JP3025224B2 - Adjustment device of the output part that can be moved by two movement methods - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The invention relates to an adjusting device according to the preamble of claim 1.

[0002]

2. Description of the Related Art According to DE-A 43 11 855, a selector shaft (Schaltwel) of a transmission (transmission, Schaltgetriebe) of a motor vehicle is already known.
An adjustment device (Stelleinrichtung) for the operation of le) is known. In this case, the first drive is arranged perpendicular to the second drive. FIG.
As shown in FIG. 5, the torsion of the selector shaft is generated by a first driving device. The first drive linearly drives the rack. The rack is in mesh with a gear fixedly connected to the selector shaft. Movement of the selector shaft is provided by a second drive. A second drive is operatively connected to the selector shaft for transmitting the movement.
As a result, the linear movement of the drive is transmitted directly to the selector shaft.

Due to this movement, the gear fixedly connected to the selector shaft for transmitting the rotational movement is formed with an axial extent which is such that the rack and the gear are always in mesh. Have been.

[0004] In the case of this transmission mechanism, it is disadvantageous that the gears and the teeth of the rack, which are constantly engaged, friction with each other when the selector shaft moves.
Thereby, this engagement is overloaded.
This leads to tooth wear, which is accompanied by an increase in the play of the meshing teeth. With the use of the adjusting device for the operation of the transmission selector shaft, it is necessary to ensure the operating capacity over a number of gearshifts. For this reason, the illustrated transmission mechanism is unsuitable for use for operating the transmission selector shaft.

[0005]

SUMMARY OF THE INVENTION It is an object of the present invention to provide an adjusting device having a compact construction and an operating mode with low wear.

[0006]

The object of the present invention is attained by a structure according to claim 1.

[0007]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The first drive is pivotally mounted on a slide element which is fixed axially with respect to the output, but which is arranged so as to be relatively movable in the circumferential direction. Thereby, a linear movement in the axial direction can be transmitted to the output unit. The output unit is
It is non-rotatably but axially movable with a second drive. As a result, rotational movement can be transmitted to the output by the second drive device. Both modes of movement can be transmitted to the output without entkoppelt. The output is configured such that the slide element is not compromised (i.e., is not affected) when rotational movement is introduced into the output by a second drive.

[0008] A drive that operates in a straight line or a drive that operates in a rotatorisch manner may be used. If, as a result of the two movements described above, at the output, two similarly operating drives are provided, one of the movements introduced by the drive is converted into another movement at the time. It is necessary to use the transmission of the above. It has proven advantageous to drive the slide element by means of a rotator-like drive. Such a drive and the slide element are operatively connected, for example, via a transmission element for converting a rotation movement (rotational movement) into a linear movement. In order to be able to use the smallest possible drive, it is advantageous to provide a gear element which acts as a reduction gear.

The use of a crank mechanism (crank transmission) has been found to be advantageous. Due to the adjustment of the different axial positions of the output, different states (positions) of the slide element, and thus assigned to the desired axial position of the output, are reached by the first drive. If the crank mechanism were driven in one direction only, it would have been assigned two crank mechanism states to every axial position of the slide element. Therefore, a unique assignment (Zuo
rdnung), so that the crank mechanism vibrates
(Oszillierend) should be driven.

As another possible transmission element for converting the rotation movement into a linear movement, a rack which is moved linearly by the output element of the first drive can be provided. When using a rack as a transmission element, it is advantageous if the rack can be formed integrally with the slide element. The transmission element is a particularly simple and inexpensive structure. The structural space required by the rack is very small, which has the advantageous effect of a compact structural form.

Furthermore, it has proven advantageous to use a cam mechanism (cam transmission) as the transmission element. The cam mechanism has plateaus having a slight radial inclination. Each of the flat parts is provided at a predetermined switching position (Schalts
(that is, correspondingly). This allows, for example, lanes (Gassen ,
The German words "Gasse" and "Schaltgasse" are replaced by the English word "cros"
s wise is a term for ". is annexed (assigned to)) of the sliding element to the switching position, therefore very tight regulation of the output unit can be achieved.

It is possible for each of these transmission elements to be provided with a return spring (Rueckstellfeder). In this case, the slide element is displaced by the drive against the force of the return spring. With this return spring, on the one hand,
The slide element and the transmission can be kept in operative connection by an external force constraint, while the return movement of the slide element is generated by a return spring which influences the slide element. For this purpose, it is necessary that the drive is switched to coasting (Freilauf).

[0013] The slide element is advantageously mounted in a sleeve provided with a cavity extending in the slide direction. This space is for the slide element
It is penetrated by a radial overhang connected to the output. By providing this sleeve for mounting (support), the load on the slide element is reduced and wear due to wear is prevented. The smooth surfaces of the sleeve and the slide element slide on each other. A sleeve surrounds the slide element, resulting in a compact configuration. It is advantageous if the cavity extending in the sliding direction is formed in the circumferential direction exactly in such a way that the radial extension of the slide element slides in this cavity without play in this direction , i.e. in the axial direction. all right. As a result, the support of the radial extension of the slide element is achieved by a recess that extends in the slide direction. This contributes to reducing the load on the slide element.

The use of a stroke magnet as the first drive has been found to be an advantageous embodiment. This is because the stroke magnet is particularly suitable for the adjustment of the desired lane position (Gassenposition), which requires less force than the gears for adjusting its position. It has proven advantageous to select different lanes by sliding the output. This is because the stroke movement which can then be generated by the stroke magnet can be transmitted directly to the slide element. However, in the case of using a transmission, a stroke magnet may be used for lane selection by rotation.

[0015] It has proven advantageous to create the connection between the second drive and the output by means of a gear rotatably mounted on the sleeve. Proper mounting minimizes the frictional forces exerted during the rotation movement. This gear should not rotate with respect to the output,
However, it is mounted movably in the axial direction. The gear is arranged fixed in the axial direction with respect to the second drive device. As a result, the meshing portion does not wear in the axial direction.

In order to minimize the required construction space, it has proved advantageous to provide a segment gear for the connection between the second drive and the output. The angle range of the segment gear can be matched to the rotation angle range of the output.

In another advantageous configuration, the second drive comprises:
At the rest position of the second drive, a compensating elastic body with maximum prestress is provided. When displaced from the rest position, the torque of the drive device is strengthened by the relaxation of the compensation elastic body. The use of such compensating elastics can assist in gearing. Here, considerable resistance needs to be overcome for the synchronization work to be performed. The compensating elastics are particularly useful in the case of the use of relatively low-power drives. When the engaged gear is released (the gear is removed), there is no need to perform the synchronization adjustment operation. As a result, it does not require assistance by a compensating elastic. However, the power of the second drive must be selected such that the compensating elastic body is again subjected to maximum prestress. The rest position in which the compensating elastic body has the greatest prestress is assigned to the neutral position of the selector shaft.

It has proved advantageous for at least one drive to have an overload protection device (Ueberlastungsschutz). This overload protection device prevents the transmission or continuation of the drive movement of the transmission element when it reaches a stop attached to the transmission element by means of a faulty control in the drive.
It can be activated during g). Thereby, on the one hand, when using a motor as a drive, the motor is protected from overload, which can lead to an overheating condition of the motor. On the other hand, the mechanical load on the parts reaching or at the stop is reduced. This prevents excessive mechanical loads that can cause breakage of those components.

A slipping clutch (slip coupling, friction clutch, Rutsch
kupplung , "Rutschkupplung" in German is "sl" in English
It has been found to be advantageous to create a slip clutch that can be integrated into the electric motor. If the movement introduced by the motor is detected by means of a sensor, the sensor is activated so that the actual adjusting movement and the position are detected. It has proven advantageous to arrange it immediately after the slipping clutch.

Furthermore, it has proved advantageous to provide an overload protection device having elastic elements. This elastic element experiences an elastic deformation against the force introduced from the drive due to damping of the movement of the transmission element when exceeding a predetermined displacement position. Thereby, the maximum displacement in the then predominant movement direction can only be achieved in a weakened (damped) movement configuration.

A switching mechanism (with which a gear selection can be made) by means of an adjusting drive (by means of which the gear selection can be effected), by means of this switching mechanism, an additional movement mode of the output which differs from the gear selection by means of the course of switching of the adjusting drive. , Which can be realized to define the switching lane), an adjusting device having only one adjusting drive can be constructed. Thereby, costs and construction space for the second drive for operation of the output are saved. But,
A switching drive for switching the switching mechanism is required. However, as a switching drive, a drive with very low power and thus a very compact configuration is sufficient.

It has proven advantageous for the switching mechanism to include a locking element. The locking element blocks (blocks) one of the two modes of movement from time to time. As a result, the output can only be driven by the adjusting drive in a non-blocking manner at any time. The lock element has a first pawl. The first pawl fits axially without play in a first recess of the output portion to lock the output portion. Thereby, the output portion is blocked (prevented) from sliding. The locking element has a second pawl. The second pawl fits circumferentially into the second recess to lock the output against movement about its axis of rotation.

It has been found to be an advantageous embodiment to provide (correspond to) a plurality of recesses in the first pawl. In this case, the respective recesses limit the lanes of the gear device connected subsequently to the output.

[0024] The large torque acting on results in the gears being quickly engaged. It has proven advantageous if the second pawl always remains in the second recess. To release the lock, the second pawl is moved to a position in which the second recess is formed larger than the second pawl to ensure rotation movement of the output in the circumferential direction. obtain.

Forming the second recess in the form of a slit has proven to be a particularly advantageous embodiment. In so doing, the second pawl is positioned at the position of the axis of rotation of the output in order to allow rotation movement. In this embodiment, as soon as the second pawl is positioned at a position off the axis of rotation of the output, the output is blocked from rotation. As a result, switching between exercise modes can be realized particularly easily without any overlap between them. The output unit is always exclusively one exercise system,
That is, it can be driven only in the direction of a rotating or linear movement.

The adjusting drive comprises a helical gear (spiral meshing, spiral gearing, Schraegverzahn)
(ung) is connected to the output of the adjusting device. With this helical gear, both rotational and linear movements can be transmitted in a simple manner to the output of the adjusting device. A particularly suitable transmission has been found to be the transmission known from DE 42 38 368 A1.

It has proven particularly advantageous to use an electric motor available as a standard component which is advantageous in terms of price as the drive. These motors are driving devices that work in rotation. The power required for its operation is taken from a generator operated by the vehicle's internal combustion engine. In comparison, hydraulically actuated regulators would require that a separate hydraulic system, including pumps, accumulators (Druckspeicher), and multiple valves be provided for operation of the regulator. Has disadvantages.
The costs for supplying the necessary hydraulic power are thereby considerable. Also, the energy demand is much higher than in electrical systems because of the leaks that are always present in hydraulic systems.

Another advantage with the use of an electric motor is that the current supply line (Stromanschlussleitungen) can be easily laid,
And only a few places are needed. In another particularly advantageous embodiment, the adjusting drive is connected to a flange for connecting to a gear device. The flange is used for receiving an additional element that enables another function. On the one hand, the flange is used for vehicles with manual gearshifts (vehicles with manual transmission, handgeschaltetes Fahrz
eug) gear shift linkage (Schaltgestaenge)
Is formed so as to close the opening provided for the through-guide of the helmet. Thereby, the actuator (adjustment member) can be inserted without having to make any changes to the gear device casing. In addition, the flanges can be provided with sealable through-guides for the injection and discharge of gear oil and through-guides for the sensors (ie ducts for them can be provided).
The temperature of the gearing or the temperature around the gearing so that in the control of the automated gear change (switching process) the increase in the force required to engage the gear as the temperature decreases can be taken into account. It has proven to be advantageous to detect In many vehicles, the control purpose (for example, EKS ,
That sensor for the clutch shaft rotational speed detection utilized in Electronic Clutch system) can be integrated. As a result, the additional device can be spatially centered on the flange, so that the necessary supply lines and conductors (Zu- und Ableitungen) can be bundled and laid on this flange. This has the consequence of being advantageous for manufacturing.

It has proved advantageous for at least one drive to be provided with a device allowing manual adjustment of the output of the drive. This allows the gear to be disengaged (disengaged) by this device for manual operation in the event that the vehicle stalls with the electronics engaged and the gear engaged. As a result, the gears (gear units) are switched without load, and the vehicle can be hauled in a conventional manner by the towing vehicle. However, before the gear is manually disengaged, it is necessary to ensure that the handbrake (parking brake) is applied to prevent the vehicle from moving (Wegrollen) when disengaging the engaged gear .

[0030] Both drives with devices for manual operation may be provided. With this device, these drives can each be displaced in the direction of movement driven in normal operation. This allows you to manually change the gear, especially the start gear (drive gear, Anfahrgan
g , German "Anfahrgang" is English for "starting gea"
r " ).

It has been found to be advantageous to provide the motor shaft of the drive with a concavo-convex shape (groove, profile) at the end opposite the output. This uneven shape corresponds to the corresponding uneven shape (Geg) of the operating element, especially the tool loaded on the vehicle.
enprofil). However, the device may be located elsewhere. In some circumstances, it may be particularly advantageous to choose a predetermined location that is easily accessible. Thereby, in some circumstances, a transmission for a power turn (Kraftumlenkung) may be required.

By manual driving, the output element can be positioned at a desired position, preferably at an idling position. The desired position can be confirmed by the operating force to be consumed. For example, gearing and shedding require more force than adjusting the output element in the region of idling. As a result, the idle position can be identified by a smooth hand operation.

[0033]

Embodiments of the present invention will be described below in detail with reference to the drawings. The basic structure of the adjusting device (Stelleinrichtung) 1 will be described with reference to FIGS.

The adjusting device 1 is provided with a slide element (Schiebeelem) via a crank mechanism (crank transmission) 14.
ent) 7 is connected to the first drive device 3. The slide element is mounted in a sleeve 23 and has a radial (radial) overhang 27 on the end side. The overhang portion penetrates (engages with and penetrates) the space 25 provided in the sleeve 23 to form an output portion (Ausgang).
steil) 9 is fitted into a radial slit (radial slot) 28 extending in the circumferential direction. Sleeve 2
The space 25 provided in 3 is formed in the form of a slit 26 extending in the axial direction.

The output section 9 further has an axial space 35. The axially extending portion 33 of the segment gear (segment gear, Segmentzahnrad) 31 mounted on the sleeve 23 fits into the axial space. The segment gear is
By gearing, reduction gear (Untersetzungsgetriebe)
6, it is in engagement with the toothed shaft (serrated shaft, Zahnwelle) of the active second drive 5;

The function of the illustrated adjusting device will now be described. The adjusting device 1 is provided with a selector shaft (Schaltwe) of a transmission (shift transmission, Schaltgetriebe).
lle) Available for 10 automated operations.
Here, the output 9 of the adjusting device 1 is the selector shaft. The first drive 3 works with an oscillating movement and operates the crank mechanism 14. The crank mechanism 14 is connected to the slide element 7 that performs a linear motion. Through the radial extension 27,
The linear movement of the slide element 7 is transmitted to the output unit 9. At that time, the slide element 7 slides in the sleeve 23 that supports it. The axially extending cavity 25 in the sleeve 23 allows the sliding element 7
Are supported in the circumferential direction.
The desired lane (gear route, Gasse) is entered by this linear movement transmitted to the output unit 9. Gear selection
The rotation is performed by the output unit 9 or the selector shaft 10. The necessary rotational movement is controlled by the second drive 5
Introduced by This drive device 5 drives the segment gear 31. The axially extending portion 33 that fits in the axial space 35 of the output portion 9 causes the segment gear 31 to be moved.
Is transmitted to the output unit 9. The output unit 9 and the segment gear 31 are axially movable relative to each other. As a result, the linear motion transmitted to the output unit 9 does not affect the position of the segment gear 31. The slide element 7 is rotatably connected to the output unit 9. As a result, the second driving device 5
The rotational movement of the output section 9 introduced from does not affect the slide element 7. In order to engage the desired gear, more force is required for lane selection (Gassenwahl). As a result, a relatively powerful drive is required for this. In order to be able to take into account the smallest possible drive, this drive may be provided with a reduction gear 6.

The driving devices 3 and 5 are fixedly connected to the casing 8. The casing, with flange
And can be fixedly connected to the gear device casing . The flange closes a space previously provided for the guide-through of the gearshift linkage (Schaltgestaenge). The flange及 beauty casing 8 easily may be integrally formed.

The adjustment device 1 shown in FIG. 3 for operating the selector shaft 10 essentially corresponds to the adjustment device described with reference to FIG. A difference is that a rack (Zahnstange) 15 is provided instead of the crank mechanism 14. This rack 15 is driven by means of the first drive 3 for the linear movement transmitted to the slide element 7. In the embodiment shown, the slide element 7 and the rack 15 are formed integrally.
The output element 4 of the first drive, which works in rotation, engages the rack 15. The rotation of the output element 4 of the first drive device 3 causes the rack 15 to move axially in the axial direction.

FIGS. 4a and 5 show the following adjusting device. That is, in the case of the adjusting device, a cam mechanism (cam transmission) 17 is attached to the first drive device 3.
Is attached. The rotating output element 4 of the first drive 3 is in engagement with the gear 16. The gear is fixedly connected to a cam (Nocken) 18 or is formed integrally therewith. The end of the slide element 7 moves on the cam 18. The slide element is a return spring (Rueckstellfeder) 19
Thus, the cam 18 is connected to the cam 18 with external force.
However, the working connection between the cam 18 and the slide element 7 may be created by a groove-claw connection.

FIG. 4 b shows a plurality of plateaus 24.
Is shown. These flat parts are arranged corresponding to one lane, respectively.
FIG. 6 shows a stroke magnet (a lifting magnet, Hubmagnet , German “Hubmagne”) as the first drive device 3.
"t" is the English equivalent of "lifting magnet"
That) 21 regulating device 1 having is illustrated. An end of the slide element 7 protrudes into the stroke magnet 21. A return spring 19 acts on the end opposite the end, which has an axial overhang. When the stroke magnet 21 receives the action of the current, the slide element 7 moves the return spring 19 depending on the supplied current or the supplied voltage.
Is moved linearly against the force of Lane selection is performed by the stroke magnet 21. As shown in FIGS. 7 and 8, the connection is made later (nachschalte
n) If lane selection is performed by rotary motion in a gear device (transmission), the stroke magnet 21
Abtriebsteil 22 acts on a turning lever (reversing lever, Umlenkhebel) 30. The turning lever is fixedly connected to the selector shaft 10. On a side opposite to the stroke magnet 21, a return spring 19 is provided. The return spring assures the connection between the turning lever 30 and the driven portion 22 of the stroke magnet 21 that is restricted by an external force.
Trigger of the stroke magnet 21 (activation, Ansteuer
As a result, the driven portion 22 is displaced by the ung) against the restoring force of the return spring 19 acting on the turning lever 30.

The adjusting device 1 shown in FIGS. 9 and 10
Corresponds essentially to the adjustment device shown in FIGS. 1 and 2, but additionally has a compensating elastic body (Kompensationsfede).
r) (for example, compensation spring) 36. This is attached to the segment gear 31. The compensating elastic body 36 is fixedly connected to the segment gear 31 that can be rotationally driven by the second driving device 5, and the adjusting device 1
Is supported by the casing 8. Segment gear 31
Intermediate position (neutral position, Mittelstellun
In g), the compensation elastic 36 has the greatest prestress. When the segment gear 31 is displaced (that is, deviates from the intermediate position) by the second driving device 5, the torque supplied by the driving device is strengthened by the relaxation of the compensation elastic body. This assists and accelerates the process of engaging the selected gear. By means of the second drive 5, the segment gear 31 is again brought into the intermediate position. At that time, the compensation elastic body 36 is prestressed again. The force required for this is provided by the second drive 5. This direction of motion is assigned to disengage (ie, return to neutral) the engaged gear. Disengaging the engaged gear requires less force than engaging the gear. This is because the synchronization adjustment work (Synchro
nisationsarbeit) need not be performed.
For this reason, by providing the compensation elastic body 36,
A second drive 5 with relatively low power can be used to engage the gear.

FIGS. 11 to 14 show one adjusting drive device.
An adjusting device 1 having only (Stellantrieb) 2 is shown. By means of this adjusting drive 2, the helical gear (Schra
A selector shaft 10 as an output 9 of the adjusting device 1 is driven via an e.g. The helical gear 53 has a spindle 54 that can be driven by the adjusting drive 2. This spindle 54 is at the end,
It is mounted using a support (bearing) 63 supported by the casing 8 and is in engagement with the driven element 55. The driven element is fixedly connected to the selector shaft 10. The driven element 55 and the selector shaft 10 may be formed integrally.

The selector shaft 10 has a switching mechanism (S
chaltmechanismus) 49 is attached. The switching mechanism includes a lock element (Verriegelungselement) 50. This locking element 50 is arranged at the end 67 of the selector shaft 10 on the side opposite to the gear device. The lock element 50 includes a switching drive device 59 and a locking element (Rastelement) 65. The locking element comprises a first klaue 39
And a second pawl portion 41. The first claws 39 are provided with a plurality of first recesses (Vertiefungen) 43 (that is, correspondingly arranged), and the second claws are provided with one second recess 45. Have been. The first concave portion 43 is formed on the outer periphery of the selector shaft 10 so as to extend in the circumferential direction at positions shifted from each other in the axial direction. The second recess 45 is disposed on the end 67 of the selector shaft 10 on the distal side. In this embodiment, the second concave portion is formed in a groove shape and intersects with the rotation axis 47 of the selector shaft 10.

Control the switching drive 59 (start, Ansteuer
n), the locking element 65 can be brought into various operating positions. Depending on their operating position,
The manner of movement (axial movement or rotatable) of the selector shaft 10 is adjustable. In the first operating position shown in FIG. 11, the first pawl 39 is engaged in one of the first recesses 43. Thereby, the selector shaft 10 is blocked from linear movement (ie, is prevented from linear movement). At the same time as the engagement of the first claws 39 in the engagement, the positioning of the second claws 41 to the position of the rotation axis 47 of the selector shaft 10 is performed. Thereby,
The oscillating rotation of the selector shaft around the rotation axis 47 and the pawl 41 is possible. As a result, a rotational movement of the selector shaft 10 can be generated by the adjusting drive 2 via the helical gear 53. In the second operating position, the first pawl 39 is withdrawn from the first recess 43. The second pawl portion 41 is at a position deviated from the rotation axis 47 of the selector shaft 10. In this position, the second pawl portion 41 is engaged with the second concave portion 45 in the circumferential direction without play. Thereby, the selector shaft 10 is blocked from rotational movement. Since the spindle 54 of the helical gear 53 has a pitch in the axial direction, a linear movement is transmitted by the adjusting drive 2 to the selector shaft 10.

FIG. 12 is a sectional view showing the switching drive device 59 and the first claw portion 39 which is engaged (bits) in one of the first concave portions 43. The rotation of the selector shaft 10 in the axially locked state is enabled by the expansion of the first recess 43 in the circumferential direction.

FIGS. 13 and 14 partially show another embodiment of the locking element 50. The locking element has a different device from FIG. 11 for blocking the rotary movement of the selector shaft 10. In FIG. 13, the second recess does not intersect with the rotation axis 47 of the selector shaft 10. For this reason, the second recess 45
In order to allow rotational movement (Freigabe), a part of the radially extending portion (Erstreckung) is formed to have a circumferential spread. In the operating position in which the rotational movement of the selector shaft 10 can be generated by the adjusting drive 2, the second pawl 41 is at the position indicated by the broken line in FIG. Is engaged. The locking element partially illustrated in FIG. 14 shows a second pawl 41 formed in a trapezoidal shape. The pawl portion 41 is engaged with a second concave portion 45 also formed in a trapezoidal shape. The circumferential play between the second pawl 41 and the second recess 45 can be adjusted by the radial position of the pawl 41. The second pawl portion 41 and the second concave portion 45 are engaged without play in the circumferential direction.
In the engaged state (depicted in broken lines in FIG. 4), the selector shaft is blocked against rotational movement.

FIG. 15 shows a partial view of the adjusting unit.
The structure for the transmission of the movement introduced from the first drive 3 is shown. The structure shown is distinguished from the structure shown in FIG. 1 in that an overload protection device (Ueberlastungsschutz) 69 is provided. The basic functions described with reference to FIG. 1 continue to be unchanged.

The overload protection device 69 shown in FIG.
It has an elastic element 75. This elastic element is realized by elastic elements (for example, springs) 77 and 79 surrounding the slide element 7 coaxially. On the other hand, these elastic elements 77,
79 is coaxially surrounded by a sleeve 23 used for mounting the segment gear 31. The elastic elements 77 and 79 are respectively provided at the ends on the sleeve 2.
3. The slide element 7 has a support surface (Auflageflaeche) for the elastic elements 77, 79.
n) are provided with radial projections 85, 87. These radial projections 85, 87 increase the diameter of the slide element 7, which diameter is still smaller than the inner diameter 101 of the sleeve 23. The sleeve 23 has on its end side protruding parts 89, 91 formed by a ring and directed radially inward.
These protrusions are respectively elastic element 77,
79 is the second support surface.

Erroneous control of the driving device 3 (erroneous start, Fehlansteu
erung) and the slide element 7 is moved beyond the normal extent in one direction of displacement (Auslenkrichtung).
When it is moved, for example, the protrusion 87 of the slide element 7 comes into operative contact with the elastic element 79 (Wirkkonta).
kt). The kinetic energy of the slide element 7 is at least partially changed to the deformation energy of the elastic element 79 which is impacted and acted on, and the slide element is braked.
As a result, the radial extension 27 is moved to the stopper 88.
Is prevented from hitting.

The structure shown in FIG. 16 is a stopper damper (Anschlagdaempfung) as an overload protection device 69.
This is another embodiment of the present invention. In this embodiment, the intermediate sleeve 93 is used.
including. The elastic element 77 in the intermediate sleeve,
79 are arranged. Elastic element 77, 79
Are sandwiched in the intermediate sleeve 93. Here, the slide element 7 is formed from the rack 15 and the intermediate sleeve 93. In this case, the stopper buffer is integrated with the slide element 7. The intermediate sleeve 93 has at its end opposite the drive a radially inwardly directed projection 95. The projection is a support surface for the first elastic element 79. The first elastic element 7 is inserted into the intermediate sleeve.
9 is inserted. Radially coaxially extending projections 99 forming support surfaces for the elastic elements 77, 79
Is inserted. The second elastic element on the side of the drive 3 is fitted in the rack 15 and the intermediate sleeve 93 is on the end side, for example with a blocking ring
The ssring 97 is closed (sealed) by a reduced diameter (Einschrumpfen). The elastic elements 77 and 79 are confined in the intermediate sleeve 93. The elastic elements 77, 79 are prestressed by the axial push-in depth (Einschiebetiefe) of the shut-off ring 97 in a pre-specifiable manner when closed. Soft elastic body (spring)
Are inserted into the rack 15 and the intermediate sleeve 9 under normal operating conditions (operating conditions).
3 is prestressed to represent a static bond (starre Verbindung). When the radial overhang 27 strikes the stopper 88, the kinetic energy of the rack 15 is at least partly changed to the potential energy of the elastic element affected and the relative movement between the rack 15 and the intermediate sleeve 93. Begins.

FIG. 17 shows a segment gear 31 provided with a stopper damper as an overload protection device. The maximum displacement angle of the segment gear is limited on both sides by stoppers 105. Segment gear 3
1 is a recess 103 for receiving elastic elements (eg, springs) 81, 83 at a height at the stopper.
It has. The elastic element has a limited edge (Begrenzungskant) extending in the radial direction of the segment gear.
e) projecting beyond. Incorrect activation of drive 5 (feh
When the segment gear 31 is displaced beyond its usual extent, an elastic element, for example an elastic element 81, which is arranged on the corresponding side, is attached to this elastic element (corresponding to lerhafte ansteuerung). (Operationally connected to the stopper 105). The kinetic energy of the segment gear 31 is converted into the deformation energy of the elastic element 81 which is acted upon. Thereby, it is only possible for the segment gears 31 to come into collision with slowed down movements.

FIGS. 18 and 19 show a segment gear 31 including an overload protection device 69 having an elastic element (for example, a spring). The segment gear has a cavity 10 for receiving the internal segment car part 107.
9 The segment gear 31 and the inner segment wheel 107 are formed by two elastic elements 81, 8 arranged on both sides of the inner segment wheel 107 tangentially between the inner segment wheel 107 and the segment gear 31.
And 3 are operatively linked . Internal segment vehicle section 10
7 is rotatably mounted on the sleeve 23, wherein smooth rotation is ensured by a slide bearing (Gleitlager) 111. Further, the internal segment wheel portion 107 has an axial extension 33 that bites into the longitudinal groove of the output portion in the axial direction. On the other hand, the segment gear 31 partially rotatably surrounds the internal segment wheel, and is rotatably mounted on the internal segment wheel. The inserted elastic elements 81, 83 provide a rotationally fixed connection between the segment gear 31 and the internal segment wheel 107 during the correct operation (activation) of the drive device 5 (ie, so that they do not rotate relative to each other). Has a spring constant (elastic constant, spring constant) that guarantees connection.

Next, a function method of the overload protection device will be described in detail. As a result of erroneous control (erroneous operation) of the driving device 5,
There is a possibility that the internal segment vehicle portion 107 may hit one of the stoppers arranged in the gear device. When the internal segment vehicle portion 107 hits, a further rotation of the internal segment vehicle portion is hindered. The drive gear 5 drives the segment gear further. The kinetic energy of the segment gear 31 is changed to the deformation energy of at least one of the elastic elements 81 and 83. At that time, the relative movement between the internal segment wheel portion 107 and the segment gear 31 starts. If the elastics (springs) of the elastic elements 81, 83 are fixedly connected on one side at the distal end to the inner segment wheel and at the opposite end fixedly to the segment gear 31. When the inner segment car portion 107 hits the two elastic elements 81 and 83, the stress energy (Spannungsene) is increased.
rgie). In this case, one elastic element receives a tensile load, and the other receives a compressive load.
Another possible embodiment of a stop damper for a segment gear is known, for example, from DE 195 25 840 B1.

FIG. 20 shows an adjusting device 1 having a flange 117 for coupling to a gear device. The flange 117 has a duct 121 for injecting and discharging gear oil. Another additional element 119 is a rotational speed sensor 12 protruding into the gear device for detecting the clutch shaft rotational speed.
A duct for 5 is formed. In this embodiment, the temperature sensor 127 is connected to the casing 8 of the adjusting device 1.
It protrudes only inside. However, this temperature sensor 12
7 may project into the gearing through a duct which may be provided for this. This temperature value is transmitted to a control device, for example a control device for the control of automated gear changes. At this time, the drive device can be controlled (started) by the control device in consideration of the temperature that governs the inside of the gear device. The operating force required to engage the gear then increases with decreasing temperature. In this embodiment, the driving device 5 is a slipping clutch (friction clutch, slipping coupling, Rutschkupplung).
73 are provided. Such a slipping clutch 7
3 already in the drive casing or in the motor 57
It may be integrated into. In addition, the adjusting device has a number of sensors 129, 131 for detecting the adjusting movement introduced by the drive.

The second drive 5 has, at its free end, a device 133 for manual operation of the output element 5b of the second drive 5. This device 133 is provided with an uneven shape (groove, notch) of the motor shaft (motor shaft) 135.
This is achieved by providing an end with:
This end of the motor shaft 135 is connected to a closing element 139 in the motor casing of the second drive 5.
Covered by

Next, the function of this device will be described in detail.
If the vehicle remains geared and clutched (engaged), it is not possible to tow it off with the towing vehicle. If the electronic device fails, the driver cannot set the gear position. Furthermore, if the vehicle is equipped with an EKS and the clutch is engaged, the driver cannot switch gears without load. For this case, a device for manual operation is provided. Thus, the driver can manually enter the neutral position where the gearing is switched without load by opening the hood and removing the cover element by manual operation of the motor shaft 135. The neutral position, in this case the idling position, is identified by the operating force to be applied (ie, by the amount of force required during operation). However, if it is known which gear is engaged, an operating method for manually releasing (releasing) the gear may be given in advance.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of an adjusting device having a crank mechanism.

2 is a side view of the adjustment device shown in FIG. 1 along the section line II-II.

FIG. 3 is a view similar to FIG. 1 with a rack.

FIG. 4a is a view similar to FIG. 1 with a cam transmission; b is a schematic diagram of a cam having a plurality of flat portions.

FIG. 5 is a section line VV of the adjustment device shown in FIG. 4a;
FIG.

FIG. 6 is a view similar to FIG. 1 when a stroke magnet is provided as a driving device.

FIG. 7 is a view of a stroke magnet device for generating a rotating motion.

FIG. 8 is a side view as viewed from the right side of FIG. 7;

FIG. 9 is a view similar to FIG. 1, but with a compensating elastic body attached to the drive device.

FIG. 10 is a side view of the adjustment device shown in FIG. 9 along the section line XX.

FIG. 11a is a view of an adjustment device having a switching mechanism, only one adjustment drive and a locking element. b
FIG. 3 is a view taken along the line AA in FIG.

FIG. 12 is a side view of the lock element taken along section line XII-XII in FIG. 11a.

FIG. 13 is a view of a rotary lock element.

FIG. 14 is a view similar to FIG. 13, but having another structural configuration.

FIG. 15 is a diagram of an overload protection device having elastic elements.

FIG. 16 is a diagram of an overload protection device having an elastic element that can be prestressed.

FIG. 17 is a view of a segment gear having a stopper shock absorber as an overload protection device.

18 is a view of the overload protection device integrated with the segment gear, taken along line III-III of FIG. 19;

19 is a sectional view taken along line IV-IV in FIG.

FIG. 20 shows an adjusting device with a flange and an additional element.

[Explanation of symbols]

REFERENCE SIGNS LIST 1 adjustment device 2 adjustment drive device 3 first drive device 4 output device of first drive device 5 second drive device 5 b output element of second drive device 6 reduction gear 7 slide element 8 casing 9 output unit 10 selector Shaft 13 Transmission device element 14 Crank mechanism 15 Rack 16 Gear 17 Cam mechanism 18 Cam 19 Return spring 21 Stroke magnet 22 Follower section 23 Sleeve 24 Flat section 25 Void 26 Slit 27 Radial overhang 28 Radial slit 29 Gear 30 Turning lever 31 Segment gear 33 Axial overhang 35 Axial void 36 Compensation spring 37 Rest position 39 First pawl 41 Second pawl 43 First recess 45 Second recess 47 Rotation axis 49 Switching mechanism 50 Lock element 53 Lotus Gear 54 spindle 55 driven element 57 electric motor 59 switching drive 63 bearing 65 locking element 67 end of selector shaft 69 overload protection device 71 stopper buffering device 73 slipping clutch 75 elastic element 77 spring element 79 spring element 81 spring Element 83 Spring element 85 Slide element protrusion for spring element 77 87 Slide element protrusion for spring element 79 88 Stopper 89 Sleeve protrusion 91 Sleeve protrusion 93 Intermediate sleeve 95 Intermediate sleeve protrusion 97 Shut-off ring 99 Protrusion of rack 101 Inner diameter of sleeve 103 Space for spring elements 81, 83 105 Stopper 107 Internal segment car part 109 Space for accommodating internal segment car part 111 All Bearing 117 flange 119 additional elements 121 duct 123 sealing element 125 permits rotational speed sensor 127 Temperature sensor 129 Sensor 131 Sensor 133 manual adjusting device 135 motor shaft 137 groove 139 closing element

──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Lutz Leimbach Germany Day 97421 Sch Weinfurt Hardergasse 32 (72) Inventor Thomas Wilde Germany Day 97523 Sch Vanfeld Goethestrasse 11 (72) Inventor Erwin Bayer DE 97506 Grafenluheinfeld Lindenstraße 3 (72) Inventor Ingo Franz DE 97453 Meinberg Sonnenteller 3 (56) References JP 63-63637 (JP, A) JP-A-1-10545 (JP, A) JP-A-58-191354 (JP, A) JP-A-2-271164 (JP, A) JP-A-58-166155 (JP, A) JP-A-3-99271 (JP, U) Japanese Utility Model Showa 58-171533 (JP, U) Japanese Utility Model Showa 60-31537 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16H 61/28 F16H 35/00 F16H 61/34

Claims (24)

(57) [Claims] 1. Two movements having a plurality of drives, each of which can be transmitted to an output via a transmission mechanism, in particular for operating a transmission for a motor vehicle. A control device for the output part which is movable in a manner, wherein a movement of the output part in a first movement manner can be generated by a first drive and in a second movement manner by a second drive. The adjusting device in which the movement of the output of the first drive device (3) can be generated by a slide element (7).
And the slide element is axially fixed to the output (9), but is arranged so as to be able to move relative to the output in the circumferential direction, and the output is connected to the second output (9). as drive unit (5) does not rotate relative, but that it is connected movably in the axial direction, and the scan
Ride element (7) is mounted in sleeve (23)
Space where the sleeve extends in the sliding direction
(25), and the empty space is the slide element.
The projecting portion (27) of the
Adjustment device, characterized in that it is penetrated for connection with the force part (9) . 2. The connection between the second drive (5) and the output (9) is formed by a gear (29) rotatably mounted on the sleeve (23). 2. The adjusting device according to claim 1 , wherein the output part is arranged so as not to rotate relative to each other, but movably in the axial direction. 3. 3. The connection between said second drive (5) and said output (9) is formed by a segment gear (31) rotatably mounted on said sleeve (23),
2. The adjusting device according to claim 1 , wherein the output (9) is arranged so as not to rotate relative to the segment gear, but to be movable in the axial direction. 4. The first drive (3) is connected to the slide element (7) via a transmission element (13) which acts like a rotator and converts its movement into a linear movement. 2. The method of claim 1, wherein
The adjustment device according to any one of claims 3 to 3 . 5. The transmission element (13) is formed by a crank mechanism (14) pivotally connected to the slide element (7).
5. The adjusting device according to 4 . 6. The transmission element (13) is formed by a rack (15) connected to the slide element (7), the rack being an output element (4) of the first drive (3). 5. The adjusting device according to claim 4 , wherein the adjusting device is engaged with the adjusting device. 7. A cam mechanism (1) wherein said transmission element (13) is pivotally mounted on said slide element (7).
The adjusting device according to claim 4 , wherein the adjusting device is formed by 7). 8. The adjusting device according to claim 4 , wherein a return spring (19) is attached to the transmission element (13). 9. A stroke magnet (21) may be provided as the first driving device (3), and a driven part (22) of the stroke magnet is connected to the slide element (7). The adjusting device according to any one of claims 1 to 3 , characterized in that: 10. The second driving device (5) is provided with a compensating elastic body (36), and the compensating elastic body has a maximum prestress at a rest position (37) of the driving device (5). has, and characterized by enhanced by relaxing the torque supplied thereby in a state displaced from the rest position (37) by the drive device (5), any one of the preceding claims An adjustment device according to item 1. 11. An adjusting device for the operation of an output element for a transmission, in particular for a motor vehicle, which is provided with an adjusting drive, by means of which a gear is selected. In the adjusting device to be obtained, a switching mechanism (49) is attached to the adjustment driving device (2), and the switching mechanism is adapted to perform a switching process when a request for a movement mode different from the gear selection of the output section (9) is required. providing the ability to define the switch lanes to the adjusting drive (2), and said switching mechanism (49) comprises a locking element (50), the order the locking element of the lock of the output unit (9) The first recess (4
3) First pawl (3)
9) and a second recess (45) of said output without circumferential play for locking said output (9) against movement about its axis of rotation (47). Characterized by having a second pawl (41) that engages
That regulatory apparatus. 12. A plurality of recesses (43) are provided corresponding to the first claws (39), and each of the recesses (43) is connected after the output section (9). and wherein the determining the lanes of the gear device, according to claim 11
An adjustment device according to item 1. 13. The second pawl (41) of the locking element (50) remains in the second recess (45) independently of its switching position,
And to release the lock to a position as follows, in which the second recess (45) is inserted in the circumferential direction in order to guarantee the rotational movement of the output (9). 2. The method according to claim 1 , wherein the position can be moved to a position formed larger than (41).
2. The adjustment device according to 1 . 14. The second recess (45) is formed in the shape of a slit, and the second pawl (41) is provided with a rotation axis (22) of the output part (9) to allow the rotational movement. 4
The adjusting device according to claim 13 , wherein the adjusting device is positioned in the position of 7). 15. The adjusting drive (2) is connected to the output (9) via a helical gear (53), the driven element (55) of the helical gear having the output. 12. Adjustment device according to claim 11 , characterized in that it is fixedly connected to the part (9). 16.A plurality of driving devices, and the driving device
The movement of each is transmitted to the output unit via the transmission mechanism.
For operation of the transmission, especially for motor vehicles
The output unit can be moved by two movement methods.
Of the output in a first movement mode by one drive
Movement can be generated and the second By drive
Motion of the output in a second motion mode may be generated.
In the adjusting device, Said first drive device (3) comprises a slide element (7);
And the slide element is connected to the output
Axially fixed to part (9), but circumferentially
Are arranged so as to be capable of relative movement, and the output unit is
Not to rotate relative to the second drive (5), but
That they are movably connected in the axial direction,  At least one drive(35) is an overload protection device
(69) for driving the transmission element (7, 31).
The transmission of the dynamic movement is transmitted to this transmission element (7, 31).
Reach the correspondingly arranged stopper (88, 105)
The overload protection device must be
Place(3May be activated due to miscontrol in 5)
That,as well asThe overload protection device (69) is a slippin.
This is realized by using the clutch (73).
Sustained drive in the direction of movement where the clutch is dominant
Activated when hit by
thingCharacterized byAdjustment device. 17.A plurality of driving devices, and the driving device
The movement of each is transmitted to the output unit via the transmission mechanism.
For operation of the transmission, especially for motor vehicles
The output unit can be moved by two movement methods.
Of the output in a first movement mode by one drive
Movement can be generated and by the second drive
Motion of the output in a second motion mode may be generated.
In the adjusting device, Said first drive device (3) comprises a slide element (7);
And the slide element is connected to the output
Axially fixed to part (9), but circumferentially
Are arranged so as to be capable of relative movement, and the output unit is
Not to rotate relative to the second drive (5), but
That they are movably connected in the axial direction, At least one drive (3, 5) is an overload protection device;
(69) for driving the transmission element (7, 31).
The transmission of the dynamic movement is transmitted to this transmission element (7, 31)
Reach the correspondingly arranged stopper (88, 105)
The overload protection device must be
Can be activated by erroneous control in
And The overload protection device (69) is
Element (75), and the element is specified in advance.
When the possible displacement position is exceeded, the transmission element
Drive (7, 31) for damping the movement of the
(35) deforming against the force introduced from 5)
WhenCharacterized byAdjustment device. Characterized in that 18. An electric motor (57) can be used as a driving device, any claim 1 to 17
Adjustment device according to one paragraph or. 19. The adjusting device according to claim 1, which has a flange for coupling to a gear device, wherein said flange (117) enables an additional element (119) to enable another function. An adjustment device characterized in that it is used to receive 20. The apparatus according to claim 1, wherein the flange has at least one duct for injecting and discharging gear oil.
21), and the duct has a first additional element (1).
20. Adjusting device according to claim 19 , characterized in that it can be closed with a sealing element (123) as (19). 21. The flange (117) is provided with a separate element (121), such as a sensor (125), preferably a temperature sensor (127) and a speed sensor (125) for detecting the clutch shaft speed. 20. Adjustment device according to claim 19 , characterized in that it has a duct for: 22. At least one of said drives (3, 5) comprises a device (133) allowing manual adjustment of an output member (4, 5b) of said drive. Any one of claims 1 to 11, or claims
An adjustment device according to claim 16 or claim 17 . 23. The driving device (5) capable of driving the output member (5b) in a gear selection direction has a device (133) by which the motor shaft (135) of the driving device (5) is changed. 23. Adjustment arrangement according to claim 22 , characterized in that it is fixedly connected to the output element (5b) and can be driven manually. 24. The motor shaft (135) has an uneven shape (137) on the end side, and the uneven shape of the operating element to be used for manual driving is engaged with the uneven shape. 24. The adjustment device according to claim 23 , characterized in that it is characterized by the fact that