DE10316434A1 - Gearbox control unit comprises rear gear selection gate and perpendicular gates for changing into six forward gears - Google Patents

Abstract

The hand controlled gearbox comprises a selection gate (8) perpendicular to the gear change gates (10). In the upper gear change gate one can change into rear gear and in the following gates one can change into gears 1,2,3,4,5, and 6. A gear change pin can move into predetermined selection positions along a selection gate into central rotational position of the change lever. An Independent claim is included for a gear change control lever shaft.

Description

The invention relates to an actuating unit for a manual transmission and a Shift shaft.

In motor vehicles, especially passenger cars, are increasingly finding automated manual transmission input. This is usually done by Hand actuating the gearshift transmission via the shift lever replaced by an actuating unit that a shift shaft in the same way operated as done by hand. The contained in the actuator Motors are controlled by a control unit depending on the operating states of the Vehicle, for example the speed, the actuation of a Throttle control and the respective engine speed actuated. With such automated Manual transmissions not only improve driving comfort. It will be additional the consumption is reduced because it increases in a long course is driven economically.

The invention has for its object a compact Actuating unit for a manual transmission to create, which is advantageous as complete pre-assembled unit can be flanged to a manual transmission.

The above task is done with an actuator for one Manual transmission solved, which contains a rotatable about an axis and along the axis Slidable shift shaft with at least one shift pin, which is in a middle Rotational position of the selector shaft along a selection lane in predetermined Selector positions are displaceable, from which it turns when the selector shaft rotates in switching elements provided on the manual transmission for switching gears of the Gear engages, a switching unit by means of which the selector shaft in axial sliding rotary engagement with a switch motor, and a selection unit, by means of which the selector shaft rotates axially with a selector motor stands.

The sleep unit advantageously has one of the switch motor rotatably driven threaded spindle, the rotation of which in a longitudinal movement Spindle nut is converted, which spindle nut across one across to it linear mobility with a toothing in the axial direction of the Gearshift shaft meshing is engaged, so that the gearshift shaft axially displaceable relative to the spindle nut and by movement of the Spindle nut is rotatable.

For certain applications, it is useful to use the switch motor and the spindle nut a reduction or transmission gear to arrange.

The selection unit advantageously has one that is rotatable on the selector shaft, but axially non-displaceably mounted toothed segment ring, the one with predetermined Includes radial segment toothing into which one of the Selector motor engages gears that can be driven by rotation.

To guide the toothed segment ring advantageously projects on a housing the actuating unit rigidly attached guide part in a groove of Segment ring.

The guide member is advantageously a sleeve, the one with a Circumferential toothing formed by a selectable motor driven pinion outsourced.

In a preferred embodiment of the invention Actuating unit has the toothed segment ring for storage in a housing Actuator a ball orbit, the slope of which in areas those arranged in the ball orbit on a housing-fixed Bearing inner surface is equal to the pitch of the segment toothing.

The ball orbit is advantageously formed in a plastic ring which in a shoulder of the toothed segment ring is arranged.

In an advantageous development of the invention Actuating unit is rigidly connected to the shift shaft of a hub and between the hub and a rotational engagement between the shift motor and the shift shaft mediating shift pinion are arranged springs that the shift pinion in a Preload predetermined rotational position relative to the hub.

Cams which engage are advantageously formed on the shift pinion with preloaded, approximately parallel to the axis of the selector shaft Are cantilevers that are accommodated in the hub.

An outer lateral surface of the hub axially removed from the shift pinion forms advantageously a bearing surface for the toothed segment ring.

The control shaft is preferably a plastic injection molded part, the mechanical areas subject to higher stresses are formed from sheet metal parts which, when Injection molding is inserted into the mold or on the finished plastic injection molded part are attached.

Advantageously, there are axial pins on the selector shaft arranged and is with a housing of the actuating unit Switch shaft surrounding ring disc rigidly connected, which has a cutout, through which the alley pins with an axial displacement of the neutral Switch position located shift shaft and the at a Shift gate corresponding axial position of the shift shaft and rotation the selector shaft for switching a gear between two neighboring ones Gassenstifte is included.

Advantageously, the washer through the face of a rigid with the Housing of the actuating unit connected, pot-like cylinder formed, on the inner peripheral surface of the toothed segment ring is mounted.

The inner circumferential surface of the washer is advantageously used for Guiding the selector shaft.

The extraordinarily compact actuating unit according to the invention can be used for all types of manual gearboxes of a component are switchable, for preselecting gears in one direction is movable and for shifting the gears in one direction vertical direction is movable.

A selector shaft, as used in particular in a Actuator according to the invention is suitable, is advantageously from a Plastic injection molded part assembled with a sheet metal part. Advantageous is also a design of the selector shaft such that a circular cylindrical Sheet metal part is connected to the plastic injection molded part.

The invention is described below with the aid of schematic drawings for example and explained in more detail.

They represent:

Fig. 1 shows a typical circuit diagram of a manual transmission,

Fig. 2 is a cross sectional view of a flange of a manual transmission,

Fig. 3 is an overall view of an actuator unit according to the invention,

Fig. 4 is a diagram of a switching unit,

Fig. 5 is a partial cross section through the actuator of FIG. 3, taken along the line VV,

Fig. 6 is a diagram of a selecting unit,

Fig. 7 shows a partial longitudinal section through the operating unit according to Fig. 3,

Fig. 8 is a partial cross section through the actuator of FIG. 3, taken along the line VIII-VIII,

Fig. 9 is a side view of a toothed segment ring,

Fig. 10 is a schematic for explaining a shifting elasticity,

Fig. 11 is a side view of a part of the switching shaft,

Fig. 12 is a perspective view of a hub,

Fig. 13 is a side view of a part of the shift shaft with befindlichem it, segment ring,

Fig. 14 is a side perspective view of a portion of the switching shaft similar to FIG. 13, but by 180 ° reversed,

Fig. 15 is a diagram for explaining functional elements of the shift shaft,

Fig. 16 is a perspective view of the shift shaft,

Fig. 17 to 20 are sectional views of the switching shaft according to the line XX in Fig. 3 different for illustrating four embodiments,

Fig. 21 is a diagram for explaining the streets guide the selector shaft,

Fig. 22 is a perspective view of a portion of the switching shaft for explaining the lanes guide and

Fig. 23 is an end view of the arrangement according to FIG. 22, rotated by about 180 °.

For a better understanding of the invention, some are first Basic relationships in a known manual transmission explained.

Fig. 1 shows a typical shift pattern of a manual transmission, with a selector gate 8 , from which shift gates 10 depart at right angles, the reverse gear can be shifted in the uppermost shift gate and gears 1, 2, 3 and 4 as well as in the shift gates which follow down 5 and 6 can be switched. A shift pin or actuator must be movable in such a way that it follows the shift pattern as is known per se in actuating devices for manual transmissions.

The distance between the switching gates can only be 7.5 mm, for example amount and the distance between two switching positions within one Shift gate can be, for example, only 20 mm on the shift mouthpiece.

Fig. 2 shows a gear flange 12 of a gear housing, not shown, within which (according to Fig. 2 down) shift jaws 14 and 16 are arranged, which must be moved to the left or right to shift a gear according to Fig. 2. The dotted line denotes the axis of a selector shaft which extends from an actuating unit to be flange-mounted on the flange 12 through the gear housing and the free end of which is supported at 18 on the gear housing. The inner diameter D of the flange is, for example, 64 mm; for the operating unit is shown in FIG. 2 above the flange 12 a space of, for example, only a maximum of 100 mm.

Fig. 3 shows a top view of an inventive actuating unit which can be flanged to the gearbox 12th The actuation unit has a housing 20 to which a switch motor 22 and a selector motor 24 are attached, which interact in the manner explained below with a switch shaft 26 , the free end 28 of which in the installed state at 18 ( FIG. 2) on the transmission housing (not shown) ) is stored.

Also visible in FIG. 3 are shift pins 30 rigidly connected to the shift shaft 26 , one of which interacts with the shift mouth 14 or the other with the shift mouth 16 when the shift shaft 26 is in the corresponding axial position.

FIG. 4 schematically explains the structure of a switching unit 31 contained in the actuating unit, by means of which the switching shaft 26 can be rotated about its longitudinal axis.

The switching motor 22 , for example an electric motor, drives a threaded spindle 32 , the rotation of which is transmitted into a translation of a spindle nut 34 which is displaceably guided on the housing (not shown in FIG. 4). The translation of the spindle nut 34 is transmitted via a toothing 36 attached to the spindle nut 34 and extending transversely to its displaceability to an external toothing 38 rigidly connected to the selector shaft 26 and extending along the selector shaft 26 , so that the translational movement of the spindle nut 34 in a rotation of the shift shaft 26 is converted, the shift shaft 26 being displaceable in its axial direction. In this way, the shift pin 30 can be rotated about the axis of the shift shaft 26 , so that the shift jaws 14 can be shifted to the left or right.

The pitch of the toothing or the thread of the threaded spindle 32 can be so small that self-locking occurs. This can be avoided by increasing the slope and compensating for this higher gear ratio of the spindle drive by means of a reduction gear 40 between the switching motor 22 and the threaded spindle 32 . In the example shown, the reduction gear 40 is a planetary gear. It is understood that the reduction gear can also be a conventional spur gear.

Fig. 5 illustrates the structure of the switching unit in more detail:
A drive shaft 42 of the shaft motor 22 is positively connected to an adapter 44 . The adapter 44 has an external toothing which, as a sun gear, engages with planet gears 46 . The planet gears 46 are designed as sintered parts, the porous base material of which is interspersed with plastic or graphite-containing substances in order to create slide bearing properties in their core bore. This makes it possible to mount the planet gears 46 directly on carrier pins 48 which are inserted into a carrier cage 50 until they rest on a collar 52 . The cylindrical protrusion on the side opposite the collar 52 is compressed, so that a bead 54 is formed which serves to secure the carrier pin 48 with respect to the carrier cage 50 . Alternatively, a bead could be swaged on both sides of the carrier pin 48 .

The carrier cage 50 is advantageously designed as a plastic part and z. B. positively connected by serration to the threaded spindle 32 . The carrier cage 50 is floating in its axial position. As a result, it can run against a surface 56 on one side and a surface 58 on the other side. In this case, the plastic acts like an axial plain bearing.

• - Die Führungslänge A kann bei Herstellung relativ ungenau erzeugt werden. Dadurch ergibt sich nach der Montage in der Gehäusebohrung 64 ein axialer Überstand, der durch Heißprägen auf das Höhenniveau der Flanschfläche 66 eingestellt wird. Dabei dient ein Freiraum 68 als Reservoir, um das verdrängte Volumen aufzunehmen.
• - Die Darstellung a zeigt die Ausführung des Hohlrades 60, wie sie sich nach der Herstellung ergibt. Unten erkennt man eine Geometrieveränderung, die anhand der Montage eines Lagers 70 erzeugt wird. Durch axiales Heißprägen wird ein Wulst angestaucht, der das Lager 70 axial sichert (Darstellung b).
• - Die genannten Verfahren des Heißprägens haben den Vorteil, dass auf einen Sicherungsring für das Lager 70 verzichtet werden kann. Außerdem wird eine hohe Positionsgenauigkeit an der Flanschfläche 66 erzielt, obwohl das Maß A relativ ungenau hergestellt werden kann.
• - Vorteilhaft ist weiterhin, dass das Lager 70 auf die Gewindespindel 32 aufgesteckt und beidseitig durch einen rollierten Wulst in einer festen Position gehalten wird. Die Spindelgeometrie selbst ist ein- oder mehrgängig ausgeführt und wird im Stirnschnitt durch Evolventen beschrieben. Ein Durchmesser 72 dient als Loslagerfläche und stützt sich im Gehäuse 20 ab. Zwischen dem Gehäuse 20 und dem Durchmesser 72 ist ein Gleitlager 74 eingepresst.

The planet gears 46 are in engagement with a ring gear 60 which is fixedly connected to the housing 20 via an anti-rotation device 62 . The design of the ring gear 60 as a plastic part offers the following options for assembly:

• - The guide length A can be generated relatively inaccurately during manufacture. This results in an axial protrusion after assembly in the housing bore 64 , which is adjusted to the height of the flange surface 66 by hot stamping. A free space 68 serves as a reservoir in order to accommodate the displaced volume.
• - The representation a shows the design of the ring gear 60 , as it results after manufacture. A change in geometry can be seen below, which is generated on the basis of the mounting of a bearing 70 . A bead is compressed by hot axial stamping, which axially secures the bearing 70 (illustration b).
• - The above-mentioned methods of hot stamping have the advantage that a retaining ring for the bearing 70 can be dispensed with. In addition, a high positional accuracy is achieved on the flange surface 66 , although the dimension A can be manufactured relatively imprecisely.
• It is also advantageous that the bearing 70 is plugged onto the threaded spindle 32 and is held in a fixed position on both sides by a rolled bead. The spindle geometry itself has one or more threads and is described in the face cut by involutes. A diameter 72 serves as a floating bearing surface and is supported in the housing 20 . A sliding bearing 74 is pressed in between the housing 20 and the diameter 72 .

The spindle nut 34 is a plastic part that has the toothing 36 ( FIG. 4) arranged on the side. On the opposite side, two grooves 76 ( FIG. 7) are embedded, in which two pins 78 guide the spindle nut 34 and serve to prevent rotation. The pins 78 are firmly pressed into the housing 20 , advantageously at right angles to the axis of rotation of the selector shaft 26 and the spindle nut 34 . The surface 80 ( FIG. 7) is at a short distance from the housing bore 82 under normal operating conditions. Under impact load, a force component from the toothing 36 forces the threaded spindle 32 to bend. This deflection is minimized by the contact of the surface 80 with the housing bore 82 and thus prevents twisting.

The shift pinion 84 , which is connected in a rotationally fixed and rigid manner to the shift shaft 26 and is provided with the axially extending radial toothing, transmits the translated torque to the shift shaft 26 . The rolling diameter advantageously corresponds to the effective force application diameter on the switching pin 30 .

The diagram of the selection unit 85 is explained below with reference to FIG. 6, with which a rotation initiated by the selection motor 24 is circulated into an axial displacement of the selector shaft 26 .

Starting from the interface requirements in the transmission, the shift pin 30 must ensure that any shift gate position is achieved as a pure lifting movement within the neutral position of the shift forks 14 or 16 . This requirement is known from manual actuators. Specifically for use in an automated manual transmission, there is still the requirement that the aisle height must be detected within a shift lane by means of short travel distances. To do this, a pin 86 is pushed against the fixed aisle boundary with a force of approximately 500 N.

The input variables are the angle of rotation and the torque of the selector motor 24 . The output variables are the stroke movement and the force at switching pin 30 .

The demands to be made on the selection unit are achieved using a segment toothing 88 which runs radially at a constant pitch angle and with which the selector motor 24 designed as an electric motor engages via a spur gear toothing 90 . The segment toothing 88 is formed on a toothed segment ring 92 , which is freely movable or rotatable in the circumferential direction, but firmly positioned in the axial direction, on the selector shaft 26 . A pin 94 fastened in the housing 20 serves to guide and support the toothed segment ring 90 when the torque from the selector motor 24 is introduced into the segmented toothing 88 via the spur toothing 90 . The guide geometry 96 and the segment toothing 88 follow the same circumferential pitch. The angle of rotation is converted into the shift shaft 26 in a stroke movement. The torque to force ratio on the selector shaft 26 results from the ratio of the angle of rotation on the selector motor 24 to the pitch on the segment toothing 88 . The structure of the selection unit is explained in more detail below with reference to FIGS . 7 to 9.

The drive shaft 98 of the selector motor 24 is positively connected (corresponding to the spur gear toothing of FIG. 6) to an adapter 100 which has an external toothing 102 which engages with the segment toothing 88 . A sleeve 104 is firmly pressed into the housing 20 and forms a slide bearing for the adapter 100 forming a drive pinion. A front end of the sleeve 104 extends into a groove 106 of a further sleeve 108 which is rigidly connected to the segment toothing 88 and together forms the toothed segment ring 92 ( FIG. 6). In this way, the sleeve 104 supports the selection force acting on the selector shaft 26 and forms the pin 94 of FIG. 6.

As can be seen from FIG. 9, the segment toothing 88 is formed on a “side wall” of the groove 106 , offset radially inward.

As can be seen from FIG. 7, a pot-like cylinder 110 is pressed into the housing 20 with its outer diameter. The sleeve 104 ( FIG. 8) is inserted in a bore 112 and thus secures the axial position of the cylinder 110 in the housing 20 . The inner diameter of the cylinder 110 has a smooth, drawn sheet metal surface and serves as a bearing surface for supporting a recirculating ball guide 114 . This requires a surface hardness of around 58 to 64 HRC on the inside diameter of the cylinder. The recirculating ball guide 114 is sprayed onto a shoulder 118 of the sleeve 108 as a plastic ring 116 , so that the outer diameter of the plastic layer or of the plastic ring 116 and that of the sleeve 108 result in a flush surface. A ball orbit 120 is embedded in the plastic ring 116 and runs in load-bearing areas 122 at the same pitch as the segment toothing 88 . In these areas, the ball rolls radially on the inside of the shoulder 118 and radially on the outside on the inside diameter of the cylinder 110 . Both treads have smooth metallic surfaces to support static and dynamic bearing forces. Return zones 124 are arranged between the load-bearing regions 122 , the angle of inclination of which is chosen to be correspondingly flat, so that the balls can overflow freely. The balls do not support in the return zones, ie the support surface lying radially on the inside has a smaller diameter than in the supporting areas 122 .

It should also be pointed out that a bottom flange 126 ( FIG. 7) of the sleeve 108 is freely movable in the circumferential direction and in the axial direction to a fixed position between a collar 126 formed on the selector shaft 26 and a switching elastic unit 128 firmly connected to the selector shaft 26 , which is explained below, is clamped.

In this way, the toothed segment ring 92 composed of the segment toothing 88 and the sleeve 108 can be rotated and is axially fixed to the selector shaft 26 .

The selector shaft 26 can thus be axially displaced by actuating the selector motor 24 and rotated independently of it by actuating the selector motor 22 about its axis.

The structure and function of the switching elasticity unit 128 , which corresponds functionally to the prior art, is explained below with reference to FIG. 10. The shift elasticity unit 128 is located between the shift pinion 84 formed with the axially extending toothing 38 and the shift shaft 26 . A hub 130 is fixedly connected to the selector shaft 26 and offers a receptacle for prestressing springs 132 . The pinion 84 introduces the flow of force via driver webs 134 into the prestressed springs 132 . If there is a resistance at switching pin 130 , the springs are compressed in accordance with their characteristic curve. At the same time, flanks 136 are rotated via the webs 134 until stops 138 are reached. Then there is a positive connection between the shift shaft 26 and the shift pinion 84 because the stops 138 are firmly connected to the shift shaft 26 . From this point on, energy is no longer stored in the springs 132 .

The structure of the switching elastic unit is explained in more detail below with reference to FIGS. 11 to 14:
The entrainment webs are located on the shifting pinion 84 134 (Fig. 10) forming cam 140 engaged with the springs 132 of FIG. 10 forming spring beams 142 are provided. The switching pinion 84 ideally consists of sintered material. Alternatively, reinforced plastic is also possible. The hub 130 serves to receive and preload the spring bars 142 . In Fig. 12 the recording window 144 are illustrated. In its lower region, the receiving windows 144 are divided into two segments 146 in order to ensure that the spring bars 142 are firmly clamped in place. Flanks 148 form a support for the spring bars 142, which tend to spread. Characterized the spring beams are biased to a particular level of force 142nd The spring force is supported on the selector shaft 26 by means of driving teeth 150 . As an alternative, the hub 130 can also be designed as a component of the selector shaft 26 in the form of an injection-molded plastic part.

The outer surface 152 serves as a sliding bearing surface to support the rotation of the shift shaft 26 when shifting. The inner diameter 154 of the toothed segment ring 90 ( FIG. 13), which is the transmission element for the selection movement, acts as a counter bearing surface. It is therefore advantageous to manufacture the hub 130 from a material with slide bearing properties, for example as a plastic injection molded part.

The cantilevers 142 ( FIG. 11) are designed as beams that are firmly clamped on one side. Ideally, individual bars are connected to one another via webs 156 . It is imperative that a web 156 is firmly fixed between the segment 158 ( FIG. 12) and the switching shaft surface 160 .

Fig. 14 shows a segment 162 that realizes the limit for the angle of rotation within the spring characteristic. Gaps 164 extend through the cams 140 ( FIG. 11), which correspond to the surface 166 that form the prestressed spring bars 142 . In this way, an angle of rotation for clamping the spring bars 142 within the dimension 168 can be realized. If the cams 140 bear against the surfaces 168 after the rotation, the torque is positively transmitted to the selector shaft 26 via the driver teeth 150 .

The segment 162 is a separate sintered component and can be designed as part of the control shaft 26 .

Overall, the described switching elasticity unit thus achieves limited rotatability between the switching pinion 84 and the hub 130 or the switching shaft 26 which is fixedly connected to the hub.

Basic functions of the selector shaft with regard to the functionality of switching and locking with and without active interlock, as are known per se from the prior art, are explained below with reference to FIG. 15. The lower and upper limit for the dialing path across all lanes is defined via the switching pin 30 , a switching shaft shoulder 170 and a stop 172 fixed to the housing. The selector shaft 26 can move within the dimension 174 specified by the selector shaft shoulder 170 and selector pin 30 .

The structure of the shift shaft 26 is explained in more detail with reference to FIGS. 16 to 20.

The illustrated control shaft 26 advantageously consists of at least one plastic injection molded part 176 . Surfaces that are subjected to higher functional loads, such as the shift pins 30 , the surfaces 178 and the edges 180 that come into contact with the shift forks or guides ( FIG. 2), are preferably made of metal with a good surface quality. The central area 182 can be filled to increase the torsional rigidity. The area 182 and the blocking surfaces 184 and 186 are advantageously ribbed. This increases rigidity and reduces shrinkage during injection molding. The outer surface of the front end 28 of the selector shaft is used for mounting on the gear housing. This area, like other areas, can be inserted as a tube or rod 188 made of steel during injection molding. Depending on the length of the rod material, the anchoring may be in the vicinity of the lower or upper switching pin 30 .

Figs. 17 to 20 show in cross section four variant embodiments of the higher stressed areas switching pin 30 and surface 178. The basic principle is to use drawn or stamped metal sheets which are inserted into the mold as segments during injection molding or are applied, for example clipped, onto the injection-molded base body of the selector shaft.

Fig. 17 shows a variant in which a sheet metal segment 189 is produced integrally by deformation and is inserted into the injection mold. In areas B and C, window-like openings are provided which lead to anchoring between the base body 176 of the bearing shaft 26 and the sheet metal segment 189 .

In the embodiment according to FIG. 18, the sheet metal segment 190 is produced from two individual parts D, which are connected by laser welding 192 . The connection to the base body 176 takes place as in FIG. 17.

In the embodiment according to FIG. 19, the sheet segment 189 produced as a whole is clipped onto the injection-molded plastic body 176 in its recess E.

In the embodiment of Fig. 20, two symmetrical sheet-metal parts are inserted in longitudinally direction of the shift shaft 26, formed on the plastic base body grooves G 194th

The design of the selector shaft 26 as an injection molded part brings a considerable reduction in weight and manufacturing costs compared to a design made of steel. The ribbing and the formation of certain surfaces and edges from sheet metal enable the same stiffness and strength ratios and durability properties to be achieved as with a conventional selector shaft made of steel.

For the shifting precision, a clean guidance of the shifting shaft is necessary in such a way that the shifting pin 30 can be moved safely into the individual shifting lanes in which the shifting forks are arranged. Are shown in Fig for this guide. 21 schematically shows a cross section in the upper half a schematic plan view and in the lower half, arranged on the switching shaft 26 pins 196 in mutual axial distance. The number of pins is 1 greater than the number of possible shift gates for the transmission. The center distance between two adjacent pins 196 corresponds exactly to the distance between two adjacent switching gates 198 .

When the selector shaft 26 rotates, two adjacent pins 196 enclose an annular disk 200 or receive the annular disk 200 between them, which is rigidly connected to the transmission housing 20 . As a result, the movement in the axial direction is blocked for the shift shaft 26 and it is ensured that the shift pin is only in a shift gate 198 .

The described functional unit of the aisle guide is explained in more detail with reference to FIGS . 22 and 23.

Cylindrical pins 196 are pressed or injected into the shift shaft 26 . The pins are advantageously made of metal. The axis of the pins 196 intersects the axis of the shift shaft 26 so that both have the same center of rotation.

A cylindrical housing part 202 is rigidly connected to the housing 20 of the actuating unit or is formed in one piece therewith. The end face of the cylindrical housing part 202 shown forms a total of the annular disk 200 , which has a cutout 204 through which the pins 196 can move when the control shaft 26 is in a predetermined rotational position range. The inside diameter of the housing part 202 or the ring disk 200 is designed such that it guides the selector shaft.

The width of the cutout 204 is at least as large as the diameter of the pins 196 . When the selector shaft 26 is rotated, two adjacent pins 196 receive the washer 200 between them, so that the selector shaft 26 cannot be axially displaced.

The width or the angular range of the cutout 204 in connection with a so-called active interlock can be such that independent of the. Shift gate level, in which the shift finger is located, is designed by rotating within the angular range of the cutout 204 each gear engaged. Is the angular range of the cutout 204 of Fig. 22 symmetrically to the neutral position of the shift finger between two shift slots.

Gem. Fig. 23 may be the halved α in Fig. 22 unregistered pivot angle 2 and with respect to FIG. 22 or unbalanced in a half of the section 204 of FIG. 23 be disposed. The angle α ( FIG. 23) borders on one side to the neutral position and is equal to the swivel angle plus the diameter of the pins 196 . The design of the cutout 204 ( FIG. 23) which is asymmetrical with respect to the neutral position has the advantage for the control of the selector shaft 26 that the neutral center position can be detected as a stop via the pins 196 .

The described design of the aisle guide has the advantage that the functionally existing component is also used (the cylindrical housing part 202 is advantageously the cylinder 110 described with reference to FIG. 7). The available space is optimally used. Only a minimum of components is required.

It is understood that the described embodiment in many Way can be changed and described features individually or in different combinations can be present. The applicant retains protect themselves from individual features even without combining them with others To claim features, for example a method for Production of the control shaft designed as a composite part.

The claims filed with the application are Proposed wording without prejudice for obtaining further patent protection. The The applicant reserves the right to add more, so far only in the description and / or To claim drawings disclosed combination of features.

Relationships used in subclaims point to the others Training the subject of the main claim by the features of respective subclaim; they are not considered a waiver of achieving one independent, objective protection for the combinations of features of to understand related subclaims.

Since the subjects of the subclaims with regard to the prior art reserves the right to make its own and independent inventions on the priority day Applicant before becoming the subject of independent claims or To make divisional declarations. You can continue to be self-employed Inventions contain one of the objects of the previous Have independent claims independent design.

The exemplary embodiments are not intended to limit the invention understand. Rather, there are numerous within the scope of the present disclosure Changes and modifications possible, especially such variants, elements and combinations and / or materials, for example by combination or modification of individual in connection with that in general Description and embodiments as well as the claims described and in features or elements contained in the drawings or Process steps for the person skilled in the art with regard to solving the problem can be found and through combinable features to a new item or new ones Lead process steps or process step sequences, also insofar as they Test and work procedures concern.

Claims (17)

1. Actuating unit for a manual transmission, containing
a shift shaft rotatable about an axis and displaceable along the axis with at least one shift pin, which in a middle rotational position of the shift shaft is displaceable along a selection gate in predetermined selection positions, from which it turns when the shift shaft is rotated into shift elements provided on the transmission for shifting gears the gear engages,
a switching unit by means of which the switching shaft is in axially displaceable rotary engagement with a switching motor, and
a selection unit, by means of which the selector shaft is in rotational axial engagement with a selector motor. 2. Actuator according to claim 1, wherein the switching unit is one of the switch motor has a rotatably drivable threaded spindle Rotation is converted into a longitudinal movement of a spindle nut, which spindle nut has a transverse to its linear movability running teeth with an axial in the switching times extending toothing is engaged, so that the shift shaft relative to the Spindle nut can be moved axially and by moving the spindle nut is rotatable. 3. Actuating unit according to claim 2, wherein between the switching motor and the threaded spindle a reduction or transmission gear is arranged. 4. Actuating unit according to one of claims 1 to 3, wherein the Selection unit one rotatable on the selector shaft, but axially immovable stored toothed segment ring containing one with a predetermined pitch has radial radial toothing, into which one of the Selector motor engages gears that can be driven by rotation. 5. Actuator according to claim 4, wherein for guiding the Tooth segment ring rigidly attached to a housing of the actuating unit Guide component engages in a groove of the toothed segment ring. 6. Actuating unit according to claim 5, wherein the guide member Is sleeve, which is formed with a circumferential toothing, of which Selector motor drivable pinion bearings. 7. Actuating unit according to one of claims 4 to 6, wherein the Tooth segment ring for its storage in a housing of the actuating unit has a ball orbit, the slope of which in areas where in the orbiting balls arranged on a housing-fixed Bearing inner surface is equal to the pitch of the segment toothing. 8. Actuator according to claim 7, wherein the ball orbit in one Plastic ring is formed in a shoulder of the toothed segment ring is arranged. 9. Actuating unit according to one of claims 1 to 8, wherein a hub is rigidly connected to the shift shaft and between the hub and one the rotational engagement between the switch motor and the switch shaft mediating shift pinion springs are arranged which the shift pinion in a Preload predetermined rotational position relative to the hub. 10. Actuating unit according to claim 9, wherein cams on the shift pinion are formed, which engage with biased, approximately parallel to the axis of the selector shaft are spring bars that run in the hub are included. 11. Actuator according to claim 4 and 10, wherein an outer Shell surface of the hub axially removed from the shift pinion a bearing surface for forms the toothed segment ring. 12. Actuating unit according to one of claims 1 to 11, wherein the Control shaft contains a plastic injection molded part, the mechanically higher stressed areas are formed from sheet metal parts during injection molding are inserted into the mold or on the finished plastic injection molded part are attached. 13. Actuating unit according to one of claims 1 to 12, wherein on the Shift shaft pins are arranged at an axial distance and with a Housing of the actuating unit surrounding the selector shaft Annular disc is rigidly connected, which annular disc has a cutout, through which the pins in an axial displacement of the neutral Switch position located shift shaft and the at a a shift gate corresponding axial position of the shift shaft and Rotation of the selector shaft to shift one gear between two Adjacent alley pins are added between them. 14. Actuator according to claim 4 and 13, wherein the washer through the face of a rigid with the housing of the actuator connected, pot-like cylinder is formed on the inner peripheral surface the toothed segment ring is supported. 15. Actuator according to claim 13 or 14, wherein the inner Circumferential surface of the washer serves to guide the selector shaft. 16. switching shaft, in particular for an actuating unit according to claim 1, which control shaft from at least one plastic injection molded part and a metal sheet molding is composed. 17. Switching shaft according to claim 16, wherein at least one circular cylindrical Metal part is connected to the plastic injection molded part.