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
  • F16H48/00—Differential gearings
  • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
  • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
• • 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
  • F16H48/00—Differential gearings
  • F16H48/06—Differential gearings with gears having orbital motion
  • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
• • 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
  • F16H48/00—Differential gearings
  • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
  • F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
• • 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
  • F16H1/00—Toothed gearings for conveying rotary motion
  • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
  • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
• • 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
  • F16H48/00—Differential gearings
  • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
  • F16H2048/204—Control of arrangements for suppressing differential actions
• • 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
  • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
  • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
  • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
  • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
  • F16H37/0806—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts
  • F16H37/0813—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one input shaft
  • F16H37/082—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one input shaft and additional planetary reduction gears

Definitions

• the invention relates to a transmission module for a differential assembly for variable torque distribution in the drive train of a motor vehicle and a differential alan extract with such a transmission module.
• Differential arrangements of the type mentioned usually comprise a differential gear with an input shaft and two output shafts, wherein the output shafts have a balancing effect with each other.
• variable torque distribution differential assembly is such that a portion of the torque introduced through the input shaft is diverted from the differential carrier prior to being split between the two output shafts; the branched-off torque component is additionally introduced after the distribution of the remaining torque on one of the two output shafts.
• a gear stage and a friction clutch are provided per output shaft.
• the gear stage includes an input gear driven by the differential carrier that accelerates or decelerates an output gear. By coupling the output gear to the associated output shaft of the differential, the latter is accelerated or decelerated.
• a larger torque can be transmitted than on the other of the output shafts in order to increase the driving stability of the motor vehicle.
• Such gear arrangements can be used for distributing the torque between the two side shafts of an axle differential or for the controlled distribution of the torque between the two output shafts of a center differential of a multi-axle driven motor vehicle.
• a differential assembly with a differential gear and two gear stages is known.
• Each of the gear stages includes two sun gears with mutually different numbers of teeth and with the two sun gears meshing planetary gears.
• these gear teeth In order to achieve a translation from the first sun gear to the second sun gear, these gear teeth have profile-displaced teeth which are in engagement with a continuous toothing of the planet gears.
• the present invention has for its object to propose a transmission module for a differential assembly, which is simple in construction, allows a high positioning accuracy and has a low power loss. It is a further object of the present invention to propose a gear arrangement for variable torque distribution with such a transmission module.
• a first solution consists in a transmission module for the variable torque distribution in the drive train of a motor vehicle, comprising a drive shaft which is rotatably drivable relative to a housing about a first axis of rotation; a hollow shaft, which is arranged coaxially with the first shaft and can be driven in rotation relative thereto; a gear stage having a first sun gear drivably connectable to the hollow shaft, a second sun gear coaxially and adjacent to the first sun gear rotatably connected to the drive shaft, and a ring gear disposed in the housing on a rotation axis parallel to the rotation axis is rotatably mounted and is in meshing engagement with the first sun gear and the second sun gear, wherein the first and the second sun gear have different numbers of teeth; a friction clutch having a first clutch member rotatably connected to the first sun gear and a second clutch member rotatable relative to the first clutch member and rotatably connected to the sleeve shaft, the first sun gear being drive-connected to the s
• a second solution to the above object consists in a transmission module for variable torque distribution in the drive train of a motor vehicle, comprising a drive shaft which is rotatably drivable relative to a housing about a first axis of rotation; a hollow shaft, which is arranged coaxially with the first shaft and is rotatably drivable relative thereto; a gear stage having a first sun gear rotatably connected to the hollow shaft, a second sun gear coaxially and adjacent to the first sun gear and drive-linkable with the drive shaft; and a ring gear rotatably supported in the housing on a rotation axis parallel to the rotation axis is and with the first sun gear and the second sun gear in meshing engagement, wherein the first and the second sun gear have different numbers of teeth; a friction clutch having a first coupling part, which is non-rotatably connected to the second sun gear, and a second coupling part rotatable relative to the first coupling part, which is non-rotatably connected to the drive shaft, the drive
• a third solution consists in a transmission module for variable torque distribution in the drive train of a motor vehicle, comprising a drive shaft which is rotatably drivable relative to a housing about a first axis of rotation; a hollow shaft, which is arranged coaxially with the first shaft and can be driven in rotation relative thereto; a gear stage with a first sun gear, which is rotatably connected to the hollow shaft, a coaxial and adjacent to the first sun gear arranged second sun gear, which is rotatably connected to the drive shaft, and with a ring gear, which is rotatable in a support member on a rotation axis parallel to the rotation axis is mounted and in meshing engagement with the first sun gear and the second sun gear, wherein the first and the second sun gear have different numbers of teeth, and wherein the support member is rotatably mounted in the housing coaxially to the rotation axis; a friction clutch having a first coupling part which is rotatably connected to the housing, and a rotatable relative
• All three embodiments of the invention have the advantage of a simple structure and thus a simple production and assembly. It is ever gear only required a ring gear, which is in meshing engagement with the first and the second sun gear. That is, in total, each gear stage comprises only three gears.
• the use of the ring gear is particularly favorable because a high degree of wrap around the sun gears is achieved.
• a plurality of teeth of each formed between the ring gear and sun gear pairing engaged with each other so that the load per tooth is low.
• Another advantage of the transmission module according to the invention is that the radial space is relatively small and the unit is compact.
• the transmission module is versatile and can be used for example in an axle differential for variable torque distribution between two side shafts of a drive axle. Alternatively or in addition to this, the transmission module can also be used in a center differential of a multi-axle driven motor vehicle, wherein it serves for the variable torque distribution between the front axle and the rear axle.
• the friction clutches are preferably designed in the form of multi-plate clutches and comprise two coupling parts, namely an outer disk carrier, with the outer disk rotatably and axially slidably connected, and an inner disk carrier, rotatably connected to the inner disk carrier and are axially displaceable. It is understood that the two coupling parts in the three embodiments can be designed in principle both as outer disk carrier and as an inner disk carrier.
• the ring gear has a first toothed area, which meshes with the first sun gear, and a second toothed area, which meshes with the second sun gear, wherein the two toothed areas have different toothings with different numbers of teeth ,
• the ring gear has a first toothed area, which meshes with the first sun gear, and a second toothed area, which meshes with the second sun gear, wherein the two toothed areas have a matching toothing.
• the two sun gears which have the same center distance relative to the axis of rotation of the ring gear relative to each other profile-shifted teeth.
• the advantage of the matching toothed regions of the ring gear lies in the high degree of accuracy of the tooth engagement with the sun gears meshing therewith. It is particularly advantageous if the two toothed areas of the ring gear seamlessly connect to each other, that is, form a single common continuous toothing.
• both toothed areas can be produced together, which has a favorable effect on the cost.
• the teeth of the two sun gears and the teeth of the ring gear have the same module.
• the translation or reduction from the first sun gear to the second sun gear is effected only by profile displacement of the two gears to each other.
• the teeth numbers of the first and second sun gears are selected such that a ratio of 0.85 to 1.15, except for a ratio of 1.0, between the first and the second Sun gear is generated.
• a supplementary or reduced torque of ⁇ 15% can be transmitted to the corresponding drive shaft.
• a translation is generated quickly from the first sun gear to the second sun gear.
• the number of teeth of the ring gear is greater than the number of teeth of the first sun gear, which in turn is greater than the number of teeth of the second sun gear.
• the sun gears and the ring gear are preferably helically toothed.
• the helical gears are preferably designed such that the axial forces acting on the first and the second sun gear by the toothing engagement with the ring gear - are directed towards each other - when driving forward of the motor vehicle.
• the sun gears and the ring gear can of course also have straight teeth.
• the ring gear is preferably mounted rotatably by means of a roller bearing on a bearing shoulder of the housing eccentrically to the axis of rotation of the sun gears.
• the first sun gear is rotatably mounted on the second sun gear by means of bearing means, which in turn is rotatably connected to the drive shaft.
• an axial adjustment device for actuating the friction clutch is provided.
• This can be designed, for example, in the form of a ball ramp arrangement known per se, which comprises two disks centered on the axis of rotation and balls held axially between the disks.
• one of the discs is axially supported relative to the housing and the other is axially displaceable.
• the two discs On their facing end faces, the two discs have an equal number of ball grooves with increasing in opposite circumferential view depth, wherein in each pair of opposing ball grooves one of the balls is held.
• the friction clutch can also be actuated hydraulically.
• the Axialverstellvorraum is designed in the form of a piston-cylinder unit.
• the piston is designed annular and sits in an outwardly sealed annular chamber in the housing.
• the annular piston acts on the disk set of the friction clutch via a thrust bearing.
• a further solution to the above object consists in a differential arrangement for variable torque distribution in the drive train of a motor vehicle, comprising a differential gear with a rotatably driven differential carrier, differential gears, which are rotatably supported in the differential carrier and rotate together with this about the axis of rotation, as well as two side gears rotatably mounted on the rotation axis, which mesh with the differential gears; and at least one transmission module according to one of the above three solutions, wherein the hollow shaft is rotatably connected to the differential carrier and wherein the drive shaft is rotatably connected to one of the two side gears.
• the transmission module may have one of the abovementioned embodiments.
• the differential assembly may be used as an axle differential of a single- or multi-axle driven motor vehicle and / or as a center differential of a multi-axle driven motor vehicle.
• FIG. 1 shows a transmission module according to the invention according to a first embodiment a) in longitudinal section; b) in cross-section the gear arrangement;
• Figure 2 shows a transmission module according to the invention according to a second embodiment in longitudinal section
• Figure 3 shows a transmission arrangement according to the invention with a transmission module according to the invention in a third embodiment as a schematic diagram
• FIG. 4 schematically shows a gear arrangement according to the invention with a gear module according to the invention in a fourth embodiment as a schematic representation
• Figure 5 schematically shows a transmission arrangement according to the invention with a transmission module according to the invention in a fifth embodiment as a schematic diagram
• FIG. 6 schematically shows a gear arrangement according to the invention with a gear module according to the invention in a sixth embodiment as a schematic representation
• FIG. 7 schematically shows a gear arrangement according to the invention with a gear module according to the invention in a seventh embodiment as a schematic representation
• FIG. 8 schematically shows a gear arrangement according to the invention with a gear module according to the invention in a eighth embodiment as a basic representation
• FIG. 1 shows a gear module 2 which has a first shaft in the form of a drive shaft 3, a second shaft rotatably mounted coaxially with the first shaft in the form of a hollow shaft 4, a gear stage 5 lying in the torque flow between the drive shaft 3 and the hollow shaft 4, and a friction clutch 6 for coupling a gear 32 of the gear stage 5 to the hollow shaft 4 comprises.
• the drive shaft 3 is rotatably supported by means of a rolling bearing 7 in a housing 8 of the transmission module 2 and sealed by a shaft seal 9 with respect to this.
• the drive shaft 3 has a flange 10 for connection to an associated side shaft, not shown here, of the motor vehicle.
• the transmission module 2 is screwed via a flange 12 to a differential housing of a differential gear, not shown here.
• the drive shaft 3 is rotatably connected via a longitudinal toothing with a side gear of the differential gear.
• the hollow shaft 4 is rotatably connected via a longitudinal toothing with the differential carrier of the differential carrier.
• the hollow shaft 4 is formed integrally with a sleeve extension 13 of the differential carrier. In this case, the sleeve extension 13 relative to the differential housing 14 by means of a Rolling bearing 15 rotatably mounted and sealed by a sealing ring 16 relative to this.
• an axial adjustment device 17 is provided, which is designed in the form of a hydraulically actuated piston-cylinder unit.
• This comprises an annular piston 18 which is seated in an annular chamber 19 of the differential housing 14 and sealed by means of sealing rings 20, 22 with respect to this.
• the piston 18 is displaced in the direction of the friction clutch 6.
• the friction clutch 6 is acted upon axially via an axially interposed thrust bearing 24 and a pressure plate 25.
• the friction clutch 6 comprises a first clutch part in the form of an inner disk carrier 26, which is non-rotatably connected to the hollow shaft 4 via a spline and axially movable and rotationally fixed relative to the inner disk, and a second coupling part in the form of an outer disk carrier 27, the is rotatably connected to the gear 32 of the gear stage 5 and are held axially movable and rotationally fixed relative to the outer disk.
• spring means 29 are arranged which are axially supported against the inner disk carrier and act on the pressure plate 25 of the effective direction of the piston-cylinder unit counteracting.
• the spring means 29, which are designed as helical springs, thus serve to reset, so that the friction clutch is released at unconfirmed piston-cylinder unit.
• the outer disk carrier 27 is cup-shaped and includes a bottom 28 which serves as a support surface for the disk set 23. Furthermore, the outer disk carrier 27 is integrally formed with the designed as a sun gear 32 gear of the gear stage.
• the gear stage 5 comprises, in addition to the first sun gear 32, a ring gear 33 meshing therewith and a second sun gear 34 meshing with the ring gear 33, which is arranged axially adjacent to the first sun gear 32.
• the first sun gear 32 is connected to an outer surface of the outer disk carrier 27 and over this sen rotatably mounted on a hub 36 of the second sun gear 34 by means of a rolling bearing 35.
• the rolling bearing 35 serves as a radial and thrust bearing.
• the friction clutch 6 is located radially inside the ring gear 33 and with partial overlap to this, so that there is a compact structure.
• the second sun gear 34 is rotatably connected via a spline between the hub 36 and the drive shaft 3 with this.
• the hub 36 On the flange side, the hub 36 has an outer bearing surface 37, on which the roller bearing 7 is seated.
• the ring gear 33 is rotatably supported by means of a rolling bearing 38 on a bearing shoulder 39 of the module housing 8 on an axis B eccentric to the axis of rotation A. It follows that the sun gears 32, 34 in a peripheral region with the ring gear 33 mesh, which can be seen in the upper half of the picture.
• the arrangement of the sun gears 32, 34 to the ring gear 33 can be seen in particular in Figure 2.
• the axial distance between the axis of rotation A, on which the sun gears 32, 34 lie, and the axis B, on which the ring gear 33 is located denoted by E.
• the speed ratio is made possible by profile displacement of the toothings of the two sun gears 32, 34 relative to each other, wherein the sun gears and the ring gear 33 have the same module.
• the ring gear 33 has two toothed portions 41, 42 with matching teeth, one of which is meshingly engaged with the first sun gear 32 and the other with the second sun gear 34. In order to achieve a speed ratio between the two sun gears 32, 34, these have a different number of teeth.
• the numbers of teeth of the sun gears 32, 34 are chosen so that between the hollow shaft 4 and the drive shaft 3, a speed difference of up to 15% is achieved. In the present case, a translation from the first sun gear 32 to the second sun gear 34 is generated quickly.
• the first sun gear 32 has a larger number of teeth Z1 than the number of teeth Z2 of the second sun gear 34, wherein the teeth number ratio Z1 to Z2 is between 1, 10 and 1, 12.
• the ring gear 33 has a number of teeth Z3 which is greater than the number of teeth Z1 of the first sun gear 32nd
• the operation of the gear module is as follows.
• the friction clutch 6 When the friction clutch 6 is open, the inner disk carrier 26, which is connected in a rotationally fixed manner via the hollow shaft 4 to the differential carrier 13, rotates faster than the latter via the gear stage 5 with the If the friction clutch 6 is closed by operating the Axialverstellvorraum, an additional torque is tapped directly from the differential carrier and introduced via the friction clutch 6 and the gear stage 5 in the drive shaft 3. This additional torque flow is shown in FIG. 1 with the aid of arrows. The closing of the clutch thus causes an asymmetric torque distribution between the two output shafts of the differential gear, so that the driving stability of the motor vehicle is increased in certain driving conditions.
• FIG. 2 shows a second embodiment of a transmission module according to the invention.
• the differential gear 43 with its differential cage 44 is partially visible, on which a ring gear 45 is mounted for torque introduction.
• the differential cage 44 has two sleeve-shaped projections 13, with which it is rotatably mounted in the differential housing 14 by means of the rolling bearing 15 about the axis of rotation A.
• a plurality of differential gears 46 are rotatably mounted on a pivot axis A perpendicular to the pin 49, which rotate together with the differential carrier.
• differential gears 46 are two bywel- lenzier 47 in meshing engagement, which serve to transmit torque to the respective drive shaft 3 of the transmission module 2.
• the side-shaft gears 47 are rotatably mounted in the differential cage 44 on the axis of rotation A and axially supported via thrust washers 48 with respect to this.
• thrust washers 48 with respect to this.
• only one half of the differential gear and only one transmission module is visible, wherein the non-visible half is designed approximately mirror-symmetrically to the visible half.
• the transmission module shown 2 2 is characterized in that the Axialverstellvoruze 17 2 is designed in the form of a ball ramp assembly.
• This comprises two coaxial to the axis of rotation A discs 52, 53 and held between the discs balls 54.
• the first of the discs is designed as a support plate 52 which is axially supported relative to the differential housing 14 and held against rotation therewith.
• the second disc is axially displaceable and rotationally driven Adjusting washer 53 designed.
• the two discs 52, 53 each have on their mutually facing end faces a plurality of circumferentially distributed and extending in the circumferential direction ball grooves with oppositely variable depth. In each case a pair of opposing ball grooves one of the balls 54 is taken up, over which the two discs are supported axially.
• the adjusting disc 53 is supported radially only via the balls 54 relative to the support disc 52, wherein the support disc is fixed on a sleeve-shaped projection of the differential housing 14.
• the balls 54 are held in a cage arranged axially between the two discs with circumferentially distributed windows.
• adjusting disk 52 To achieve a rotational movement of the adjusting disc 53, this is provided on its outer peripheral surface with an outer toothing 55.
• a pinion In the external teeth 55 engages a pinion, not shown, which is rotatably mounted in the housing 14 and is rotatably driven by an electric motor.
• adjusting disk 52 and support plate 53 In the unactuated state, that is at fully open friction clutch 6, adjusting disk 52 and support plate 53 are in the closest possible position to each other.
• the balls 54 run in areas of lesser depth.
• a spread takes place between the discs, wherein the adjusting disc 52 is axially displaced in the direction of the friction clutch 6.
• the adjusting disk 52 has on its rear side a radial pressure surface, which acts on the pressure plate 25 axially via an interposed thrust bearing 56.
• the pressure plate 25 is axially in abutment with the disk set 23 and acts upon the ball ramp arrangement with an axial force in the closing direction.
• an actuation of the ball ramp assembly leads to a predetermined blocking of the friction clutch 6 and thus a coupling of the first sun gear 32 2 to the faster rotating differential cage 44.
• the adjusting disc 53 is actuated in the opposite direction. This effect axially supported on the gear housing and the adjusting washer 53 acting on compression springs, which are not visible in the present section, a provision of the adjusting disk in the direction of the support disk 54th
• a thrust washer 57 is provided axially between the hollow shaft 4 and the hub 36 of the second sun gear 34 2 .
• the first sun wheel 32 2 is rotatably mounted on the hub 36 of the second sun gear 34 2 by means of a radial bearing 58 and axially supported by means of a thrust bearing 59 with respect to this.
• axial forces acting on the first sun gear 32 2 are supported by the outer disk carrier 27 2 and introduced into the module housing 8 from the second sun gear 34 2 via the roller bearing 7.
• the cup-shaped outer disk carrier 27 is fixedly connected to the first sun gear 32 2 by welding.
• the outer disk carrier is present adjacent to the first sun gear 32 2 arranged.
• the friction clutch 6 and the disk set 23 are thus on a larger diameter than in the above embodiment, while the gear stage 5 in this case builds radially compact.
• FIG 3 shows a schematic diagram of an inventive differential assembly 62 for variable torque distribution between two side shafts 63, 63 'in the drive train of a motor vehicle.
• the differential assembly 62 is symmetrical and comprises a differential gear 43, as already described in connection with Figure 2, with two transmission modules according to the invention 2, 2 ', which are arranged axially adjacent to the differential gear 43.
• the two gear modules 2, 2 ' correspond to each other and are therefore described together, with components of the right gear module are provided with a primed by one mark.
• the two gear modules correspond in terms of their structure and operation to those of Figure 1 and Figure 2, to the description of which reference is made. In this case, corresponding components are provided with the same reference numerals as in Figures 1 and 2.
• the required for the actuation of the friction clutches 6, 6 'Axialverstellvorraumen are not shown. It is the ring gear 45 recognizable, which is in meshing engagement with a drive pinion.
• the ring gear 33, 33 ' has two toothing regions with a continuous toothing, wherein a first toothed region 41, 41' meshes with the first sun gear 32, 32 * and a second toothed region 42, 42 'meshes with the second sun gear 34, 34' ,
• the speed ratio is accomplished by profile displacement of the teeth of the two sun gears 32, 32 ', 34, 34' to each other. It can be seen that the left and the right ring gear on different eccentric axes B, B 1 , each with the same center distance to the axis of rotation A, are arranged.
• FIG. 4 shows a gear arrangement in a further embodiment, which largely corresponds in terms of its construction to that of FIG.
• the present embodiment differs only in the configuration of the ring gears 33 4 , 33 4 '.
• the toothed area 41 4 , 41 4 ' which meshes with the first sun gear 32, 32', and the toothed area 42 4 , 42 4 ', which meshes with the second sun gear 34, 34 "are each at different diameters and have different numbers of teeth
• the first sun gear 32, 32 'couplable to the differential cage 44 has a larger number of teeth Z1 than the number Z2 of the second sun gear 34, 34' which is rotationally fixed to the drive shaft 3, 3 '
• the first toothed portion 41 4 , 41 4 "of the ring gear 33 4 , 33 4 'meshing with the first sun gear 32, 32' also has a larger number of teeth than that with the second sun gear 34 , 34 'meshing second gear portion 42 4 , 42 4 ' of the ring gear.
• the operation is the same as the above management forms.
• FIG. 5 shows a gear arrangement in a further embodiment, which largely corresponds to that of FIG. 3 with respect to its structure and mode of operation.
• the present embodiment is characterized in that the first sun gear 32, 32 "is rotatably connected to the differential cage 44 and that the second sun gear 34, 34 'via the friction clutch 6, 6' with the drive shaft 3, 3 'can be coupled
• the first coupling part 26 5 , 26 5 of the friction clutch 6, 6 ' which is designed as an outer disk carrier, is connected in a rotationally fixed manner to the second sun gear 34, 34.
• the second clutch part 27 5 , 27 5 ' of the friction clutch which forms the inner disk carrier It can be seen that the ring gears 33, 33 'each have a continuous toothing or two toothed areas 41, 42, 41 ", 42' with matching toothing.
• the two sun gears 32, 34; 32 ', 34' have profile-shifted teeth with different numbers of teeth relative to one another, wherein they have the same center distance to the respective ring gear 33, 33 '.
• the translation is also effected here by the profile displacement of the two sun gears to each other.
• the numbers of teeth of the sun gears 32, 34; 32 ', 34' are designed so that a translation into speed, that is, the outer disk carrier 26 5l 26 5 1 rotates faster than the drive shaft 3, 3 '.
• FIG. 6 shows a gear arrangement in a further embodiment, which largely corresponds in terms of its structure to that of FIG.
• the present embodiment differs only in the embodiment of the ring gears 33 ⁇ , 33 ⁇ '.
• the gearing area 41 6 , 4 V, which meshes with the first sun gear 32, 32 ', and the toothed portion 42 6 , 42 6 ', which meshes with the second sun gear 34, 34 ' are each at different diameters and have different numbers of teeth.
• FIG. 7 shows a gear arrangement in a further embodiment which, with respect to its structure, largely corresponds to that of FIG.
• the first sun gear 32, 32 'rotatably connected to the differential cage 44, and the second sun gear 34, 34' is rotatably connected to the associated drive shaft 3, 3 '.
• the ring gear 33 7 , 33 7 ' which with its first toothed portion 41, 41' with the first sun gear 32, 32 'and with its second toothed portion 42, 42' with the second sun gear 34, 34 'is engaged, is in one Support member 30, 30 'rotatably mounted on an axis of rotation A of the sun wheels parallel axis B, B'.
• the carrier element 30, 30 ' is rotatably mounted in the housing 8, 8' by means not shown bearing coaxial with the axis of rotation A.
• the friction clutch 6 7 , 6 7 ' comprises a first coupling part 26 7 , 26 /, which is held firmly against the stationary module housing 8, 8'.
• the friction clutch 6 7 , 6 / a second coupling part 27 7 , 27 /, which is designed as an inner disk carrier and with the support member 30, 30 'rotatably connected.
• internal disk carrier and outer disk carrier can also be reversed without the function of the transmission module changes.
• the operation of the arrangement is as follows. In the unactuated state, the support member 30, 30 'runs together with the ring gear 33, 33' in the block about the axis of rotation A, wherein "in block” means that the two components perform relative movement to each other.
• the two sun gears 32, 34; 32 ', 34' have relative to each other profile-shifted teeth with different numbers of teeth, where they have to the associated ring gear 33 7 , 33 7 'the same center distance E, E'.
• the translation is here also by the profile displacement of the two sun gears 32, 34; 32 ', 34' causes each other.
• the numbers of teeth of the sun gears are designed so that a translation is done quickly.
• FIG. 8 shows a gear arrangement in a further embodiment, which largely corresponds in terms of its construction to that of FIG.
• the present embodiment differs only in the configuration of the ring gears 33 s, 33 8 ', which each have two different toothing areas.

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• Mechanical Engineering (AREA)
• Retarders (AREA)
• Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)

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