Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H61/26—Generation or transmission of movements for final actuating mechanisms
  • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
  • F16H61/32—Electric motors actuators or related electrical control means therefor
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H57/00—General details of gearing
  • F16H57/04—Features relating to lubrication or cooling or heating
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
  • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
  • F16H63/30—Constructional features of the final output mechanisms
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H61/24—Providing feel, e.g. to enable selection
  • F16H2061/242—Mechanical shift gates or similar guiding means during selection and shifting
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H61/26—Generation or transmission of movements for final actuating mechanisms
  • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
  • F16H2061/2869—Cam or crank gearing
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H61/26—Generation or transmission of movements for final actuating mechanisms
  • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
  • F16H2061/2884—Screw-nut devices
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
  • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
  • F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
  • F16H63/20—Multiple final output mechanisms being moved by a single common final actuating mechanism with preselection and subsequent movement of each final output mechanism by movement of the final actuating mechanism in two different ways, e.g. guided by a shift gate
  • F16H2063/208—Multiple final output mechanisms being moved by a single common final actuating mechanism with preselection and subsequent movement of each final output mechanism by movement of the final actuating mechanism in two different ways, e.g. guided by a shift gate using two or more selecting fingers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
  • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
  • F16H63/30—Constructional features of the final output mechanisms
  • F16H2063/3076—Selector shaft assembly, e.g. supporting, assembly or manufacturing of selector or shift shafts; Special details thereof
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
  • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
  • F16H63/30—Constructional features of the final output mechanisms
  • F16H2063/3083—Shift finger arrangements, e.g. shape or attachment of shift fingers

Definitions

• the invention relates to an actuating unit for a manual transmission and a selector shaft.
• Automated manual transmissions are increasingly being used in motor vehicles, in particular passenger cars.
• the operation of the gear shift transmission which is normally carried out manually by means of the shift lever is replaced by an actuation unit which actuates a shift shaft in the same way as is done by hand.
• the motors contained in the actuation unit are actuated by a control unit as a function of the operating states of the vehicle, for example the speed, the actuation of a throttle lever and the respective engine speed.
• Such automated manual transmissions not only improve driving comfort. Consumption is also reduced because more driving in a long gear is more economical.
• the object of the invention is to create a compact actuating unit for a manual transmission, which can advantageously be flanged to a manual transmission as a completely preassembled unit.
• an actuating unit for a manual transmission which contains a shift shaft that can be rotated about an axis and displaceable along the axis, with at least one shift pin that can be shifted in a middle rotational position of the shift shaft along a selector gate into predetermined selector positions, from which it can be moved when the selector shaft rotates, engages in shift elements provided on the manual transmission for shifting gears of the transmission, a shift unit by means of which the selector shaft is in axially displaceable rotary engagement with a shift motor, and a selector unit by means of which the shift shaft is rotatable in axial engagement with a selector motor stands.
• the switching unit has a threaded spindle which can be driven by the switching motor and whose rotation converts into a longitudinal movement of a spindle nut. is converted which spindle nut is in engagement with a toothing extending in the axial direction of the selector shaft via a toothing extending transversely to its linear movability, so that the selector shaft is axially displaceable relative to the spindle nut and rotatable by movement of the spindle nut.
• the selection unit advantageously has a toothed segment ring which is rotatably but axially non-displaceably mounted on the selector shaft and which has radial segment toothing which runs with a predetermined pitch and into which a toothing which can be driven by the selector motor engages.
• a guide part rigidly fastened to a housing of the actuating unit advantageously projects into a groove of the toothed segment ring.
• the guide component is advantageously a sleeve which supports a pinion which is formed with peripheral toothing and can be driven in rotation by a selector motor.
• the toothed segment ring has a ball orbit for mounting in a housing of the actuating unit, the pitch of which is equal to the pitch of the segment toothing in regions in which balls arranged in the ball orbit bear against an inner surface fixed to the housing.
• the ball orbit is advantageously formed in a plastic ring which is arranged in a shoulder of the toothed segment ring.
• a hub is rigidly connected to the shift shaft and springs are arranged between the hub and a rotary engagement between the shift motor and the shift shaft, which bias the shift pinion in a predetermined rotational position relative to the hub.
• Cams are advantageously formed on the shift pinion, which are in engagement with prestressed spring bars, which run approximately parallel to the axis of the shift shaft and are received in the hub.
• An outer lateral surface of the hub axially removed from the shift pinion advantageously forms a bearing surface for the toothed segment ring.
• the control shaft is preferably a plastic injection-molded part, the regions of which are subjected to higher mechanical stresses are formed from sheet metal parts which are inserted into the mold during injection molding or are attached to the finished plastic injection-molded part.
• alley pins are arranged on the selector shaft at an axial distance and a ring disk surrounding the selector shaft is rigidly connected to a housing of the actuating unit, which has a cutout through which the alley pins pass when the selector shaft in the neutral switch position is axially displaced and which at one a shift gate corresponding axial position of the shift shaft and rotation of the shift shaft for switching a gear between two adjacent alley pins is recorded.
• the annular disk is advantageously formed by the end face of a pot-like cylinder rigidly connected to the housing of the actuating unit, on the inner peripheral surface of which the toothed segment ring is mounted.
• the inner circumferential surface of the annular disc advantageously serves to guide the selector shaft.
• the extraordinarily compact actuating unit according to the invention can be used for all types of gear shift transmissions which can be shifted by means of a component which can be moved in one direction for preselecting gears and can be moved in a direction perpendicular to one direction for shifting the gears.
• Actuating unit is suitable, is advantageously composed of a plastic injection molded part with a sheet metal molded part. It is also advantageous to design the selector shaft in such a way that a circular cylindrical sheet metal part is connected to the plastic injection molded part.
• FIG. 3 shows an overall view of an actuating unit according to the invention
• FIG. 4 shows a diagram of a switching unit
• FIG. 5 shows a partial cross section through the actuating unit according to FIG. 3, cut along the line V-V,
• FIG. 7 shows a partial longitudinal section through the actuating unit according to FIG. 3
• FIG. 8 shows a partial cross section through the actuating unit according to FIG. 3, cut along the line VIII-VIII.
• FIG. 9 is a side view of a toothed segment ring
• FIG. 11 is a side view of part of the selector shaft
• FIG. 12 is a perspective view of a hub
• FIG. 13 is a side view of a part of the selector shaft with a toothed segment ring thereon
• FIG. 14 is a perspective side view of a part of the selector shaft similar to FIG. 13, but turned over by 180 °
• FIG. 15 is a diagram for explaining functional elements of the selector shaft
• FIG. 17 to 20 sectional views of the selector shaft according to line XX in Fig. 3 to explain four different embodiments,
• 21 is a diagram for explaining the routing of the shift shaft
• Fig. 22 is a perspective view of part of the shift shaft for explaining the alley and
• FIG. 23 is an end view of the arrangement according to FIG. 22, rotated by approximately 180 °.
• 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, with 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 that 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 shift gates can be, for example, only 7.5 mm and the distance between two switching positions within a 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 transmission housing and the free end of which is mounted at 18 on the transmission housing.
• the inner diameter D of the flange is, for example, 64 mm; According to FIG. 2, a space of only a maximum of 100 mm is available for the actuation unit above the flange 12.
• 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 extend
• FIG. 3 shows a top view of an actuating unit according to the invention, which can be flanged onto the gear flange 12.
• the actuation unit has a housing 20, on 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.
• 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 switch motor 22 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, which extends 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.
• 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 incline 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.
• the reduction gear 40 is a planetary gear. It is understood that the reduction gear can also be a conventional spur gear. 5 explains the structure of the switching unit in more detail:
• a drive shaft 42 of the switching 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 compressed 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 a serration with 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.
• the plastic acts like an axial plain bearing.
• 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 imprecisely during manufacture. This results in an axial protrusion after assembly in the housing bore 64, which is set to the height of the flange surface 66 by hot stamping.
• a free space 68 serves as a reservoir 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 methods of hot stamping mentioned have the advantage that a retaining ring for the bearing 70 can be dispensed with.
• a high positional accuracy is achieved on the flange surface 66, although the dimension A can be produced relatively inaccurately.
• 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 is single or multi-start and is described in the front section 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 let in, in which two pins 78 guide the spindle nut 34 and serve as an anti-rotation device.
• the pins 78 are firmly pressed into the housing 20, advantageously at right angles to the axis of rotation of the control 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 non-rotatably and rigidly connected to the selector shaft 26, provided with the axially extending radial toothing gear 84 transmits the translated torque to the selector shaft 26.
• the rolling diameter corresponds to the effective force application diameter on the switching pin 30.
• the diagram of the selection unit 85 is explained below with the aid of FIG. 6, with which a rotation initiated by the selection motor 24 is circulated into an axial displacement of the selector shaft 26.
• 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 recorded within a shift lane by means of short travel distances. For this purpose, a pin 86 is pushed against the fixed lane 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 the 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 fixed in the housing 20 serves to guide and support the toothed segment ring 90 when the torque is introduced from the selector motor 24 via the spur toothing 90 into the segment toothing 88.
• 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 translation of torque to force 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 is in engagement 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 with which ser 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.
• segment toothing 88 is formed on a “side wall” of the groove 106, offset radially inward.
• 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 inside diameter of the cylinder 110 has a smooth, drawn sheet metal surface and serves as a bearing running 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 as a plastic ring 116 onto a shoulder 118 of the sleeve 108, so that the outer diameter of the plastic layer or 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 running surfaces 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 bear in the return zones, i.e. the radially inner support surface is smaller in diameter than in the load-bearing areas 122.
• a base 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.
• the toothed segment ring 92 composed of the segment toothing 88 and the sleeve 108 is rotatable and 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 switching elasticity unit 128 is located between the switching pinion 84 formed with the axially extending toothing 38 and the switching shaft 26.
• a hub 130 is fixedly connected to the switching shaft 26 and offers a receptacle for pretensioning springs 132.
• the pinion 84 transfers the power flow Driver webs 134 into the preloaded 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 switching pinion 84 On the switching pinion 84 are the driver webs 134 (FIG. 10) forming cams 140, which are in engagement with the spring bars 142 of FIG. 10 forming spring bars 142.
• the switching pinion 84 ideally consists of sintered material. Alternatively, reinforced plastic is also possible.
• the hub 130 serves for receiving and prestressing the spring bars 142. In FIG. 12, receiving windows 144 are shown. In its lower area, the receiving windows 144 are divided into two segments 146 in order to ensure that the spring bars 142 are firmly clamped. Flanks 148 form a support for the spring bars 142, which tend to spread open. As a result, the spring bars 142 are pretensioned to a certain force level. Via a drive toothing 150 the spring force is supported on the control shaft 26.
• the hub 130 can alternatively 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. I-dealer manner are connected to one another via bars 156 in the case of single beams. It is imperative that a web 156 is firmly fixed between the segment 158 (FIG. 12) and the switching shaft surface 160.
• Gaps 164 extend through the cams 140 (FIG. 11), which correspond to the surface 166 which 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 transmitted positively to the selector shaft 26 via the entrainment / toothing 150.
• the segment 162 is a separate sintered component and can be designed as part of the shift shaft 26.
• 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.
• the selector shaft 26 can move within the dimension 174 specified by the selector shaft shoulder 170 and selector pin 30.
• control shaft 26 The structure of the control shaft 26 is explained in more detail with reference to FIGS. 16 to 20.
• the illustrated selector shaft 26 advantageously consists of at least one plastic injection molded part 176.
• Functionally more highly stressed surfaces such as the selector pins 30, the surfaces 178 and the edges 180, which come into contact with the selector forks or guides (FIG. 2), are preferably made of metal with good surface quality.
• the central region 182 can be filled to increase the torsional rigidity.
• the area 182 and the blocking surfaces 184 and 186 are advantageously ribbed. This increases stiffness 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 design variants of the shift pin 30 and surface 178 areas subject to greater stress.
• the basic principle is to use drawn or punched sheets which are inserted into the mold as segments during injection molding or onto the injection-molded base body of the shift shaft. brought, for example clipped on.
• FIG. 17 shows a variant in which a sheet segment 189 is produced holistically by forming 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.
• 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.
• the sheet segment 189 produced as a whole is clipped onto the injection-molded plastic body 176 in its recess E.
• two symmetrical sheet metal parts 194 are inserted into grooves G, which run in the longitudinal direction of the control shaft 26 and are formed on the plastic base body.
• control 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.
• 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 washer 200, which has a cutout 204 through which the pins 196 can move when the selector 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.
• the width or the angular range of the cutout 204 in connection with a so-called active interlock can be such that, regardless of the shift gate level in which the shift finger is located, each engaged gear is designed by rotation within the angular range of the cutout 204. 22 is symmetrical to the neutral position of the shift finger between two shift gates.
• the swivel angle 2 ⁇ not shown in FIG. 22 can be halved and arranged asymmetrically with respect to FIG. 22 or in one half of the cutout 204 of FIG. 23.
• the angle ⁇ (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 which is asymmetrical with respect to the neutral position (FIG. 23) has the advantage for the actuation of the switching 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.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Gear-Shifting Mechanisms (AREA)
• Structure Of Transmissions (AREA)
• Agricultural Machines (AREA)

Priority Applications (3)

Applications Claiming Priority (4)

Publications (2)

Family

ID=28676057

Family Applications (1)

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Citations (3)

• 2003
  • 2003-04-10 IT ITMI20030717 patent/ITMI20030717A1/it unknown
  • 2003-04-10 DE DE10316434A patent/DE10316434A1/de not_active Withdrawn
  • 2003-04-10 BR BR0304407-6A patent/BR0304407A/pt not_active Application Discontinuation
  • 2003-04-10 FR FR0304474A patent/FR2838497A1/fr not_active Withdrawn
  • 2003-04-10 DE DE10391583T patent/DE10391583D2/de not_active Expired - Fee Related
  • 2003-04-10 AU AU2003232601A patent/AU2003232601A1/en not_active Abandoned
  • 2003-04-10 WO PCT/DE2003/001184 patent/WO2003087632A2/de not_active Application Discontinuation

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