 8 is a cross-sectional view of an actuator according to the invention;
Figure 9 is a cross-sectional view of an actuator according to the invention;
Figure 10 is a cross-sectional view of an actuator according to the invention;
Figure it is a cross-sectional view of an actuator according to the invention;
Figure 12 shows an element of an actuator;
Figure 13 is a cross-sectional view of an actuator according to the invention;
Figure 14 is a table;
Figure 1Sa shows an arrangement of a sensor;
Figure 15b shows an arrangement of a sensor;
Figure 16a is a graph;
Figure 16b is a graph;
Figure 16c is a graph;
Figure 17a is an arrangement of a sensor;
Figure 17b is an arrangement of a sensor;
Figure 17c is an arrangement of a sensor;
Figure 17d is an arrangement of a sensor;
Figure 18a is an arrangement of a sensor;
Figure 18b is an arrangement of a sensor;
Figure 18c is an arrangement of a sensor;
Figure 19a shows a graph
Figure 19b shows a graph
Figure 20 shows a device according to the invention;
Figure 21 shows a device according to the invention;
Figure 22 shows a device according to the invention;
Figure 23 shows a device according to the invention;
Figure 24 shows a device according to the invention;
Figure 25 shows a device according to the invention;
Figure 26 shows a device according to the invention;
Figure 27 shows a device according to the invention;
Figure 28 shows a device according to the invention;
Figure 29 shows a device according to the invention;
Figure 30 shows a device according to the invention;
Figure 31 shows a device according to the invention;
Figure 32 shows a device according to the invention;
Figure 33 shows a device according to the invention;
Figure 34 shows a device according to the invention;
Figure 35 shows a device according to the invention;
Figure 36 shows a device according to the invention;
Figure 37 shows a device according to the invention;
Figure 38 shows a device according to the invention;
Figure 39 shows an operating device according to the invention;
Figure 40 shows an operating device according to the invention;
Figure 41a is a cross-sectional view of Figure 39;
Figure 41b is a front view of Figure 39;
Figure 41c is a cross-sectional view of Figure 39;
Figure 42 is a fragmentary view of an operating device;
Figure 43 shows the gearbox housing and the actuators;
Figure 44 is a cross-sectional view of the gearbox actuator;
Figure 45 shows the kinematic chain with four articulated joints of the selection actuator assembly; and
Figure 46 shows the essential components of the slide solution.

 FIG. 1 is a schematic representation of a vehicle which includes in the transmission train a drive motor 1, for example an internal combustion engine, a torque transmission system 2 and a gearbox 3. FIG. 2 also represents a differential 4, output shafts 5 and wheels 6 driven by the output shafts. Rotational speed sensors not shown which detect the rotational speeds of the wheels can be arranged on the wheels. The speed sensors can also functionally belong to other electronic units, for example an anti-lock system (ABS). At least one vehicle speed and / or a gearbox rotation speed can be determined by means of a control unit 7 from a wheel rotation speed.

 The drive unit 1 can also be configured as a hybrid drive, which includes for example an electric motor, a freewheel, and an internal combustion engine.

 The torque transmission system 2 is produced as a friction drive, but the torque drive system can just as easily be configured as a magnetic powder coupling, flap coupling or torque converter with converter bypass coupling or other coupling. The friction clutch can also be produced as an automatic adjustment clutch with wear correction.

 The automated gearbox operating device 3 comprises a control unit 7 and an actuator 8 which can be controlled by the control unit 7. Likewise, the control unit 7 can control an actuator 11 for automatically operating the torque transmission system 2. In Fig. 1 shows a control unit 7 and an actuator shown diagrammatically 8. The control unit 7 can be produced in the form of an integrated control unit which executes the control or regulation, for example of the torque transmission system and the gearbox. Motor electronics can also be integrated into the control unit. Likewise, the control of the torque transmission system and the gearbox, respectively of the actuators 7, 11 for maneuvering the torque transmission system and the gearbox, can be carried out by different control units.

 The present invention also refers to the prior application DE 19 504 847, the content of which expressly belongs to the content of the publication of this application.

 It is also possible that the control units of the torque transmission system1 of the gearbox and / or the engine control are arranged separately and communicate with each other via data lines and / or signals.

 The control units or the electronic units are also connected to signals with sensors which communicate the operating parameters of the current operating point to the control unit or the control units.

 It is also possible that the control unit receives all the necessary information via data lines or a data bus.

 The control unit 7 is equipped with a computer unit or, in other words, a computer unit in order to be able to receive, process, store, interrogate and transmit the signals and the incoming system quantities. The control unit also generates control quantities and / or signals intended to control the actuators, as well as to be transmitted to other electronic units.

 The torque transmission system 2 is mounted on a flywheel 2a or connected to it. The flywheel configuration may consist of a one-piece flywheel or a split flywheel comprising a primary mass and a secondary mass, and a torsional oscillation damping device which is arranged between the individual masses of the flywheel, it that is to say between the primary mass and the secondary mass. A starter ring gear 2b can also be arranged on the flywheel. The clutch comprises a clutch disc 2c with friction linings and a compression plate 2d as well as a clutch cover 2e and a spring 2f with discs.

The automatic adjustment clutch also further comprises means which allow displacement and wear correction, and the invention provides for the presence of a sensor, for example a force or path sensor, which detects a situation in which correction is necessary, for example for reasons of wear, and is also executed automatically upon detection.

 The torque transmission system is operated by means of a disengagement device, for example a disengagement stop 10. The control device controls the actuator 11 which performs the operation of the clutch. The disengagement device can be maneuvered by an electric motor, an electro-hydraulic device, for example by maneuver by pressure medium, for example by hydraulic means or another maneuvering mechanism. The disengagement device 9 with disengagement button 10 can be produced in the form of a central disengagement device which is arranged coaxially with the input shaft of the gearbox and which engages or disengages the clutch by means of loading, for example, of the clutch disc spring tongues. However, the disengagement device can also be configured in the form of a mechanical disengagement device, which operates, biases or handles a disengagement stop or a comparable element.

 The actuator 8 maneuvers in particular the gearbox 3 by means of its single element at least output or maneuver, or by means of several output or maneuver elements, to switch and / or select. The control of the switching and / or selection operation depends on the type of structure of the gearbox.

 In particular, gearboxes with a central axis of the gearshift lever or, in other words, with a central switching shaft in which a switching or selection process is carried out by an axial operation, must be taken into account. of the central switching shaft or by an operation of this shaft in the peripheral direction, or vice versa respectively.

An actuator maneuvers for example by means of a maneuvering element the axial maneuver of the central switching shaft and maneuvers by means of another maneuvering element the maneuver of this shaft in the peripheral direction. The switching movement can then be carried out in the peripheral direction and the selection maneuver in the axial direction, or vice versa.

 It is also necessary to take into account gearboxes with two shafts in which are respectively arranged a shaft intended for the switching of the gear reduction and a shaft intended for the selection of this reduction, the two shafts being maneuvered in direction device in order to execute a switching process or a selection process.

 Consideration must also be given to gearboxes with switch rods in which the switch rods are operated axially in order to switch a gear reduction by means of a switching process, a selection process being carried out by selection of the actuated switching rod.

 The switching shafts or rods represent switching elements internal to the gearbox, or the shafts maneuver these elements inside the gearbox during an operation. The actuator 8 directly or indirectly operates switching elements internal to the gearbox to engage gears or reduction ratios, to leave or to change them, for example a central shaft or switching shafts or switching or other switching elements.

 The control unit 7 is connected to the actuator 8 via the signal link 12 in such a way that control signals or sensor signals or operating status signals can be exchanged, transmitted or questioned. The device further includes the signal links 13 and 14 by means of which the control unit can be at least temporarily in signal link with other sensors or other electronic units. Such other electronic units can be, for example, engine electronics, anti-lock system electronics or anti-skid control electronics. Other sensors may be sensors which generally characterize or detect the operating state of the vehicle, for example sensors for the rotation speed of the engine or the wheels, a throttle valve position sensor, a position sensor. the accelerator pedal or other sensors. The signal link 15 represents a link to a data bus, for example a CAN bus, by which vehicle system data or other electronic units can be made available since the electronic units are generally networked by through computer units.

 An automated gearbox can be switched, or subjected to a gear change, in such a way that it is the driver of the vehicle who initiates such a process by sending a shift signal or switching to higher or lower speed, by example by means of a switch, button or other gearbox selection device 40. A signal for selecting the next gear to be engaged could also be sent. Correspondingly, a signal indicating the speed in which the gearbox should be switched can also be made available by means of an electronic gearshift lever.

 In another gearbox program, an automatic gearbox operation can be selected in such a way that the selection of the current gear is made according to the operating parameters and that eventually a switching process is started. automatically. However, an automated gearbox can also execute a gear change autonomously, at certain predetermined points, for example by means of characteristic values, characteristic curves or characteristic fields and on the basis of sensor signals, without the driver must cause a gear change.

 It is also possible to establish a neutral position N in which there is no drive link between the input of the gearbox and the output of the gearbox. It is also possible to select a garage position P in which a garage lock is produced. This garage position can also be automatically selected when, for example, the ignition key 51 is removed from the contact cell and the operating condition of the vehicle allows it. If, for example, the ignition key was removed at high speed, no garage lock-up could be performed automatically in this situation.

 The gearbox selection unit 40 can therefore be established at an area M, for manual speed selection by the driver, an area D, for automatic speed selection for operation in operation, an area P , for a garage lock, and / or an N zone for a neutral position.

A manual gear change can also be initiated for example by means of switches or a lever.

 The vehicle is preferably equipped with an electronic accelerator pedal 23 or electronic load lever, the accelerator pedal 23 controlling a sensor by means of which the engine electronics 20 controls or regulates for example the supply of fuel, the instant of ignition, the injection time or the position of the throttle valve via the engine signal line 21 1. A signal link is established between the electronic accelerator pedal 23 with sensor 24 and the engine electronics 20 via the signal line 25.

The engine electronics 20 is connected to signals with the control unit 7 via the signal line 22. In addition, a gearbox control electronics 30 can also be connected to signals with the units 7 and 20. A throttle valve control by electric motor is suitable for this purpose, the position of the throttle valve being controlled. by means of the engine electronics. In such systems, a direct mechanical connection to the accelerator pedal is no longer necessary or appropriate.

 The vehicle further comprises an engine starting device 50 which controls engine electronics and a controlled starter to start and / or start the engine, starting for example from an attempt to start the engine made by the driver, for example by operating the ignition key 51 in the ignition lock.

 Figure 2 shows a cross-sectional view of an actuator 5 according to the invention which is controlled by a control unit to maneuver a gearbox, for example to switch or select gear ratios. The actuator 100 operates a gearbox 3 which respectively has a shaft for each of the interventions: switching and / or selection of the gearbox reduction.

 The shaft 101 is operated for switching gears while the shaft 102 is controlled to select the gear reduction. To operate the switching shaft 101 or the selection shaft 102 in order to switch or select the gear reduction, the switching shaft or the selection shaft is pivoted or rotated by a predetermined angular magnitude, each by a drive unit and for example by a mechanism mounted downstream.

FIG. 2a shows a switching slide 190, with switching lanes 191 and selection lane 192, the selection process being a selection process between the switching lanes 191 and the switching process being an operation inside a switching corridor 191. The switching diagram or the switching slide 190 is shown in the case of a typical gearbox with five forward gears and one reverse gear, the position of the reverse gear can also be arranged in the area of the line 193 in lines. interrupted. In addition, all the switching slides for 4-speed, 5-speed or 6-speed gearboxes can be considered equivalent as switching slides, the individual positions of the speeds resulting from the structure of the gearbox
The actuator 100 of Figure 2 operates the switching shaft 101 and the selection shaft 102 for switching and / or selection. The actuator 100 comprises two drive units 103 and 104, which execute a switching process or an automated selection process by a command from the control unit 7.

 The drive units 103, 104 consist, according to an advantageous configuration, of electric motors, for example direct current motors, alternating current motors, traveling wave motors or the like.

 The drive unit 103, for example an electric motor, drives a motor shaft 105 which is housed in the area 106. The motor shaft 105 carries a worm screw 107 which meshes with a screw gear 108 unending. The worm gear 108 is rotatably housed in the area of the shaft 109. A gear 110 is connected endlessly without possible reciprocal rotation, which will be simply referred to by the terms of without rotation, to the gear 108 of the screw being for example formed integrally with it. The gear 110 can be a spur gear, a bevel gear or another gear. A lever 111 is connected without rotation to the shaft 101, being for example received by means of a toothing, the lever 111 comprising in one of its end zones lîla a toothing 112 which meshes with the toothing lOa of gear 110.

 The drive movement of the electric motor drives the shaft 105 so that the gear 110 which meshes with the teeth of the lever is driven by means of the worm and the worm gear, so that the lever 111 is rotated and that the axis 101 is thus operated for switching.

 The operation of the shaft 102 is carried out in a corresponding manner by means of the electric motor 104, the electric motor 104 driving the shaft 120 to which is connected without rotation an endless screw 121 which meshes with the screw gear 122 unending. A gear 123 is connected to the worm gear 122. A lever 124 is connected to the shaft 102, for example the selection shaft, for example by means of a toothing, and this lever comprises in the front region 124a a toothing 125 which meshes with the toothing of the gear 123. The rotation of the gear 123 rotates the lever 124 and thus operates the selection shaft 102.

 The axes of the shafts 130 and 131 of the motors are arranged in parallel in this embodiment, so that the orientations of the stators 132 and 123 of the electric motors 103 and 104 are arranged substantially in parallel. It is also possible to arrange the axis 130 and the axis 131 to form between them a predetermined angle, which is not zero. Preferably, the two motors can be arranged at an angle for example of 900 or in a range of 300 to 1500.

 The plane which passes through the axis 130 and the worm gear 108 can be the same plane as that of the axis 131 and the worm gear 122.

These planes can also be offset relative to one another, by being parallel, or be arranged one relative to the other at a previously definable angle.

 The gearbox selection or switching drive is respectively constituted by an electric motor and a two-stage mechanism in which the first stage of the mechanism is produced in the form of a worm mechanism and a second stage of the mechanism is mainly realized as a spur gear stage. The spur gear stage consists of a gear driven by the worm as well as a toothed sector produced in the form of a lever.

 According to another advantageous concept of the invention, at least part of the control electronics or of the power electronics can be received inside the actuator 100. According to another advantageous example of embodiment of the Invention, it may be appropriate to arrange the control electronics and the power electronics in a separate housing.

 The actuator 100 can be received advantageously on the gearbox 3, for example by being clamped or screwed there.

 The configuration of the gearbox 3 is that of a conventional gearbox, with traction force interruption. The configuration of the actuator 100 is that of an actuator designated by the English term add-on, that is to say an actuator by addition, which can be mounted on the gearbox to perform, in substitution for a manual operation mechanism, an automated operation of the gearbox.

 The actuator 100 comprises a housing 140 on which the electric motors 103 and 104 are fixed or to which they are connected, the motor shaft protruding through an opening in the housing 140 and the mechanisms, for example a screwless mechanism end or a spur gear mechanism or other mechanism being arranged inside the housing 140.

The shafts 101 and 102 further project through at least one opening in the housing. According to another concept of the invention, it may be appropriate for two output elements of the actuator, one for each shaft, to protrude into the mechanism for the operation of a switching shaft and a selection shaft, in order to operate switching elements internal to the gearbox for switching or selecting the gearbox, for example by means of a positive engagement link or a friction link.

 Figure 3 shows an actuator for operating, for example switching or gear reduction, of a gearbox.

 In this exemplary embodiment, the gearbox comprises a central switching shaft 205 which can be turned in the peripheral direction for switching and can be maneuvered in the axial direction for selection.

 The drive 201, for example an electric motor, comprises a motor shaft 206 which is for example housed in the zone of the housings 207a and 207b. The motor shaft 206 has a worm screw 208 which meshes with a worm gear 209. A gear 210 is connected without rotation to the worm gear 209 or is formed integrally with it. A lever 211 is connected without rotation to the central switching shaft 205, for example by means of a toothing or a positive engagement link, and the lever 211 has in the front zone 211a, a toothing 12 which meshes with the toothing 210a of the gear 210. As soon as the worm gear motor 201 drives the worm gear, the lever 211 is pivoted by means of the gear 210 and the toothing 212, and the central switching shaft is therefore operated in the peripheral direction.

 The drive motor 202, for example an electric motor, drives a motor shaft 220 which can be housed in the zone 221. A worm screw 222, which drives the worm gear or meshes with it, is connected to the motor shaft 220, and the worm gear is arranged relative to the axis 223, which is not visible in this representation. Another gear 224 is connected without rotation to the worm gear or is integrally formed with it. A fork 203 which can pivot relative to the axis 231 is arranged so as to maneuver the central switching shaft in the axial direction. A lever arm 232, which has in the region 232a a toothing which meshes with the toothing of the gear 224, is connected without rotation to the fork 230. Under the effect of the drive of the shaft 220 and of the worm, the worm gear rotates so that the gear 224 also rotates. In this way, the lever 232 rotates around the axis 231 so that the fork 230 which operates the central switching shaft by means of a positive engagement link performs an operation of the central switching shaft in the axial direction .

 Figure 4 shows a view of the actuator 200, where the drive units 201 and 202 and their stators 203 and 204 are shown. The electric motors are screwed or clamped on the housing 240, the motor shafts 206 and 220 protruding through at least one opening in the housing 240. The worm screw 222 drives the worm gear 223a, which is connected in positive engagement or without rotation to the gear 224. The gear 224 causes the pivoting lever 232 to rotate, after which the fork 230 rotates around the axis 231. The fork 230 enters the space zone of the central switching shaft between the substantially annular circular zones 241 and 242, a connection in positive engagement being guaranteed. Under the effect of the operation or rotation of the fork 230 about the axis 231, the central switching shaft 205 is maneuvered in the axial direction.

 Figure 5a shows the stator drive unit 203 and the motor shaft 206, in which the worm screw 208 meshes with the worm gear 209. The worm gear is arranged to rotate relative to the axis 260, and the gear 210 which drives the lever 211 is connected without rotation to the worm gear. The pin 261 is used to house the gear 210 and / or the worm gear 209 in the area of the housing 240, which is not shown in this exemplary embodiment.

 FIG. 5b represents a drive unit 201, for example an electric motor, with stator 203.

The motor shaft 206 comprises a worm screw 208 on which a gear 209 of the worm gear meshes. A substantially annular circular element 207 is connected to the worm gear 109 without rotation, this substantially annular circular element being composed substantially of the elements 270a and 270b.

The elements 270a and 270b are for example two disc-shaped elements which are spaced from one another and are connected to each other without rotation. Between the elements in the form of circular annular discs 270a and 270b is arranged a substantially annular circular element 271. The element 271 comprises windows 272 in which force accumulators are received 273. The force accumulators are received under prestress in housings elements 270a and 270b, the force accumulators passing through the windows 272 of element 271. In the event of relative rotation of elements 270a, 270b relative to element 271, the force accumulators are biased in the peripheral direction and there results in a torque transmission to the disc-shaped member 271 from the disc-shaped members 270a, 270b via the force accumulators. To this disc-shaped element 271 is connected without rotation the shaft 275, and the gear 210 is connected without rotation to the shaft 275 so that an elastic stage is interposed, in the direction of intervention, between the drive of the worm gear 209 and the gear 210.

The force accumulators 273 are received under prestress in the windows of the elements 270a, 270b and 271, so that a relative rotation of the element 271 with respect to the elements 270a, 270b takes place only when the force force of one of the elements in relation to the other element is greater than the prestress.

 When the force load exceeds the prestress, the force accumulator acts as an elastic member.

 FIG. 5c represents a fragmentary view of an actuator according to the invention in which the two sensors 278 and 279 capture or respectively detect the displacements of the gears 277 and 276.

The gears 276 and 277 are mounted on the elements arranged to rotate with respect to each other, for example parts 270b, 271 in the form of discs. The disc-shaped parts 270b and 271 have the teeth in the radially outer marginal zone. The sensors are configured in such a way that they detect without contact the teeth of the teeth which pass in front of the sensors arranged essentially in a stationary manner. The sensors detect them for example by induction or by means of a characteristic magnetic quantity, for example by a Hall effect sensor or in another non-contact manner, for example in an optical manner. The beam of an optical transmitter could periodically be interrupted by the teeth and pass freely, so that this would result in a pulsed beam and that a sensor could detect this pulsed beam. Any optical sensor which intervenes by means of rays, in particular electromagnetic rays, can be provided as an optical sensor.

 The two sensors 278 and 279 separately detect the position and / or the speed and / or the acceleration of the elements 270b, 271 and the central control unit can calculate using the signals from the sensors the relative rotation of the two parts 270b and 271 .

 Figures 6a and 6b show the circular annular elements 270a, 270b and 271, with housings substantially in the form of windows 272 and 274, and the force accumulators 273. The circular annular element 271 has in its radially outer zone 275 a toothing 276 which serves as an incremental transmitter to detect the speed of rotation or the position of the disc 271.

 The windows 272 and the housings 274, which may for example be pocket-shaped imprints, receive the force accumulators in a linear arrangement, and the discs 270a, 270b and 271 each receive four force accumulators which are respectively offset by 900 relative to each other. The force accumulators can also be pre-stressed curvilinear force accumulators which are substantially received in a circular arrangement in the openings. The configuration of the force accumulators 273 can also consist of a combination or nesting of several force accumulators, for example two force accumulators nested one inside the other. The configuration of the force accumulators 273 may consist of cylindrical compression springs or, for example, of other elastic elements, for example elastic elements of plastic.

 Figures 7 to 9 show in cross section another embodiment of an actuator 300 with two drive units for implementing a switching and / or selection process in order to automate a gearbox 301, without capacity switching under load.

 The housing 302 of the actuator 300 is connected to the casing 303 of the gearbox or is fixed thereto, for example using fixing means 304 such as screws. The actuator can for example be clamped as a solution by addition, in place of a switching dome for manual switching on a gearbox 301 which can also be provided for manual switching. A drive 399, 398, for example an electric motor, is available for each of the switching and selection movements and the operation. A third drive can also be provided to control the operation of the torque transmission system. Such an actuator can also be an actuator with an electric motor. It is also possible to provide an actuator which can be operated by pressure medium, for example hydraulic or pneumatic, or another actuator.

 On the gearbox 301 is flanged the actuator 300 provided with the drives, for example electric motors, for the switching and the selection of the gearbox reduction of the gearbox 301.

The drives 399, 398 configured as electric motors are not shown in the
Figure 7. They are however shown in Figures 8 and 9. The electric motors however include motor shafts or drive shafts 305 and 306 which are visible in cross section. To the motor shaft 305 is connected a worm 307 which meshes with a worm gear 308 and drives it. The disc-shaped, substantially annular circular elements 309a and 309b are connected substantially without rotation to the worm gear 308. The elements 309a and 309b are spaced apart from each other in the axial direction and are connected to each other without rotation. The fixed connection without rotation of the elements 309a and 309b can for example be effected by means of bolts in the form of spacers, or of rivets. Between the elements 309a and 309b is received a substantially annular circular element 310. The elements 309a, 309b and 310 have housings 312 or indentations in the form of windows which serve to house the force accumulators 311. The force accumulators 311 are preferably arranged under prestressing in the accommodation. The force accumulators 311 are used for the transmission of force from the elements 309a, 309b to the circular annular element 310, the force being transmitted and communicated from the circular element 310 to the shaft 313. The shaft 313 is housed rotatable by means of element 314 relative to element 309a. The shaft 313 is further housed in the housing 302 using at least the single housing 316. The preload of the force accumulators serves to define the force limit when the switching movement is actuated. When the prestressing force of the force accumulators 311 is exceeded, for example when a stop is reached, the force accumulators can only be used once before continuing to operate the gearbox.

 The shaft 313 drives the gear 315, the drive movement of the actuator drive is transmitted from the gear 315 via the gear 317 to the gear 318 and from there to the shaft switching center 320.

The gear 317 is housed by means of the pin 321 and the housing 322, for example a sliding housing or a rolling housing in the area of the housing.

 The gear 318 is received by means of an internal toothing on the external toothing of the central switching shaft and is connected to it without rotation.

 The switching movement for switching the gearbox is transmitted to the central switching shaft 320 as a rotary movement from the drive. The transformation of the movement, from the electric motor to the central switching shaft 320, is carried out by means of a worm mechanism whose worm screw 307 is located on the extended shaft 305 of the motor. The worm gear 308 is housed on a shaft 313, in such a way that these two elements can execute a relative rotation with respect to each other. The drive torque is transmitted from the worm gear 308 to the shaft 313 via a driving disc 309a which is located laterally on the worm gear 308 and force accumulators. prestressed 311, for example springs. On the shaft 313 is moreover fixed without rotation a toothing 315 which finally drives the central switching shaft 320 by means of an intermediate gear 317 and another gear 318.

The intermediate gear 317 is added in the present embodiment for reasons of optimization of the structure space. It is also possible to optionally omit this intermediate gear. The background corresponding to this subject relates to the pivot angle, which may possibly be relatively large, which the central switching shaft can rotate. The distance between axes of the gears and therefore the space required are reduced by the effect of the intermediate gear 317. Likewise, the gear 318 can be produced in the form of a toothed sector, in which a toothing is only arranged over a usable angular area.

 The selection of the switching scheme corridor or the switching slide is carried out by moving back and forth, around the central switching axis 320, of a socket 330 which can be produced by means of lateral fingers 340 and 341 a link in positive engagement with the transmission members or switching elements 342 and 343 arranged downstream, internal to the gearbox. The rotational movement of the shaft 306 must be transmitted to the sleeve 330, which guarantees a profile 331 of splined shaft in the present embodiment, but a linear guide for taking over the torque could also be used as a variant. .

 The displacement movement of the sleeve 330 is driven by a drive 398, for example an electric motor, by means of an endless screw 350 which is located on the extended motor shaft 306. The rotational movement is then transmitted to a worm gear 351 which is provided, without rotation, with teeth 352 by means of which a toothed sector 353 mounted downstream is driven. To the toothed sector 353 are also fixed here without rotation two levers 354a and 354b at the two ends of which are rollers 355a, 355b which penetrate into a notch 360 on the outside of the sleeve 330. In this way, the movement of movement of the levers 354a, 354b is converted into a movement of movement of the sleeve 330. According to another advantageous example of embodiment, it may be appropriate for only one lever to penetrate one of the sides in the sleeve 330.

 The rollers 355a, 355b are housed in the housings of the levers by means of housings 371, for example sliding housings such as bushings, or rotary housings.

 Electric motors 399, 398 can be fitted with incremental sensors. A current measurement of the motor current can also be carried out. The signals of the current measurement of the motor current are used as a characteristic quantity of the operating state, the control being able to generate control signals as a function for example of this motor current.

 The final power stage of the control electronics can be integrated in the gearbox actuator case described above, but it is also conceivable that the electric power is transmitted by a control device. Signals and electrical energy come from outside to the gearbox actuator 300 via a plug not shown.

 The mechanism integrated into the actuator 300 can be mounted either directly or by means of a carrier element 370 inserted in the actuator housing 302. The carrier element may for example be made of plastic.

 The arrangement of the drives is configured in such a way that the motor shafts are oriented parallel to each other. It may also be appropriate for the axes to form an angle.

 Figures 10 to 12 show in cross section another embodiment of an actuator 400 with two drive units 401 and 402 for the implementation of a switching and / or selection process for the automation of a switch box without the possibility of load switching.

 The housing 402 of the actuator 400 is flanged on the gearbox casing or is fixed thereto, for example screwed. The actuator can for example be clamped on a gearbox as an addition solution. Two drives 401 and 402, for example electric motors, are respectively available, one for the switching movement and the other for the selection movement, and they operate. A third drive, which controls the torque transmission system, can also be provided. Such an actuator can be an actuator with an electric motor. It is also possible to provide an actuator which can be operated by pressure medium, for example hydraulic or pneumatic, or another actuator.

 Electric motors have motor shafts or drive shafts 406 and 406 which are shown in cross section. To the motor shaft 405 is connected a worm 407 which meshes with a worm gear 408 and drives it. The disc-shaped, substantially annular circular elements 409a and 409b are connected substantially without rotation to the worm gear 408. The elements 409a and 409b are spaced from each other in the axial direction and are connected to each other without rotation. The fixed connection without rotation of the elements 409a and 409b can for example be effected by means of bolts in the form of spacers, or of rivets.

 Between the elements 409a and 409b is received a substantially circular annular element 410. The elements 409a, 409b and 410 have housings 312 or indentations in the form of windows which serve to house the force accumulators 411. The force accumulators 411 are preferably arranged under prestressing in the accommodation. The force accumulators 411 serve for the transmission of force, of the driving force or of the driving power, from the elements 409a, 409b to the circular annular element 410, the force being transmitted and communicated from the circular element 410 to the shaft 413. The shaft 413 is housed in rotation by means of the element 414 relative to the element 409a.

The shaft 413 is further housed in the housing 402 using at least the single housing 416. The preload of the force accumulators serves to define the force limit when the switching movement is actuated. When the pretensioning force of the force accumulators 411 is exceeded, for example when a stop is reached, the force accumulators can only be used once before continuing to operate the gearbox.

 The shaft 413 drives the gear 415, the drive movement of the actuator drive is transmitted from the gear 415 to the gear 418 and from there to the central switching shaft 420.

In the embodiment of Figures 10 and 12, the switching movement is transmitted in the form of rotational movement of the central switching shaft 420 via a mechanism which is comparable to the mechanism of Figures 7 and 9 , and which is placed between the electric motor 401 and the switching shaft 420. In this embodiment, there is no intermediate gear 317 as at
Figure 8. In addition, another advantageous transmission of the torque is produced from the toothed sector 418 on the central switching shaft 420.

 Two rollers 422 and 423 are held on the central switching shaft 420 by means of a bolt 421 and are arranged therein for rotation. The rollers 422 and 423 can roll on rolling tracks 425a, 425b, inside the toothed sector 418. The rolling tracks are oriented essentially in parallel with the axis of the central switching shaft.

 A stroke displacement, necessary for the selection, of the central switching shaft 420 relative to the mechanism and actuator housing is thus possible, while simultaneously ensuring in rotation the central switching shaft 420 relative to the toothed sector 418.

 The switching movement intended to switch the gearbox is transmitted to the central switching shaft 420 as a rotation movement of the motor shaft starting from the drive 401. The transformation of the movement from the motor shaft from the electric motor to the central switching shaft 420, is effected by means of a worm mechanism whose worm 407 is located on the extended shaft 405 of the motor. The worm gear 408 is housed on a shaft 413, in such a way that these two elements can rotate relative to each other. The drive torque is transmitted from the worm gear 408 to the shaft 413 via a driving disc 409a which is located laterally on the worm gear 408 and force accumulators. prestressed 411, for example springs. On the shaft 413 is moreover fixed without rotation a toothing 415 which drives the central switching shaft 420 by means of the toothed sector 418.

 The command of the selection movement is transmitted from the electric motor 402 in the first place to a gear 451 by means of a worm screw 450 which is located on the extended motor shaft 406. In the hub of the worm gear 451 is a bush 452 which rotates with the worm gear 451 and has two helical notches 453a, 453b in which two other rollers 455a, 455b are arranged arranged on the 'central switching shaft 420. If the central switching shaft 420 is then held stationary by a stop of the electric motor 401 and if the electric motor 402 turns simultaneously, a stroke displacement, which is the selection displacement, of the central switching shaft is obtained 420 due to the notches 453a, 453b in a helix.

 The rollers 455a, 455b are connected by means of the journal 456 to the central switching shaft and are housed therein in rotation. Trunnion 456 is received in a bore in the central switching shaft.

 The element 451 is housed by means of the housing 460 relative to the housing, and by means of the housings 461 and 462 relative to the element 418.

 As with the spring 411 arranged in the force path for switching, an elastic member can also be arranged inside the drive chain which goes from the drive 402 to the central switching shaft in the direction of selection movement.

 The electric motors 401 and / or 402 can be fitted with incremental sensors. A current measurement of the motor current can also be performed. The signals of the current measurement of the motor current are used as a characteristic quantity of the operating state and the control can generate control signals as a function, for example, of this motor current.

 The final power stage of the control electronics can be integrated into the gearbox actuator housing described above, but it is also conceivable that the electric power is transmitted from a control device. . Signals and electrical energy come from the outside via a plug not shown to the actuator 400 th gearbox.

 The electric motors flanged or screwed on the actuator 400 can be configured in the form of modules, for example of worm and worm gear, as well as, possibly, of housings for the worm drive, which are connected to the actuator housing and are integrated into the actuator.

 The arrangement of the drives is configured in such a way that the motor shafts are oriented parallel to each other. It may also be appropriate for the axes to form an angle.

The embodiment of Figure 13 corresponds substantially to the embodiment of
Figures 10 and 12, but it is another advantageous control of the selection movement which is configured there.

 Instead of the socket 452 of Figure 12, with helical notches 453a, 453b, a helical toothing 501, for example a spindle, is formed on the central switching shaft 520, and the worm gear 550 has in the radially inner zone a corresponding counter-toothing 502 so that the worm gear constitutes the nut for the spindle.

 The torque transmission for switching takes place towards the central switching shaft 520 from the toothed sector 560 by means of a linear guide 561 for supporting the torque of the torque. The linear guide 561 for torque support has in the axial direction movement tracks 562a, 562b, on the hub side and on the shaft side, for rotating bodies 563, which may for example be of spherical configuration. The rotating bodies transmit the torque, but are axially movable in the movement tracks, so that the central switching shaft can be moved axially to execute the selection movement and in this way the rolling bodies roll on the shaft and on the hub.

 In order to prevent the rotating bodies from sliding down when the linear torque support guide is mounted vertically in the powerless state of the central switching shaft, the rolling bodies which are guided in a cage are centered with respect to the hub by means of prestressed force accumulators, for example springs 564.

The hub side of the linear torque support guide is executed in such a way that the rotating bodies can, in the centered position, run the full stroke in both directions.

The full stroke is possible in both directions at each position of the central switching shaft.

When the switching operation is carried out in the absence of force in the rest positions of the speeds of the gearbox1 the rotating bodies are movable in the axial direction under the effect of the play in the rotary guide. The springs center the cage of the rotating bodies in the middle of the hub, due to their prestressing force.

 Figure 14 is a table which represents possible variants of arrangement for an automatic operation device, on the one hand, of a gearbox for switching and / or selecting simply designated by the word box on the table and, on the other hand, a torque transmission system, for example a clutch, for clutching. There are basically in the table of Figure 14 devices with three actuators, that is to say one actuator each operation: the clutch (E), the switching (C) and the selection (S), devices with two actuators, that is to say in which the clutch and the switching (E + C) are combined and the selection (S) remains distinct, with two actuators, that is to say in which the clutch and the selection (E + S) are combined and the switching (C) remains distinct, and with a single actuator to combine the three coupling and switching and selection operations (E + C + S).

 The control device can also be combined with an actuator of the device, or be arranged in a separate housing inside the vehicle. An arrangement of the actuators or of a separate control device can be carried out directly on the vehicle body and / or on the gearbox.

The present invention also refers to application DE 196 27 980, the content of which expressly belongs to the content of the publication of this application. The present invention also refers to application DE 195 33 640, the content of which expressly belongs to the content of the publication of this application.
We will now explain with the aid of FIG. 5c the structure which corresponds to the preceding figures and the detection of a relative rotation and / or the respective rotations of two disc-shaped elements or parts. The substantially disc-shaped elements are arranged to rotate with respect to each other, the relative rotation of the two elements 270b, 271 taking place in opposition to the effect of at least one force accumulator. At least the single force accumulator can for example be configured as a cylindrical compression spring, as a spiral spring, as a coiled spring or as an elastic plastic member. At least the single force accumulator can further be configured or be arranged as a non-prestressed or prestressed force accumulator. An arrangement of pre-stressed and non-pre-stressed force accumulators can also be advantageous, for example for achieving a force characteristic on several levels. The detection of the positions and / or speeds and / or relative accelerations of the individual disc-shaped elements is carried out by means of two sensors 278, 279, one for each disc-shaped element, the control unit determining the relative rotation of the two elements with respect to each other and therefore also the compression of the single force accumulator at least arranged in the force flow which goes from one disc to another. In this way, the existing drive torque can be calculated because the stress accumulator torque is at least equal to the drive torque or is proportional to the latter or at least represents the latter.

 According to another exemplary embodiment, it is possible to advantageously use a single sensor which detects a relative rotation of the two elements 270b and 271 of FIG. 5c, the two elements performing, in addition to a relative rotation, a rotation at common rotational speed. This unique sensor detects the relative rotation of the two rotating elements based on magnetic properties or other properties which can preferably be detected without contact.

 According to an advantageous configuration of the invention shown in Figures 15a and 15b, the two elements 601 and 602 substantially in the form of discs each have at its marginal zone a magnetized or magnetizable marginal zone. The disc 601 is arranged on the drive side and the disc 602 is arranged on the output side, at least one accumulator of compressible force opposing the effect of a force being arranged between the disc 601 and the disc 602 When a torque is transmitted from one disc to another, at least the single force accumulator is compressed or stressed by a force.

 The marginal zones of the discs 601 and 602 are magnetized in such a way that the north and south poles are arranged alternately, repeating on their periphery. It may also be advantageous to arrange or mount annular magnets in the marginal areas of the disc-shaped elements. These annular magnets can consist of a magnetic material, for example a plastomagnetic material.

As magnetic materials, an alloy of ferrites or cobalt-rare earth alloys, such as cobalt-samarium, can be used. For plastomagnetic materials, the magnetic materials are for example incorporated in a plastic matrix. Plastomagnetic materials can also consist of a plastic material in which magnetic ions are received or arranged inside the molecular chains.

 The annular magnets preferably comprise numerous magnetic poles arranged in a distributed manner on the periphery, that is to say north magnetic poles (N) and south magnetic poles (S).

The number of magnetic poles distributed over the periphery can be determined here by the desired resolution. Preferably, at least 4 magnetic poles are distributed on the periphery. It is appropriate that substantially at least eight poles, possibly 16 or 32 poles are arranged or distributed on the periphery.

The distribution of the poles along the periphery is here preferably uniform.

 The two disc-shaped elements 601 and 602 are arranged, in the state of absence of force, in such a way that the respective magnetized zones 603a, 603b, which have a north pole (N) and the respective magnetic zones. 604a, 604b which have a south pole (S) are underlying each other. Thanks to this arrangement, the magnetic field is established substantially in such a way that only lines 606 of magnetic field which lie in the plane of the discs 601, 602, are formed.

 A sensor 605 sensitive to the magnetic field, for example a Hall sensor or a unipolar Hall sensor, is arranged facing the radially outer edge of the discs 601, 602 and is oriented in such a way that it responds only to a magnetic field with field lines 607 traced perpendicular to the plane of the discs and detects this magnetic field by means of a Hall voltage.

 When the north and south poles of the same magnetization of the two discs are substantially arranged directly one above the other, the lines of the field lines of the magnetic field of the magnets or magnetic poles is substantially in the plane of the discs and the sensor 605 does not detect substantially any magnetic field with field lines in a perpendicular direction. When the two discs 601 and 602 are turned relative to each other because a torque is transmitted from one of the discs 601 to the other disc 602 in opposition to the effect of the force of the accumulators of force arranged between the discs, the relative positions of the magnetic zones or poles with the same magnetization shift and this results in a magnetic field with field lines perpendicular to the plane of the discs. The sensor 605 detects this perpendicular component of the magnetic field. Depending on the fraction or the magnitude of the perpendicular component of the magnetic field, the relative rotation of the two discs 601 and 602 relative to each other, and therefore the transmitted torque, can be determined on the basis of the magnitude of the sensor signal.

 When the relative rotation increases and that magnetic poles of the same magnetization and the same direction come to be superimposed again, the vertical component of the magnetic field decreases again and possibly disappears. The control unit determines a rotation signal from the actuator or the discs and takes it into account in determining the relative rotation. As the relative rotation increases, the elastic deformation of the force accumulator located between the discs 601, 602 increases, and the force acting between the components also increases. The actuator, for example the electric drive motor, is more stressed and the speed of rotation therefore decreases.

According to the evolution of the speed of rotation of the actuator, the control unit can determine whether the relative rotation has increased or decreased.

 It is also possible to achieve a non-uniform distribution of the poles on the periphery of the discs in such a way that poles of the same magnetization but of different dimensions come to be superimposed after a rotation. In this situation, the sensor signal does not become zero since a magnetic field with vertical lines of field is present in a substantially constant manner. The vertical component of the magnetic field is therefore amplitude modulated, the absolute value of the sensor signal becoming zero only in the absence of any relative rotation between the discs.

 The Hall sensor 605 can be configured as an analog or digitally unipolar Hall sensor. In the case of a double unipolar sensor, a desired characteristic of sensor of the output signals can be achieved by applying an exclusive-OR, or XOR relationship to the two signals.

 Figure 16a is a graph 700 intended to explain or represent the operating mode or the use of a unipolar Hall sensor 605.

The intensity 701 of the magnetic field existing at the location of the sensor is represented as a function of the path s. A sensor signal 702 as well as threshold values 703 and 704 of the signal are also shown. When the intensity 701 of the magnetic field is less than the threshold value 704, the signal sent by the sensor 605 is equal to the value 705. When the intensity 701 of the magnetic field reaches the threshold value 704, the sensor signal is modified to take the value 706. This value 706 remains maintained until the intensity 701 of the magnetic field drops below the value 703.

At this path s, the sensor signal is again set to the value 705.

Figure 16b shows the plot of the density 711 of magnetic flux as a function of the path s. The path s is the magnitude of the displacement of the two elements 601 and 602. The density 711 of magnetic flux varies in a substantially analog and linear manner. The sensor signal 712 from an analog sensor 605 is shown in the lower part of Figure 16b as a function of the flux density, the flux density being proportional to the path s. The sensor signal 712 is substantially linear and varies substantially continuously as a function of the path variation in the upper part of the
Figure 16b.

 Figure 16c is a graph 720 intended to explain or represent the operating mode or the use of a double unipolar Hall sensor, as it can be installed for example at 605. The intensity 721 of the existing magnetic field at the location of the sensor is represented as a function of the path s. The path s is essentially the magnitude of the displacement of the two elements 601 and 602.

In addition, signals 722 and 723 from the sensors and threshold values 724, 725, 726 and 727 are shown. When the intensity 721 of the magnetic field is less than the threshold value 725, the signal 722 sent by the sensor is equal to a maximum value. When the intensity 721 of the magnetic field reaches the threshold value 725, the sensor signal is modified to reach a minimum value. This value remains maintained until the intensity 721 of the magnetic field drops below the value 724. At this path s, the sensor signal is restored to the maximum value.

 When the intensity 721 of the magnetic field is greater than the threshold value 727, the signal 723 sent by the sensor is equal to a maximum value.

When the magnetic field intensity 721 reaches the threshold value 727, the sensor signal is modified to take a minimum value. This value remains maintained until the intensity 721 of the magnetic field descends from the new 754 magnetized in N or S covers the N or S poles of the disc 751. When viewed from the outside, only the S and N poles of the two discs can be recognized as magnetic poles with unitary effect.

 The sensor 755 is arranged at the marginal zones of the discs facing them. The sensor is also arranged in such a way that the sensor does not send any signal in the uncovered, uncharged state, since it is arranged between the unitary magnetization facing outwards, and possibly an additional magnet 756, so that the magnetic field is oriented so as to be relatively weak at the location of the sensor. The magnet 756 is provided to optionally reinforce the intensity existing at the location of the sensor.

 When the protrusions 754 cover, as by means of flaps, the N poles, the sensor 755 sends no signal. After a relative rotation of the two disks 750 and 751, the N poles are at least partially uncovered with respect to the S poles, and field lines are established which cross the location of the sensor, and the sensor sends a sensor signal which does not disappear and which represents a relative rotation of the discs.

 It is the same for the embodiment shown in Figures 17b to 17d. The discs 770 and 771 can rotate relative to each other in opposition to the effect of the force of the force accumulators 780. In Figures 17b to 17d, the first disc 770 has protrusions 774 projecting in the radial direction , which are overhanging above the other disc 771, at least in the radially outer zone.

The marginal zones 772 and 773 of the two discs are made of magnetizable material, for example made of ferromagnetic material. The magnetizations of the marginal zones 772 and 773 are such that zones which comprise a magnetic north pole (N) or a magnetic south pole (S) are repeated on the periphery of the discs. The protrusions 774 are here magnetized either
N, that is S. In an unloaded position of the two discs, the protrusions 774 magnetized in N or S cover the N or S poles of the disc 771. When viewed from the outside, only the S and N poles of the two discs can be recognized as magnetic poles with unitary effect.

 The sensor 775 is arranged above or below the marginal areas of the discs 770, 771. The sensor is further arranged in such a way that the sensor sends no signal in the covered, unloaded state, because it is arranged between the unitary magnetization facing outwards, and possibly an additional magnet 776. The magnet 776 is provided to optionally reinforce the intensity existing at the location of the sensor.

 When the protrusions 774 magnetized as S poles cover, as by means of flaps, the N poles, the sensor 775 sends no signal. After a relative rotation of the two discs 770 and 771, the N poles are at least partially uncovered with respect to the S poles, and field lines are established which cross the location of the sensor, and the sensor sends a sensor signal which does not disappear and which represents a relative rotation of the discs.

 In Figures 18a to 18c is shown another alternative embodiment of the arrangement of a sensor 820, 821 for detecting a relative rotation of two rotating elements according to the invention. The disc-shaped components 800 and 801 are coupled together by means of force accumulators and are subjected to a relative rotation of the first disc 800 with respect to the other disc 801 when a force biases the first disc 800. The force accumulators 805 are received in window-shaped cutouts in discs 800 and 801, so that the force accumulators are supported by their end zones or at least by an end zone on the zones of radial ends or at least on an end zone 812 of the window-shaped cutouts.

The force accumulators can be received under prestressing in the windows 810, 811, so that a relative rotation of the two windows only occurs when the prestressing force is exceeded.

 In the marginal zones of the two discs 800, 801, teeth 802, 803 are arranged, and a sensor 820, 821 which acts as a differential sensor picks up and detects the teeth of the discs during a rotation of the discs. The marginal zones can be made of a magnetizable material, for example ferromagnetic material. Under the effect of the magnetization of the teeth and the magnet arranged behind the sensor elements 820, 821, the respective sensor elements detect only the magnetization of the respective disc and thus detect the speed of rotation, the position and / or disk acceleration.

 In Figure 19a is shown the signal trace for the two signals 850, 851, of the first sensor element 820 and the other sensor element 821. In the absence of any relative rotation of the two discs, the signals 850 and 851 are substantially equal. During a relative rotation of the two discs, the two signals 850 and 851 are different, as shown in FIG. 19b. The curve 860 corresponds to a difference between the signals 850 and 851, so that the relative offset of the disks can be detected for example from the pulse width 852. When the signal 860 is for the first time greater than the upper threshold 870, the signal 880 is established at a value, for example a minimum value, until the signal value 860 becomes less than the second threshold value 871, and the signal 861 is then established at a value, for example a maximum value. Rotation can thus be detected even in the case of a blocked output 801.

 The force of the maneuver can be detected directly or indirectly, by means of the sensors described, inside the force path which goes from a drive to a maneuvering element. The force may be a switching force during an automated operation of a switching process, for example during a switching process of a gearbox. The force can be a selection force during an automated operation of a selection process, for example during a gear change of a gearbox. The force can also be an operating force of a torque transmission system, for example during an automated operation of a clutch.

 The control unit can execute, by means of this force signal or by means of a signal which represents this force, a control or regulation process which makes it possible, for example, to prevent the previously definable maximum force from being exceeded during a maneuver.

 FIG. 20 shows in an exemplary embodiment an automated device for maneuvering a gearbox of the vehicle, the gearbox of the vehicle itself not being shown or only being shown partially. The device comprises a first drive motor 1001, for example an electric motor, and a second drive motor 1002, for example an electric motor. The motor 1001 maneuvers the gearbox switching process and the motor 1002 maneuvers the gearbox selection process. The two electric motors essentially comprise pole pots 1001a and 1001b with a configuration which can either be substantially cylindrical or possibly deviate from the latter. The polar pots can also have a shape which deviates from the cylindrical shape, for example by flats. The motors each have a drive shaft 1003 and 1004, and these are each equipped with a worm or are connected to such a screw in order to maneuver by means of a worm mechanism the movement of rotation or travel of a switching finger of a central switching shaft of the gearbox. The worm 1005 is in drive relationship with a worm gear 1006. The switching motor 1001 transmits the rotational movement of its output shaft 1003, passing through the screw 1005 and the worm gear 1006 endless, then by means of two parts 1007a and 1007b of discs arranged substantially in parallel and of accumulators of force interposed, to the flange 1008 which is connected on the output side to a gear 1009 or is made of a standing alone with this one.

The gear 1009 meshes with another gear 1010 which is housed in the housing by means of the pin 1001 and which meshes itself with the toothed sector 1012. The rotational movement of the output shaft of the motor 1003 transmits a torque to the toothed sector 1012, passing through the worm mechanism and the force accumulator arranged between the disc-shaped elements 1007a and 1007b and the flange. The two parts 1007a and 1007b in the form of discs are connected without rotation, rods or bolts of disc 1007a preferably penetrating into recesses in disc 1007b. However, the two disc-shaped elements can also be connected to each other by riveted connections.

 The worm gear 1006, the disc-shaped components 1007a and 1007b as well as the flange 1008 are housed in rotation on the half-shaft 1013. The half-shaft 1013 is housed while being supported or mounted in rotation, on its first side in the housing of the switching motor 1020, and on its other side on the actuator housing 1021. The worm gear 1006 is connected to the drive side of the disc-shaped elements 1007a and 1007b1 for example by means of fluted or involute teeth. For this purpose, the worm gear comprises an axial appendage 1006a which carries the toothing. The external toothing of the zone 1006a meshes with an internal toothing of the element 1007a. The non-rotating connection of elements 1007a and 1007b causes a force transmission on the two disc-shaped elements. The flange 1008 is arranged axially between the two elements 1007a and 1007b and each force accumulator 1022 is received in windows of the flange 1008 and is supported by indentations or receiving zones in the zone of elements 1007a, 1007b in the form of discs. In the event of relative rotation between the elements 1007a and 1007b and the flange 1008, a force transmission or a torque transmission is effected on the flange from the two disc-shaped elements via each force accumulator, the flange rotating on the output side a switching shaft or a switching finger. Preferably, at least two force accumulators are arranged between the disc-shaped elements and the flange, transmitting the torque and possibly also being prestressed.

 The housing of the half-shaft 1013 in a housing can be carried out by tight adjustment.

* The worm gear 1006 can preferably be made of thermoplastic material.

The force accumulator, for example the elastic member 1022, can be made of a material with a low coefficient of thermal expansion, for example of metal, rubber or plastic. This preferably results in a slight assembly play, in particular when a toothed shaft is formed on the worm gear and a toothed hub is formed on the element 1006a on the drive side of the elastic organ. This is achieved in particular when the assembly temperature is lower than the temperature observed in the main operating range. The disc-shaped components 1007a, 1007b and the flange 1008 can also be made of metal or plastic.

 According to another exemplary embodiment, it is advantageous for the spline toothing between the entry side of the elastic member, that is to say of the element 1007a, and the gear 1009 to be configured in a so that there is a slight assembly play. This is achieved, for example, by the fact that the toothed shaft 1009 is made of a material with a greater coefficient of thermal expansion and that the toothed hub consists of an element with a smaller coefficient of thermal expansion. The rotational movement is transmitted from the gear 1009 to the gear 1012 by means of a toothing with spur gears, an intermediate gear can also be arranged to transmit the torque in an exemplary embodiment. The intermediate gear is housed in the housing by means of the axis 1011. The element 1012, for example a toothed sector, is for example connected via a toothing, for example an internal toothing 1012a, to a external toothing 1025 of the central switching shaft. During a rotation of the toothed sector 1012, the central switching shaft 1026 is rotated so that the switching finger 1027 changes its angular position. The pair of teeth 1012a, 1025 is produced in such a way that the central switching shaft can be displaced by sliding in the axial direction, and that the engagement of the two teeth is however carried out in order to maintain the angular position of the finger unchanged. switch 1027, despite an axial displacement of the central switch shaft 1026 and the switch finger 1027.

 The toothed sector of the switch 1012 is received and housed by means of a torque centering drive, for example a spline toothing, on the central switching shaft which is itself housed on the guide pin 1028 fixed on the housing. . The toothed sector of the switch 1012 is held in the actuator housing 1021 in the axial direction of the guide axis 1028 fixed on the housing, by means of a counter-support 1029 so that the central switching shaft 1026 can execute a movement of rotation and stroke, but that the toothed sector 1012 can only carry out a movement of rotation. In this way, the elements with internal teeth and external teeth, that is to say 1012a and 1025, slide relative to each other, in the case where the central switching shaft 1026 performs an axial displacement in the direction of the guide pin 1028 fixed on the housing.

 The selection motor 1002 transmits to the worm gear 1031 the rotational movement of the output shaft 1004 and of the worm screw 1080 which is arranged. Another gear 1032, which meshes itself with the toothed sector 1033 is fixed without rotation to the worm gear 1031. The toothed sector 1033 is housed in rotation in the region of the pin 1034, the finger 1031 being connected without rotation to the toothed sector 1033. This connection without rotation is carried out for example by means of screws, rivets, or a connection d '' in one piece or in positive engagement. The must 1031 enters the opening 1030 of the selection fork and the opening of the selection fork is connected in positive engagement or by force effect to the central switching shaft 1026. The rotation movement of the screw without end rotates the member 1031 about the axis 1034 so that the central switching shaft 1026 is lowered or raised. The worm gear and the gear 1032 are rotatably housed on the half-shaft 1035, which is supported on one of its sides in the gearbox housing and on the other side in the gearbox actuator.

The gear 1032 meshes with a toothed sector 1033.

On the latter is fixed a selection finger 1031 which is formed integrally with the toothed sector or which is connected to it and which enters a selection fork opening fixed on the central switching shaft or made of a in one piece with it, so that a rotary movement of the selection finger 1031 causes the central switching shaft 1026 to slide along its guide axis 1028. The opening 1030 of the selection fork is made in a in such a way that the rotational movement can be carried out in the stroke and rotation zone of the central switching shaft which is necessary for switching the gearbox, regardless of the position of the selector finger. The shims or teeth which are formed on the central switching shaft in the axial direction of the guide axis and which penetrate into corresponding notches in the toothed sector 1012 allow the stroke displacement to be effected independently of the position of the sector toothed in the stroke and rotation area of the central switching shaft which is necessary for switching the gearbox.

 The opening 1030 of the selection fork is made in such a way that the finger 1031 is received by an upper zone, for example a plate-shaped zone, and by a lower zone 1030b, for example a zone in the form of plate, the two elements 1030a and 1030b being formed integrally with one another or being interconnected. The plate-shaped areas are shaped on a tubular part, which is connected to the switching shaft. The extension of the zones 1030a and 1030b of the upper and lower limit surfaces of the opening of the selection fork is established in such a way that the finger 1031 is connected in positive engagement to the opening, despite a rotation of the central switching shaft.

 The actuator housing is configured in such a way that it advantageously includes appendages so that the central switching shaft can be moved, in its rotational movement or in its running movement, only by one in such a way that the rotational and stroke movements necessary for switching the gearbox are permitted. Rotational and stroke movements which deviate from these movements can be limited by the stops. This achieves, for the gearbox operating device, a compact embodiment which saves structural space, so that the limitation of the displacement zone which actually appears avoids having to create additional space. for degrees of freedom of movement, and areas of space, all useless.

 The actuator housing is preferably fixed to the gearbox housing using screws and centering pins. However, a different attachment of the actuator housing can also be provided. The tightening configuration can be such that each screw is inserted into a through hole in the actuator housing and the actuator housing is tightened on the gearbox housing. However, the configuration of the screwing can also be such that the screw penetrates through a through hole of the actuator housing into a through hole of the switching or selection motor and the housing of the switching or selection motor is screwed or tightened in common with the actuator housing on the gearbox housing.

 It is advantageous that the axes of the electric motors 1001 and 1002 are arranged parallel to each other and that the axis of the worm gear 1006 is oriented parallel to the axis of the central switching shaft 1026. In this way , the axes of the electric motors are perpendicular to the last two axes of the worm gear and the central switching shaft. It is also advantageous for the axes of the worm gear 1031 and of the toothed sector 1033 to be perpendicular to the axes of the electric motors and to the central switching shaft. This achieves an arrangement which saves structural space.

 Figures 23 to 26 show another embodiment of a device, according to the invention, for automated operation of a gearbox. The device 1100 includes an electric motor for operating the switching movement as well as a motor 1102 for operating the selection movement. On the output side 1103, the electric motor has a worm which meshes with a worm gear 1104. Two spaced discs 1105 and 1106 are connected to the worm gear, between which a flange 1107 is arranged.

Between the flange 1107 and the two discs 1105 and 1106 are arranged accumulators of force, for example springs or elastic elements, in such a way that the accumulators of force transmit, during a relative rotation, a transmission of force between the elements 1105, 1106 in the form of discs and the element 1107. The shaft 1108 is connected without rotation to the flange and the toothing or the gear 1109 is connected in positive engagement to the shaft 1108 or formed of a standing alone with him. The gear 1109 meshes with the toothed sector 1110 and rotates the central switching shaft 1111 when the electric motor is driven. At the central switching shaft 1111 are arranged the switching finger or fingers 1112a, 1112b intended to penetrate into the switching openings 1113 of the switching rods of the gearbox. The finger 1112a operates the switching of the forward speeds, the switching finger 1112b operates in this embodiment the switching opening for the operation of the reverse gear. The electric motor 1102 also comprises a lead screw 1120 which meshes with the gear 1121 of lead screw.

The lead screw gear is housed in the area of the axis 1122 and includes a gear 1123 which includes a switching finger 1124. The switching finger enters a recess 1125 in the central switching shaft and the switching finger switching is pivoted around the axis 1122 during a rotation of the gear 1121 so that the central switching shaft 1111 is moved axially. In this way, the switching fingers 1112a, 1112b are raised or lowered in the axial direction. The recess 1125 can be machined by removing chips, for example by milling.

 Figure 24 shows the device from another perspective which represents the switching finger 1124 which penetrates into the recess 1125 of the central switching shaft 1111 in order to control a displacement movement of the central switching shaft during a pivoting of the finger 1124. The toothed sector 1110 is connected to the lower end zone of the central switching shaft 1111 by means of the connecting element 1132 with screws or rivets, or by welding, for example by welding by friction, laser welding, spot welding or the like. The switching finger 1112a as the switching finger 1112b is formed integrally with the toothed sector 1110, being, for example, manufactured in the form of a machined part in sheet metal. The contour can then be manufactured by stamping a sheet and then be machined by a die-stamping or deformation process.

 Figure 25 shows in fragmentary view the same finger 1124 which enters the recess 1125, the finger 1124 being connected in one piece with the gear 1121 and being housed in rotation about the axis 1122.

 Figure 26 shows in fragmentary view, the same central switching shaft 1111 with the recess 1123 and the switching finger 1124. At the lower end of the central switching shaft, the toothed sector 1110 is connected to the switching fingers 1112a and 1112b using the connecting element, for example a riveted or screwed connection.

 The switching finger 1112a enters one of the switching openings 1113. By the effect of a displacement of the switching finger 1112a along the axis of the central switching shaft 1111, the switching finger enters a switching opening, and the speed to engage in the gearbox is thus selected. A rotation of the switching finger 112a about the axis of the central switching shaft 1111 causes the sliding of a switching fork 1130 along the associated switching rod and therefore the switching of the gearbox and the engagement of a speed. A switching motor 1101 and a selection motor 1102 are used to generate the rotational and running movement of the switching finger 1112a, necessary for switching the gearbox. The switching motor transmits a rotational movement of the output shaft via a worm and a worm gear, i.e. a worm mechanism , to an input element of a pre-stressed elastic member, this input element consisting of two discs 1105 and 1106. The force flow is transmitted via force accumulators to the flange 1107 and from there to the shaft 1108, and from there to the gear 1109 which is meshed with the toothed sector 1110 of the central switching shaft. The worm gear, the damping element 1105 to 1107 and the gear 1109 are rotatably housed on a half-shaft, which is designated by 1140. The half-shaft 1140 is housed on one from its sides in the switch motor housing and on the other side in the actuator housing. The connection of the worm gear on the outlet side of the elastic member, for example the element 1105, 1106 and the connection on the outlet side of the elastic member, the flange 1107, is preferably carried out by the intermediate pairs of teeth, for example an internal toothing and an external toothing, as shown in FIGS. 20 to 22.

 The rotational movement is transmitted from the gear 1109 to the toothed sector 1110 by means of a spur gear system. The gear 1109 can also consist of a toothed sector, the axial dimension or length of the gear 1109 being selected in such a way that the engagement of the elements 1109 and 1110 remains guaranteed in the event of axial displacement of the central switching shaft.

The toothed sector 1110 could also be of an axial length such that the meshing remains guaranteed, the gear 1109 being able to be made shorter. It may be advantageous for the toothed sector 1110 and the switching fingers 1112a, 112b to be connected in positive engagement or to be formed in one piece.

An additional switching finger 1112b may be provided in addition to the switching finger 1112a, in the case where the gearbox is constituted in such a way that the reverse gear is for example switched by means of another switching finger than forward gears. The switching finger 1112b can then also be formed in one piece or in positive engagement with the second switching finger and / or with the toothed sector.

 The toothed sector 1110 and the switching fingers 1112a, 1112b are connected without rotation to the central switching shaft, the central switching shaft being guided in a sliding bearing bush mounted in tight fit in the actuator housing.

 The selection motor transmits the rotational movement of its output shaft by means of a worm and a worm gear, therefore a worm mechanism, to an eccentric, for example a switching finger 124. The worm gear and the eccentric are rotatably mounted on the half-shaft of the selection motor 1122, which can rest on one of its sides in the housing of the selection motor. selection and on the other side in the actuator housing. The eccentric, for example the finger 1124, enters an opening, for example the recess 1125, of the selection fork fixed on the central switching shaft or formed integrally with it, so that a movement of rotation of the eccentric causes the central switching shaft to slide in its axial direction.

 The opening 1125 of the selection fork can be made in such a way that the rotational movement can be carried out, in the travel and rotation zone of the central switching shaft which is necessary for the switching of the gearbox. speeds, regardless of the position of the eccentric. This means that the opening 1125 of the selection fork can be large enough for the switch fork finger 1124 to remain in engagement with the opening 1125 under the effect of the rotation of the central switching shaft.

 The teeth of the gear 1109 for switching the gearbox and the toothed sector 1110 are produced in such a way that the layout of the tooth blanks is in the direction of the axis of rotation.

In the stroke and rotation zone of the central switching shaft, necessary for switching the gearbox, a movement of the toothed sector and of the fixing finger which is fixedly connected to it can be carried out in the axial direction of the central switching shaft independently of the angle of rotation of the toothed sector. This is achieved by the fact that either the gear 1109 or the gear 1110 is of a length which corresponds at least to the travel area of the central switching shaft, so that the engagement of the elements 1109 and 1110 remains guaranteed, even for a full stroke of the central switching shaft.

 The switching finger 1124 intended for selection can advantageously be produced in the form of an element with a cylindrical configuration. The operating finger of the selection process can also be made of a constant thickness or according to a contour in the form of a constant thickness, so that an angular rotation of the finger causes the central switching shaft to move axially which is proportional to the angle of rotation of the finger. This achieves that the effective radius of the switching finger is kept approximately constant when pivoting away from the middle position, the ratio between the pivot angle of the eccentric and the stroke path of the 'central switching shaft having a substantially ideal linearity and the clearance between the opening of the selection fork and the eccentric is therefore substantially equal in all angular positions.

 Figure 27 shows an embodiment of an elastic member arranged in the force flow between the electric motor and the central switching shaft, in which a disc-shaped element 1105 is in connection in positive engagement with the element 1106 in the form of a disc, for example by a snap connection or by means of tabs 1105a.

Between the two elements 1105 and 1106 is arranged a component 1107 in the form of a disc. On the drive side, the element 1105 has a toothing 1180 with an internal toothing configuration. The worm gear 1104 of FIG. 23 is for example in connection with this toothing. The element 1107 comprises a flange 1107a projecting in the axial direction which has a toothing 1181 in the interior zone.

The shaft 1108 is for example in connection in positive engagement with this toothing 1181.

 Elements 1105 and 1106 have housing zones 1182 and 1183 in the form of shells, which receive force accumulators 1184. Element 1107 comprises recesses or windows 1185 in which the force accumulators are placed. The recesses 1182 and 1183 for accommodating the force accumulators are substantially of a length which is approximately equal to the axial extension of the force accumulators 1184, so that the force accumulators can be received under preload in the housings. During a relative rotation between components 1105 and 1106 and component 1107 in the form of a flange, a force urges the force accumulators 1184 and causes a transmission of torque, from element 1105 to element 1107. The prestressing of the force accumulators can be selected in such a way that, for example, compression of the force accumulators takes place only when the transmissible torque is greater than the prestressing force of the force accumulators. If the applied torque then continues to increase, the force accumulators are compressed in a manner substantially proportional to this force and reach a state in which the force accumulators wind up are blocked for a force value or a higher torque value which can be defined beforehand, or stops between the elements 1105 and 1107 are blocked. When the torque increases from this force or torque value, the transmission takes place in positive engagement, without any damping effect on the force accumulators.

 It is also the object of the invention to provide an operating device, for example an actuator, of an automatic gearbox which has a small or reduced number of parts, which can also be easily mounted by the manufacturer of gearboxes or the vehicle manufacturer, and whose space requirements are low. It is also advantageous to be able to avoid any major modifications to already existing boxes.

 Figures 29 to 32 show another embodiment according to the invention.

 On the gearbox 1201 is fixed the actuator 1202, for example an operating device, provided with electric motors 1203, 1204 and a reduction mechanism for operating the switching process and the selection process. The switching movement is transmitted in the form of a rotary movement to the central switching shaft 1205. The movement is transformed from the electric motor 1203 to the central switching shaft 1205 by means of a screw mechanism. 1206 worm gear. The rotational movement of the electric motor is transmitted to shaft 1207 through the worm gear mechanism.

On the shaft 1207 is further mounted without rotation a toothing 1208 which drives a toothed sector 1209 which is fixed on a socket 1210. This socket is connected without rotation via a bolt 1211 to the central switching shaft 1205. The drive torque from shaft 1207 is thus transmitted to the central switching shaft.

 The selection of the lane of the diagram is carried out by a reciprocating movement of the central switching shaft 1205. The transformation of movement of the electric motor 1204 to the central switching shaft is also carried out by the through a worm gear mechanism 1212. The rotational movement of the electric motor is transmitted to the shaft 1213 through the worm gear mechanism.

The shaft 1213 is further provided with a short lever 1214 mounted without rotation. The other end of this lever, or of this finger, enters a notch 1215 on the outside of the socket 1210. In this way, the pivoting movement of the lever 1214 is converted into the running movement of the socket 1210.

This socket is fixedly connected by means of a bolt 1211 to the central switching shaft. In this way, the pivoting movement of the lever 1214 is transformed into a running movement of the central switching shaft.

 During the selection process, that is to say during the stroke movement of the central switching shaft 1205, the toothed sector 1209 slides back and forth along the gear 1208 of the switching motor. When switching inside lane 3/4, the meshing takes place halfway up the gear 1208. For lane 1/2 or lane 5 / R, the meshing takes place respectively in the lower third and the upper third of the gear 1208.

 The signals and the electrical energy come from the outside, respectively to the electric motors 1203, 1204 via a plug not shown.

 The use of the socket 1210 for the operating device is relatively advantageous.

It allows the mounting of the complete actuator on the end of the central switching shaft. Such a solution is advantageous in many existing vehicle gearboxes because the central switching shaft is directly incorporated in the gearbox and is not part of a switching dome or an integral module.

According to the embodiment shown in
Figures, the actuator 1202 already completely assembled can be assembled on the gearbox 1201 already assembled. It is appropriate here that the central switching shaft 1205 is guided through the actuator or the socket 1210 and is connected without rotation to the socket 1210 by means of the bolt 1211.

The actuator 1202 is then screwed onto the gearbox housing.

 The actuator is mounted in a sealed manner vis-à-vis external dust by means of a shaft sealing ring 1216 at the top, at the location to which the socket 1210 is routed.

 Figures 33 to 38 show another embodiment of the invention. The gearbox operating device operates a gearbox with two operating shafts, for switching and selection, which protrude out of the casing. Due to the internal structure of the gearbox, the screw connections favorable to a solution by pure addition for fixing the actuator housing and the housing positions of the drive shafts are not on the same part.

The important points here are - operation of the switching shaft by the second
mechanism stage and by an additional trainer
to compensate for axial tolerances - direct operation of the switching shaft by the
second stage of mechanism using a type of
teeth which are not sensitive to small
variations in the distances between the axes - maneuvering the selection tree using a
sliding mechanism.

 The gearbox has the following features or characteristic parts: gearbox housing 1301, gear bell housing 1302, switching shaft 1303. The switching of the gears is effected by a rotation 1304 of the switching shaft. The lane selection is carried out by a rotation 1306 of the selection shaft 1305. This simultaneously results in a longitudinal displacement 1307 of the switching shaft 1303.

 The switching shaft 1303 could also be used as a single central switching shaft, with a rotation for switching and a translation for selection.

 To fix the gearbox actuator as an addition to the gearbox, the screwing 1308 of the parts 1301 and 1302 of the gearbox is suitable. The dividing line 1309 is characterized. By using these existing screwing points, no modification of the casing is necessary from the gearbox manufacturer.

 The switching shaft 1303 and the selection shaft 1305 are fixed by means of an internal intermediate piece on the housing part of the clutch bell 1302.

 The tolerances of relative positions of the switching shaft 1303 or of the selection shaft 1305 on the one hand and of the screwing points 1308 on the other hand are relatively large.

 In Figure 34 is shown for example the gearbox-gearbox actuator assembly. The Figure clearly shows the gearbox 1301, the actuator housing for the switching operation 1311a, the actuator housing for the selection operation 1311b, the drive motor 1312 for the switching and the drive motor 1313 for selection.

 In numerous exemplary embodiments, it is advantageous to use a second stage of a reduction mechanism in the range from 2 to 5, in particular in the field of the switching actuator assembly. Due to its constant reduction, a spur gear stage is suitable here. This results in requirements as to the accuracy of the distance between axes and the angular offset of the axes.

 Figure 35 shows a cross-sectional view of a switching actuator. A carrier element 1314 for the actuator assembly is screwed onto the gearbox casing 1301 at the existing screwing points. The drive motor 1312 for switching is arranged in such a way that it conforms as much as possible to the gearbox housing and that the axis of the output pinion is parallel to the switching drive shaft. 1303 subject to defects related to tolerances.

 On the upper side is flanged, on the switching drive motor 1312, a housing 1316 comprising a gear stage which consists of a pinion 1315 and a toothed sector 1317. The distance between the axes of the two elements 1315 and 1317 with mesh teeth can be produced in this arrangement according to sufficiently small tolerances.

The housing 1316 which comprises the second reduction stage and the switching drive motor 1312 are screwed together 1318 on the carrier element 1314.

 The toothed sector 1317 transmits the movement to a driver 1320 via a shaft 1319 from the housing 1316. The driver is notched in the present case, see Figure 3. In the notch protrudes a lever 1321 which is fixed to the switching operating shaft 1303 of the gearbox 1301 and which is profiled convexly in 1322, remaining of a constant thickness in a particularly advantageous manner, for reasons of minimization of play and sensitivity to tolerances.

 In the variant shown, the driver 1320 must be configured in such a way that contact with the lever 1321 is still guaranteed in the highest position 1323 and the lowest position 1324. The pole pot 1325 of the motor drive is outside the pivot area of the driver 1320 and the lever 1321.

 The arrangement shown can be produced very economically by manufacturing the housing 1316 in the form of a machined sheet metal part, an aluminum cast part or an injection molded plastic part. Manufacturing processes suitable for the toothed sector 1317 are for example precision cutting or precision stamping. The driver 1320 is based on a machined sheet metal part, the necessary stability of the notch can be achieved by welding or by masting 1326.

 It may be advantageous for the carrying element 1314 and the housing 1316 to be made in one piece, the switching drive motor being arranged as the highest element. It may also be appropriate to provide an exchange between the notched driver 1320 and the lever 1321. It is advantageous that a sufficiently exact position of the axis of the second stage of the mechanism is achieved by means of a positioning in the housing d actuator and tolerance compensation by coaches at the output of the second stage of the mechanism. This also results in a compact arrangement, separating the carrier and the housing from the second stage of the mechanism.

Economic manufacture of the actuator output with toothed sector, shaft and notched drive can be carried out by the structure shown.

 Figure 37 shows a cross-sectional view of the switching actuator assembly. The actuator housing 1311a is connected to the gearbox casing 1301 at the existing screwing points 1308. The drive motor 1312 for switching is arranged in such a way that its center of gravity is arranged as vertically as possible above the screwing points 1308.

The axis of the output pinion 1316 must be as parallel as possible to the switching axis 1303 of the gearbox.

 The output pinion 1315 directly drives the toothed sector 1326 connected to the switching shaft 1303, to perform the switching operation 1304.

As the switching motor 1312 and the output pinion 1315 are connected via the actuator housing 1311a to the gearbox housing 1311 and the switching shaft is connected to the clutch housing 1302 by an element internal intermediate, the distance between the axes of the teeth strongly depends on the tolerances. In order to keep the influence of backlash as small as possible, it is possible to preferably select a type of toothing which is insensitive to variations in distance between axes in the range of tenths of a millimeter, for example an involute toothing at low angle of attack and negative profile offset.

In order to achieve a compact arrangement of the switching actuator assembly and as small a distance as possible between the switching motor 1312 and the gearbox casing 1301, the toothed sector 1326 is made bent.

 The housing 1311a of the actuator is closed by means of a plastic cover 1327 after being screwed onto the gearbox 1301, in order to prevent the escape of lubricant and to protect the toothing from the humidity and dust. The plastic cover is made in such a way that it does not prevent the selection movement 1307 of the switching shaft 1303.

 For the illustrated arrangement of switching actuator, advantageously used as manufacturing method for the actuator housing 1311, aluminum die casting or plastic injection molding, optionally providing a composite material. fiber. The closure cover 1327 is produced in the form of an injection molded plastic part and a manufacturing process such as precision cutting with an integrated deformation step is suitable for the toothed sector 1326.

 Figure 38 shows in cross section the actuator box 1311b. The selection motor 1313 is screwed onto the actuator housing 1311b open downwards and to the side so that its output shaft, to which the engine lever 1329 is attached, is as parallel as possible to the selection 1305.

 The selection movement of the motor lever is transmitted, via the selection pin 1330 housed in rotation, to the selection lever 1331 connected without rotation to the selection shaft 1305. The selection shaft 1331 is notched for receive the selection pin 1330, the tolerances relating to its diameter and to the width of the notch being as narrow as possible to minimize the play.

 A suitable manufacturing method for the selection lever is a stamping followed by precision machining of the notch and the bore, or precision cutting.

 FIGS. 39 and 40 show operating devices in accordance with the invention, for an automated operation of a gearbox in order to maneuver the switching and selection movement of a central switching shaft of a gearbox, an electric motor being provided for each of the maneuvers, for example a rotation and an axial displacement of the shaft. Figures 41a to 41c each show a cross-sectional view or an elevational view of an element of the device.

 The device 1400 comprises an electric motor 1401 which comprises on the outlet side a worm 1403 of a worm mechanism. This worm 1403 meshes with a worm gear 1405 which is connected by means of a shaft to a gear 1412, for example a pinion. This pinion meshes with the teeth of a toothed sector 1413. A switching finger 1415 is connected without rotation and is axially fixed to the toothed sector 1413 or is formed integrally with it. The switching finger 1415 enters one of the openings 1416 of switching forks. The switching fork is maneuvered and a speed is engaged by rotation of the finger 1415. This is controlled by the effect of the operation by means of the electric motor 1402. The motor can be maneuvered in the opposite direction and the finger 1415 can pivot in the same direction back and forth. One gear or another can thus be engaged in the gearbox.

 By sliding the switching finger 1415 along the axis of the central switching shaft 1411, the switching finger is caused to enter a switching fork opening and the gear to be engaged or the corresponding switching channel or the corresponding gear group of the gearbox is selected. By rotation of the switching finger 1415 around the axis of the central switching shaft 1411, the sliding of a switching fork along the associated switching rod is carried out and the switching of the gearbox is effected. so too.

 To generate the rotational and running movement of the switching finger 1415, necessary for switching the gearbox, a switching motor 1401 and a selection motor 1402 are used and are controlled by a control unit.

 The rotational movement of the switching motor is transmitted by means of a worm mechanism, comprising a worm and a worm gear between which an elastic member, for example a force accumulator is interposed, and the movement is then transmitted from this elastic member to the switching pinion 1412. The worm gear 1405, the elastic member and the switching pinion 1412, for example a toothed sector, are housed in rotation on a half shaft 1414, which is housed on one side in the housing of the switching motor and on the other side in the actuator housing 1418. The shaft 1414 can also be received and housed on both sides in the actuator housing.

 The connection and the torque transmission of the worm gear 1405 to the drive side of the elastic member and the connection of the output side of the elastic member to the switching pinion 1412 takes place in the following manner. described above. By means of a spur gear system, the rotational movement is transmitted from the switching pinion 1412 to the toothed sector 1413, the toothed sector 1413 and the switching finger 1415 being able to be connected in positive engagement or to be formed in one piece . Another switching finger 1415a can be positively connected to the toothed sector 1413 or to the switching finger 1415, or be formed integrally with the toothed sector 1413 or the switching finger 1415.

 The toothed operating sector of the switching 1413 and the switching fingers 1415 and 1415a are fixedly connected to the central switching shaft 1412, which for example is produced in at least one sliding bearing bush, mounted in press fit in the actuator housing 1418.

 The selection motor 1402 transmits its rotational movement by means of a worm mechanism 1404 to the pinion 1406a for operating the selection movement. The worm gear 1404 and the selection pinion 1406a are rotatably housed on the half-shaft 1407 which is housed on one side in the housing of the selection motor and on the other side in the housing 1418 of actuator. On the central switching shaft 1411 is housed in rotation the selection rack 1406b, in such a way that the rack 1406b does not rotate when the central switching shaft 1411 rotates about its axis. The teeth of the pinion 1406a and of the rack 1406b are kept parallel to each other, the teeth of the engagement partners reciprocally resting on the teeth blanks. The distance between axes is thus kept constant over the entire width of the toothing contact.

 The selection rack 1406b has surfaces 1419 perpendicular to the axis of rotation of the central switching shaft 1414. The central switching shaft 1414 itself has the corresponding counter surfaces 1420, so that the tangential force of the teeth of the pinion is transmitted via the rack to the central switching shaft 1411. The rotation of the selection pinion 1406a causes the selection rack 1406b and the central switching shaft 1411 to slide along their axis . In this way, the toothed sector 1413 and the pins 1415 and 1415a slide axially, so that they can be slid in different openings of switching forks.

 Internal stops 1423 which limit the area of movement to what is necessary or admissible are produced because of the limited length of the selection rack 1406b and because of the constructive arrangements, for example, partial stamping only on the edge of the component.

 The axes of rotation of the selection pinion 1406a and of the central switching shaft 1411 are perpendicular to each other, so that the rotational movement can be carried out independently of the position of the selection pinion, and vice versa in the movement area stroke and rotation of the central switching shaft 1411, necessary for switching the gearbox.

 The selection rack 1406b is configured, according to a special embodiment, in such a way that it has a slot 1430 along the axis of rotation of the central switching shaft. The slot 1430 is connected in a rotary guide 1421, the rotary guide being of a diameter slightly larger than the width of the slot.

The central switching shaft 1411 has a zone 1422 whose diameter is greatly reduced and corresponds to the rotary guide of the selection rack 1406b. Rotational guidance can also be carried out by zones, for example only on the axial marginal zones or on the edges of the selection rack 1406b. The selection rack is attached by the slot 1430 on the central switching shaft. Since the dimension of the central switching shaft 1411 is slightly larger than that of the slot 1430, there is a positive engagement connection, for example a snap connection. Since the selection pinion is still engaged in the selection rack 1406b due to the internal abovements mentioned above and the distance between axes is ensured due to the above-mentioned embodiment of the teeth, this cannot be pulled down by the central switching shaft.

 The teeth of the switching pinion 1412 and of the toothed sector 1413 are produced in such a way that the outline of the blanks of the teeth is in the direction of the axes of rotation. In the area of the movement of movement and rotation of the central switching shaft, necessary for the switching of the gearbox, a movement of the toothed sector and therefore of fingers fixedly connected can be executed in the axial direction of the central switching shaft, independently of the angle of rotation of the toothed sector.

 The teeth of the switching pinion 1412 and of the toothed sector 1413 can also be produced in such a way that the partners of the teeth are mutually supported, for example, by tooth blanks.

 According to another kinematics of the central switching shaft 1411, in which a switching movement is a sliding movement and a selection movement is a rotary movement, the structure principle shown can be used since the switching movement becomes the selection movement and vice versa.

 The central switching shaft 1411 has at one of its end zones a zone 1432 with reduction in diameter, which is blocked by a blocking button 1431.

 This zone 1432 is received by the recess 1433 of the rack 1406b and is housed in rotation but axially fixed. To this end, the rack 1406b has, on both sides of the slot 1419, faces 1435 which prevent the rack 1406b from spreading.

 According to the invention, the vehicle comprises a drive motor, a gearbox and a torque transmission system, for example a clutch, an automatic gearbox operation device which is equipped with a control unit. and at least one actuator capable of being controlled by the control unit for automatic switching / selection of a gear reduction of the gearbox. The control unit is here in connection of signals with at least one sensor and possibly with other electronic units.

The actuator comprises a first drive 1401 for maneuvering a gearbox element 1416 to switch a gear reduction and a second drive 1402 for operating a gearbox element 1411 to select a gear reduction , the first drive 1401 operating an element of the gearbox 1416 or the device 1411 for switching the gear reduction by means of a first mechanism, for example a mechanism 1403, 1405 with worm gear downstream of which is arranged a mechanism 1412, 1413 with spur gears, and the second drive maneuvers an element of the gearbox or the device 1411 for selecting the gear reduction by means of a second mechanism, for example a 1404, 1404a worm gear, a 1406a spur gear that meshes with a rack 1406b is disposed downstream of the mechanism 1404, 1404a with a worm screw and the rack 1406b is received by being housed in rotation on a shaft 1411 movable axially and capable of turning. It is appropriate that the shaft 1411 can be relieved the teeth. The rack 1406b comprises in the axial direction a bore 1433 or a slot 1430 which receives in rotation but axially fixed a zone 1432, with reduced diameter, of the shaft 1411. The shaft 1411 comprises a zone 1432 with reduced diameter which carries in rotation the rack 1406b, a limit stop 1431 which axially ensures the rack being connected to the shaft. The end-of-travel stop is advantageously made in one piece with the shaft. In another embodiment, the rack is connected in positive engagement to the shaft. According to another exemplary embodiment, the rack is screwed by thread to the shaft.

 The rack has a central recess 1403, for example a bore, which extends in the axial direction1 and a slot 1430 which extends in the axial direction, the rack comprising, on each side of the slot, deformable elastic faces which limit the slot.

 The rack is of a substantially hollow cylindrical configuration, the slot of the rack being arranged in a face region opposite to the toothing.

 It is advantageous for the rack 1406b and / or the gear 1406a which meshes with it to be made of plastic.

 FIG. 42 represents a fragmentary view of an operating device according to the invention, in which the shaft 1411 as well as the toothed sector 1413 which is connected to it are only represented. The Figure further shows the switching fingers 1415 and 1415a which are fixedly connected to the shaft 1411 or to the toothed sector 1413. The switching fingers 1415 and 1415a operate, entering a opening of the switching fork, the forks switch 1416 to engage a gear in the gearbox.

The axial displacement of the shaft 1411 or the selection displacement is carried out by means of a drive of the shaft by means of a gear or pinion which is not shown in the
Figure 42. At the upper end of the shaft is produced for this purpose a toothing which is produced on the cylindrical surface of the tree, and the individual teeth of the toothing are of circular circular outline or are produced in the form of segments of circles, which extend over a partial angular range of the shaft. The gear therefore meshes with the toothing 1490 of the shaft 1411, while the shaft is however movable in rotation in contact with the toothing. In this regard, the teeth 1490 are arranged in such a way that the shaft can rotate. The teeth of the teeth 1490 are produced and arranged concentrically with the axis of the shaft.

 In the current traffic density conditions, it is advantageous to automate the manually known gearboxes, generally known, by means of a gearbox actuator assembly in order to automate the selection and switching process. and possibly the clutch process.

 In the case of gearboxes onto which a switching dome with a central switching shaft which projects into the gearbox can be screwed, devices according to the invention are shown in the embodiments described above. If the gearbox does not have a switching dome with a central switching shaft, but a switching shaft protruding out of the gearbox, this switching shaft is rotated for lane selection and slid in translation for the switching operation. switching. In such gearboxes, an articulation of actuators with electric drives is produced on this switching shaft. As the gearbox actuators are driven or maneuvered by electric motors, it is advantageous for the adaptation of the rotation speed or of the torque to use a second, additional stage of mechanism, both for the selection and for the switching operation: see Figure 43.

 The second stage of the switching operation mechanism essentially consists of a stage of gears and a lever which transforms the rotational movement of a toothed sector into a linear movement. For the selection movement, a second stage of the gearbox can be advantageously produced by a kinematic chain with four joints articulated in space.

 It is advantageous if the influence of the switching movement on the selection arm fixed on the switching shaft is weak or nonexistent.

 If this selector arm is driven during a changeover, so that a declutching is necessary, an appropriate control strategy makes it possible to achieve a declutching advantageously, the selection motor being adjusted during the changeover by means of a compensation curve.

 The gearbox to be automated, including its gearshift shaft, has the following features or characteristic parts: gearbox casing, intermediate box, switching catch retainer, switching shaft, gear shifting s '' by sliding the switching shaft and selecting the lanes by rotating the switching shaft.

 For centering and arrangement, for example fixing, of a gearbox actuator mounted by addition on the gearbox housing, threaded bores are suitable on the gearbox housing. Additional fixing of the gearbox actuator can be carried out on other bores. By using these already existing locations on the gearbox, no modification of the gearbox is necessary from the gearbox manufacturer.

 In Figure 43, the gearbox housing 1501 and the actuators are shown together.

Note the gearbox housing 1501, the switching motor 1511, the motor plate 1512, the actuator housing 1513, the housing bolt 1514 for centering the gearbox actuator relative to the housing of the gearbox, the switching lever 1515, the selection arm 1516, the couplings of the kinematic chain 1517 with four articulated joints, the selection motor 1518 and the actuator support 1519. The actuator support 1519 is screwed to the gearbox housing in positions 1510.

 Figure 44 is a cross-sectional view of the gearbox actuator. The actuator housing 1513 is centered by means of the housing bolt 1514 on the gearbox housing, where it enters a bore. In the actuator housing 1513 there is a gear stage which consists of a motor pinion 1522 and a toothed sector 1523. The toothed sector 1523 is housed in rotation, together with the switching lever 1515, on the housing bolt 1514. In this way, the distances between the middle of the toothed sector and the switching axis 1504 and the motor pinion 1522 are fixed according to undemanding tolerances. The toothed sector 1523 transmits to the switching lever 1515 its pivoting movement via a link in positive engagement. The pivoting movement of the switching lever 1515 is transformed into a linear switching movement 1507 by means of a spherical head 1524 which enters an opening in the shaft. The selection arm 1516 is split to compensate for the differences in height of the spherical head which appear in this case. The arrangement shown can be performed while greatly minimizing manufacturing costs since the actuator housing 1513 can be manufactured in the form of machined sheet metal parts, aluminum die-cast parts or injection-molded plastic parts. Precision cutting, sintering or precision casting methods are suitable for the toothed sector 1523. The switching lever 1515 can be manufactured by casting or by stamping. It is advantageous that the precise axis position of the second stage of the mechanism is known sufficiently by the housing of the toothed sector and of the motor pinion in the housing of the actuator. It is also advantageous for a sufficiently precise position of the axes of the lever reduction ratio to be known by the housing of the switching lever on the housing bolt.

 In Figure 45 is shown the kinematic chain with four joints articulated in the space of the selection actuator assembly. The axis 1525 of the selection motor is housed in the actuator support fixed on the gearbox casing.

The selection lever 1521 is attached to the axis 1525 of the selection motor, so that the position of the selection lever 1521 relative to the gearbox housing 1501 and therefore relative to the switching shaft 1504 is clearly defined . When the selection lever 1521 is rotated about its axis of rotation 1525, the selection arm 1516 is articulated by means of the coupling 1517 and is rotated. This rotation is transmitted via a positive engagement link to the switching shaft 1524 and thus generates the pivoting movement 1528 for lane selection.

 The kinematic chain solution with four articulated joints shows that the selection arm 1516 is driven during switching and that, in this way, the lever behavior of the kinematic chain with four articulated joints and the association between the position of the lever 1521 and the position of the 1516 selection arm vary. In order to avoid stressing the kinematic chain with four articulated joints, the selector lever is rotated during the switching process in a way which corresponds to a characteristic compensation curve.

 The arrangement shown can be realized without using many components since the switching lever 1521 can be manufactured by precision cutting, by stamping, by sintering, by casting or by plastic injection molding. A round product from a rod or plastic injection molding is suitable for the 1517 connecting rod. The selection shaft can be produced as a cast steel part or as a welded group.

 Since the selection motor axis is housed in the actuator support 1519, the position of the selection lever 1521 relative to the selection arm 1516 is defined with sufficient precision. An arrangement comprising a small number of simple components can be achieved by software compensating for the effect of switching movement on the selection actuator assembly. The kinematic chain solution with four articulated joints is also likely to select in four corridors.

 In Figure 46 are shown the essential components of the slide solution. By rotation of the selection lever 1521 around the axis 1525 of the selection motor, the selection arm 1516 is articulated by means of a spherical head with the slide positioned 1526. A connection in positive engagement between the selection arm 1516 and the switching shaft 1514 generates the selection movement 1508. The notched embodiment of the selection arm 1516 makes it possible to maintain an unchanged position for the slide during the switching process, without this resulting in a modification of the reduction in gear of the selection actuator assembly.

 The claims appended to this application are proposed formulations, without prejudice to the obtaining of patent protection which continues. The plaintiff reserves the right to claim still other particularities which are so far only exposed in the description and / or the drawings.

 References used in the sub-claims relate to the further development of the subject-matter of the main claim thanks to the features of the respective sub-claims; they should not be considered as a renunciation of obtaining independent protection of the subject of the particularities of the subclaims concerned.

 But the objects of these subclaims also constitute autonomous inventions, which represent a configuration independent of the objects of the preceding subclaims.

 The invention is also not limited to the example or examples of embodiment of the description. Rather, many alterations and modifications are possible within the framework of the invention, in particular variants, elements and combinations and / or materials which are for example inventive by combination or transformation of the particularities or elements or process steps described in the general description and embodiments as well as the claims and contained in the drawings, and which lead by particulars combinable to a new object or to new process steps or sequences of process steps, insofar as they relate manufacturing, verification and machining processes.

Claims (13)

 1. Motor vehicle comprising a drive motor, a gearbox and a torque transmission system, for example a clutch, an automatic gearbox operating device, a control unit and at least one actuator that can control the control unit so as to automatically switch / select a gearbox from the gearbox, in which  - the control unit is connected to signals with at least one sensor  the actuator comprises a first drive for maneuvering a gearbox element to switch a gearbox reduction and a second drive, for maneuvering a gearbox element to select a gearbox reduction,  characterized in that  - The first drive operates an element (101) of the gearbox, intended to switch the gear reduction, by means of a first mechanism, for example a worm mechanism downstream of which is arranged a spur gear mechanism; and  - The second drive operates an element (102) of the gearbox, intended to select the gear reduction, for example a worm mechanism downstream of which is arranged a spur gear which meshes with a received rack housed in rotation on a rotating and axially movable shaft.  2. Vehicle according to claim 1, characterized in that  - The shaft (102, 1411) can be raised and lowered (moved) by means of the second drive by means of a worm mechanism and a gear mounted downstream and the rack.  3. Vehicle according to claim 1, characterized in that  - The shaft (101) can rotate under the effect of the first drive via an endless screw and a worm gear and optionally a spur gear mechanism mounted downstream.  4. Vehicle according to claim 1, 2, or 3, characterized in that  - the shaft (1411) can rotate under the effect of the first drive and can be raised and lowered under the effect of the second drive and in that  - The rack (1406b) is rotatably mounted but axially fixed on the shaft and cannot rotate relative to the gear which meshes with the rack when the shaft is turned.  5. Vehicle according to one of the preceding claims, characterized in that  - The rack (1406b) has a bore or a slot in the axial direction which receives in rotation but axially fixed an area of reduced diameter of the shaft (1411).  6. Vehicle according to claim 5, characterized in that  - The shaft (1411) has a reduced diameter area which rotates the rack (1406b), and in that  - a limit stop, which axially blocks the rack is connected to the shaft.  7. Vehicle according to claim 6, characterized in that  - the limit stop is made in one piece with the shaft (1411)  8. Vehicle according to claim 6, characterized in that  - the limit stop is connected in positive engagement to the shaft (1411).  9. Vehicle according to claim 6, characterized in that the limit stop is screwed to the shaft (1411) by means of a thread.  10. Vehicle according to any one of the preceding claims, characterized in that  - the rack (1406b) has a central recess which extends in the axial direction, for example a bore, and a slot which extends in the axial direction and in that  - the rack (1406b) has faces. deformable elastics which limit the slit.  11. Vehicle according to claim 10, characterized in that  - The slot of the rack (1406b) is arranged in a face area opposite the toothing.  12. Vehicle according to claim 10, characterized in that  - the rack (1406b) and / or the gear (1406a) which meshes with it is made of plastic.  13. Motor vehicle comprising a drive motor, a gearbox and a torque transmission system, for example a clutch, an automatic gearbox operating device, a control unit and at least one actuator that can control the control unit so as to automatically switch / select a gearbox from the gearbox, in which  - the control unit is connected to signals with at least one sensor;  the actuator comprises a first drive for maneuvering a gearbox element to switch a gearbox reduction and a second drive for maneuvering a gearbox element to select a gearbox reduction,  characterized in that  - The first drive (1401) operates an element of the gearbox, intended to switch the gear reduction, by means of a first mechanism, for example a worm gear mechanism downstream of which is arranged a spur gear mechanism; and  - The second drive (1402) operates an element of the gearbox, intended to select the gear reduction, by means of a second mechanism, for example a worm gear mechanism, downstream of which is arranged a spur gear which meshes with a toothing which is formed, on a rotary and axially movable shaft, by means of teeth arranged concentrically with the axis of the shaft.