EP3701162A1 - Dispositif et procédé de synchronisation - Google Patents

Dispositif et procédé de synchronisation

Info

Publication number
EP3701162A1
EP3701162A1 EP18786665.2A EP18786665A EP3701162A1 EP 3701162 A1 EP3701162 A1 EP 3701162A1 EP 18786665 A EP18786665 A EP 18786665A EP 3701162 A1 EP3701162 A1 EP 3701162A1
Authority
EP
European Patent Office
Prior art keywords
gear
actuating
transmission
locking
synchronizer
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP18786665.2A
Other languages
German (de)
English (en)
Inventor
Oswald Friedmann
Wolfgang Haas
Dominik Hans
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP3701162A1 publication Critical patent/EP3701162A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/02—Arrangements for synchronisation, also for power-operated clutches
    • F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
    • F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/02—Arrangements for synchronisation, also for power-operated clutches
    • F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
    • F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
    • F16D2023/0637—Details relating to the hub member on which the sliding is arranged
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms

Definitions

  • the invention relates to a device for synchronizing between a shaft and a loose wheel, which is rotatably mounted on the shaft, with an actuating device, a synchronizer and a coupling device.
  • the invention further relates to a transmission with pairs of wheels, each comprising a fixed gear and a loose wheel to represent gears in the transmission.
  • the invention further relates to a method for synchronizing between a transmission shaft and a loose wheel, which is rotatably mounted on the transmission shaft, with a device previously described.
  • a synchronizer for a transmission with a rotationally fixed on a gear shaft in the circumferential direction of the transmission shaft synchronizer body is known, with a slidably mounted on the synchronizer body along the longitudinal center axis of the transmission shaft sliding sleeve, with at least one rotatable on the transmission shaft mounted and connected to the synchronizer body gear, which is connected to a coupling body or provided with a coupling toothing and can be coupled via the coupling body or the coupling teeth by means of the sliding sleeve with the synchronizer body.
  • German Offenlegungsschrift DE 0 2009 027 438 A1 discloses a synchronizing device for a manual transmission with a synchronizer body and at least one synchronizer ring, which can be fixed relative to one another in the circumferential direction by means of an indexing, wherein the indexing of at least one arranged on the synchronizer ring and in Substantially extending in the axial direction projection is formed, which engages in at least one recess of the synchronizer body, wherein the recess has at least one inclined surface portion on which the projection rests on a rotation of the synchronizer ring relative to the synchronizer body slidably.
  • a synchronization for a vehicle transmission which has a sliding sleeve, a synchronizer ring, a clutch comprises at least one inclined surface on which the synchronizer body and the synchronizer ring surface contact, and at least one acting between the synchronizer body and the synchronizer ring elastic element is provided, the one generates force acting in the circumferential direction, which press the inclined surfaces of synchronizer body and synchronizer ring to each other so that on the synchronizer ring a force acting in the direction of the synchronizer body force component arises.
  • the object of the invention is to optimize a device for synchronizing between a shaft and a loose wheel, which is rotatably mounted on the shaft, with an actuating device, a synchronizer and a coupling device with respect to the required space.
  • the object is in a device for synchronizing between a shaft and a loose wheel, which is rotatably mounted on the shaft, with an actuator, a synchronizer and a coupling device, achieved in that a locking device, the barrier effect between the, with respect to the idler gear , Is arranged radially outwardly operable actuator and the radially arranged within the idler gear synchronizer, is received radially within the idler gear.
  • the locking device is advantageously arranged overlapping in the axial direction to the idler gear. As a result, axial space can be saved.
  • the locking device prevents too early engagement of the clutch device. Only when a differential speed between the shaft and the idler gear is reduced substantially to zero, the locking device allows an actuating movement in the axial direction, which is converted from an actuating movement in the circumferential direction and transmitted to the coupling device.
  • the actuating movement in the circumferential direction is advantageously applied via an actuating element, such as a gear, radially outside the idler gear.
  • the synchronizer comprises a synchronizer ring package having synchronizer rings which are frictionally contacted by application of an axial actuation force to generate a frictional torque, also referred to as synchronous torque.
  • the coupling device is preferably designed as a form-locking coupling, for example as a dog clutch.
  • the lock pure direction via which the synchronizer can be actuated, arranged between an actuating element of the actuating device and a synchronizer ring of the synchronizer.
  • a preferred embodiment of the device is characterized in that the locking means is actuated by ramps to convert a rotational movement of an actuating element of the actuating device into an axial actuating movement.
  • a further preferred embodiment of the device is characterized in that the locking device comprises at least one blocking element.
  • the locking element is secured against rotation with respect to the idler gear, for example by a transmission element.
  • the blocking element can be designed as a locking ring.
  • the blocking element may also comprise a plurality of blocking segments.
  • the locking device may also comprise more than one blocking element.
  • a further preferred embodiment of the device is characterized in that the blocking element is provided with operating bevels.
  • the operating bevels which are also referred to as roof slopes, are advantageously also provided on the synchronizer and / or the coupling device.
  • a synchronizing ring of the synchronizing ring packet can rotate relative to the synchronizing device by a width of a roof slope or guide slope and thus prevent a further shifting of the synchronizing device.
  • the synchronizer device rotates back a synchronizer ring of the synchronizer ring packet and shifts further in the axial direction, but advantageously only by the amount of a wear reserve.
  • a further preferred embodiment of the device is characterized in that the blocking element is axially movable via ramps. If the actuator is rotated relative to the idler gear, then the locking member is displaced axially over the ramps in the direction of the synchronizer. The ramps thus act between the actuating element and the blocking element, which is non-rotatably but axially displaceable, coupled to the idler gear.
  • a spring device is arranged between the blocking element and a synchronizing ring of the synchronizing device.
  • the spring device is designed for example as a spring ring.
  • the spring device may also comprise a plurality of spring segments, for example, three spring segments or spring arches.
  • the synchronizer rings of the synchronizer ring packet are applied, that is brought into frictional contact. As a result, a slight friction torque is generated, wherein the synchronizer ring is rotated relative to the blocking element.
  • the guide slopes or roof slopes are then axially next to each other. About the guide slopes or roof slopes, a relatively large force can be transmitted to the synchronizer ring.
  • a further preferred embodiment of the device is characterized in that the blocking element is designed as a locking ring.
  • the guide slopes or roof slopes are, for example, mounted radially on the outside of the locking ring.
  • actuating ramps are attached to the locking ring. By way of the actuating ramps, in cooperation with corresponding counter-ramps provided on an actuating element, for example a planetary carrier, an actuating movement of the actuating element in the circumferential direction can be converted into an axial movement of the blocking ring.
  • a further preferred embodiment of the device is characterized in that the locking device comprises three blocking elements.
  • the three blocking elements are advantageously distributed uniformly in the circumferential direction.
  • guide slopes or sloping roofs are mounted, which cooperate with corresponding guide slopes or sloping roofs on the synchronizer ring of the synchronizer.
  • a further preferred embodiment of the device is characterized in that the actuating device comprises a planetary gear element of a planetary gear.
  • An actuating element of the actuating device is, for example, a planet carrier, a ring gear or a sun gear of the planetary gear.
  • the actuating element may be integrally connected to the planet carrier, the ring gear or the sun gear of the planetary gear.
  • the ring gear, the sun gear or the planet carrier but also represent the actuating element of the actuator.
  • the planetary gear element is defined for actuating the device rotated or pivoted to produce a relative rotation. This relative rotation is converted into an axial actuating movement, preferably by ramps.
  • a further preferred embodiment of the device is characterized in that the synchronizing device comprises a sliding sleeve.
  • the sliding sleeve is provided, for example radially inward, with a toothing which cooperates with a complementary toothing, which is provided radially on the outside of a coupling body, in order to enable torque transmission between the shaft and the idler gear when the coupling device is closed.
  • the toothing is designed, for example, as a spline so that the sliding sleeve in the axial direction is movable relative to the coupling body.
  • At the mutually facing ends of the sliding sleeve and the Kupplungsungskör- pers bevels or sloping roofs are advantageously provided. As a result, the engagement of the teeth between the sliding sleeve and the coupling body is simplified.
  • a further preferred embodiment of the device is characterized in that the blocking element is rotatably connected by at least one transmission element with the idler gear.
  • the transmission element may be positively connected to the idler gear, for example via a pin which engages in a recess.
  • the transmission element can also be designed as a nose or tab.
  • the transmission element is, for example, attached to the sliding sleeve. brought.
  • the transmission element allows a return movement of an actuating movement, which were caused by the previously described ramps.
  • a plurality of transmission elements are distributed uniformly in the circumferential direction.
  • Another preferred embodiment of the device is characterized in that act between a synchronizer ring of the synchronizer and the transmission element stops with a torsional backlash.
  • the coupling device is designed as a self-opening positive locking coupling. This means that the clutch device is open in the unactuated state, so no torque between the idler gear and the shaft is transmitted.
  • the coupling device is locked in a closed state. The locking is advantageously represented by the ramps, in particular by corresponding plateaus on the ramps.
  • the sliding sleeve comprises a ball pressure piece, which cooperates with a return ramp to hold the sliding sleeve in an end position.
  • the above object is alternatively or additionally achieved in that at least one previously described device for synchronizing between two on a transmission shaft adjacent idler gears of the transmission is arranged.
  • the planetary gear is preferably arranged between the two loose wheels.
  • a relative rotation of an actuating element of the planetary gear that is, for example, a sun gear, a ring gear or a planet carrier of the planetary gear, generates a synchronization of the corresponding idler gear.
  • the actuators can be coupled for example via stops with the associated idler gear, wherein only one in each case a predetermined direction of rotation, the one or the other idler gear from the stop or the attacks is released. This can be safely prevented in a simple manner an undesirable simultaneous insertion of two courses.
  • the above object is alternatively or additionally achieved in that the synchronizer and the coupling device be displaced successively by a relative movement of the actuator to the idler gear so that the idler gear is rotatably connected to the transmission shaft, the locking device ensures that the corresponding idler gear is then connected to the transmission shaft rotationally fixed when the transmission shaft and the idler gear substantially the same Have speed.
  • FIG. 1 shows a transmission with a transmission input shaft, on which two fixed wheels are arranged, and with a transmission output shaft, on which two loose wheels are arranged, which mesh with the fixed wheels;
  • Figure 2 shows a detail of Figure 1 with a device for synchronizing between the transmission output shaft and the two loose wheels;
  • FIG. 3 shows an enlarged detail from FIG. 2, in which an actuation of the left-hand idler gear shown in FIG. 3 is illustrated;
  • Figure 4A is a perspective view of a sliding sleeve of the device of Figures 1 to 3 with the clutch device open;
  • FIG. 4B shows the same illustration as in FIG. 4A with the coupling device closed;
  • Figure 5 is a perspective view of a planet carrier of the device of Figures 1 to 3 with a blocking element designed as a locking element;
  • Figure 6 is an exploded view of the device of Figures 1 to 3 with the
  • Figure 7 is a similar view as in Figure 2 with a device according to a second embodiment with a ball pressure piece and a return ramp;
  • FIG. 8 shows an enlarged detail from FIG. 7
  • FIG. 9 is a perspective sectional view of the left idler wheel in FIG. 7 with the clutch device open;
  • Figure 10 is the same view as in Figure 9 with closed and locked
  • Figure 1 1 is a perspective view of a synchronizer ring with a locking device
  • Figure 12 is a perspective sectional view of a planet carrier with the synchronizer ring and the locking device of Figure;
  • Figure 3 is a similar view as in Figure 2 with a complete longitudinal section through the two idler gears according to a further embodiment
  • Figure 14 is an enlarged detail of Figure 13;
  • Figure 15A is a perspective view of a sliding sleeve with a movement device for the sliding sleeve with the coupling device open;
  • FIG. 15B shows the same illustration as in FIG. 15B with the door closed and locked
  • FIG. 16 is an exploded view of a two-part planetary carrier with a locking device
  • Figure 17 is a partially cutaway perspective view of a moving means for synchronization with a sun gear and a locking device
  • Figure 18 is an exploded view of the locking device of Figure 17 with a
  • FIG. 1 shows a transmission 10 with a transmission input shaft 1 and a transmission output shaft 2.
  • the transmission output shaft 2 is rotatably mounted with the aid of two bearing devices 3, 4 parallel to the transmission input shaft 1 and in Figure 1 about a horizontally extending axis of rotation.
  • the fixed wheels 5, 6 are arranged on the transmission input shaft 1.
  • the fixed wheels 5, 6 are rotatably connected to the transmission input shaft 1.
  • two idler gears 7, 8 are arranged on the transmission output shaft 2.
  • the idler gear 7 meshes with the fixed gear 5.
  • the idler gear 8 meshes with the fixed gear. 6
  • the idler gears 7, 8 are rotatably mounted relative to the transmission output shaft 2, but can be rotatably connected to the transmission output shaft 2 at an actuation to represent a gear in the transmission 10 together with the corresponding fixed gear 5, 6.
  • the actuation takes place via an actuating device 9 radially outside the idler gears 7, 8.
  • the transmission designated by 10 in FIG. 1 comprises two synchronizing devices 1 1, 12.
  • the device for synchronizing 1 1 is assigned to the idler gear 7 arranged on the left in FIGS. 2, 7 and 13.
  • the device for synchronizing 12 is assigned to the idler wheel 8 arranged on the right in FIGS. 2, 7 and 13.
  • the actuating device 9 comprises an actuating wheel 13, which is provided on an outer diameter with a toothing. The outer diameter of the actuating wheel 13 is greater than the outer diameter of the two loose wheels 7, 8. In the axial direction, the operating wheel 13 between the two loose wheels 7, 8 is arranged.
  • the devices 1 1, 12 are received in corresponding recesses radially within the idler gears 7, 8.
  • the operating wheel 13 is led out between the two loose wheels 7, 8 from the receiving space for the devices 1 1, 12 within the idler gears 7, 8 radially outward.
  • the operating wheel 13 for example by means of a driven gear, radially outside the idler gears 7, 8 are actuated.
  • pressing the operating wheel 13 is rotated or pivoted.
  • the actuating device 9 comprises a planetary gear 14.
  • the planetary gear 14 is disposed in a cavity radially inwardly and axially between the adjacent idler gears 7, 8.
  • the axial space for the actuator 9 can be reduced in the transmission.
  • the planetary gear 14 comprises a sun gear 15, a ring gear 16 and Planetenrä- 7.
  • the planet gears 7 are rotatably mounted in a planet carrier
  • the sun gear 15 meshes with the planet gears 17, which in turn mesh with the ring gear 16.
  • the planet carrier 18 rotates in an unactuated state of the devices, 12 substantially synchronously with the idler gear 7.
  • the sun gear 5 rotates in the unactuated state of the devices 1 1, 12 substantially synchronously with the idler gear.
  • substantially synchronous in this context also means that the sun gear 15 and the planetary carrier 18 after actuation by the actuator 9 by a limited angle relative to the idler gears 7, the eighth can rotate to trigger a clutch, switching and / or synchronizing.
  • the ring gear 16 When operating the actuator 9, the ring gear 16 is rotated. In the actuated and unactuated state of the actuator 9, the ring gear 16 is fixed. Then the ring gear 16 has the same speed as the transmission, which is established. Thus, the ring gear 16 of the planetary gear 14 in the unactuated state of the actuator 9 has a speed of zero. When the ring gear 16 is rotated, then either the planet carrier 18 or the sun or the sun gear 15 rotates relative to the associated idler gear 7, 8. This relative twist angle is then used in an operation of one of the devices 1 1, 12 for synchronization.
  • the devices 1 1, 12 for synchronization comprise a coupling device 20 and a synchronizer 21.
  • the coupling device 20 comprises a coupling body 22, which serves to represent a rotationally fixed connection between the shaft 2 and one of the idler gears 7, 8.
  • the left idler gear 7 associated device 1 1 also comprises a locking device 23 with a locking element 24.
  • the locking device 23 is interlocking between the actuator 9 and a sliding sleeve 25, which in turn the coupling device 20th and the synchronization device 21 is assigned.
  • the synchronization device 21 comprises a synchronizer ring packet with synchronizer rings, of which the outer, that is the radially outer, synchronizer ring is provided with the reference numeral 26.
  • the device 1 1 further comprises a movement device 27 or an actuating device 27 for the blocking element 24.
  • FIG. 3 shows that the synchronizing device 21 is assigned a movement device or actuating device 30.
  • the movement device or actuating device 30 comprises a ramp 28.
  • the blocking element 24 comprises a groove 32 for showing a rotationally fixed connection to the idler gear 7.
  • the groove 32 secures the locking element 24 from rotating with respect to the idler gear 7.
  • the transmission element 33 projects radially outwards from the sliding sleeve 25.
  • the device 1 1 further comprises a spring means 34 which is designed as a spring ring or as a wire form spring.
  • the spring device 34 ensures that the synchronizer rings of the synchronizer ring packet of the synchronizer 21 are applied in order to generate a slight frictional torque. This results in that the synchronizer ring 26 is rotated relative to the blocking element 24, until guide bevels, which are also referred to as actuating bevels or sloping roofs, lie axially next to one another. About this roof slopes then a large force can be transmitted to the synchronizer ring 26.
  • FIGS. 4A, 4B and 6 it can be seen that a plurality of transmission elements 33, 35 designed as a pin are provided on the sliding sleeve 25 radially on the outside.
  • a total of three transmission elements 33, 35 distributed uniformly over the circumference of the sliding sleeve 25.
  • Radially inside the sliding sleeve 25 has a spline, which serves for producing a rotationally fixed connection with the coupling body 22 of the coupling device 20.
  • the Kupplungsungskör- per 22 and the hub portion of the idler gear 7 radially outside a complementary spline.
  • the transmission elements 33 and 35 engage in recesses of the dashed line in Figures 4A and 4B indicated return member 42.
  • the recesses are equipped with return ramps 36, 37, 35 together with the transmission elements 33, 35 cause a reset of the sliding sleeve 25.
  • the blocking element 24 serves to actuate the synchronization between the actuating element 19, the planet carrier 18 and the synchronizer ring 26. Between the actuating element 19 and the blocking element 24 act ramps, which are designated in Figure 5 with 28 and 46. The blocking element 24 is secured against rotation by the transmission elements 33, 35 via the sliding sleeve 25 with respect to the idler gear 7. If the actuating element 19 is rotated relative to the idler gear 7, then the blocking element 24 is displaced axially via the ramps 28, 46 in the direction of the synchronization device 21, which is also referred to as the synchronizing device 21 in abbreviated form.
  • the spring ring 34 takes the synchronizer ring 26, until the clearance of the synchronizer ring packet is closed and the synchronizer rings abut each other.
  • the synchronizer ring 26 is rotated by a certain angle of rotation, so that the roof slopes 44 of the locking element 24 are located in front of the roof slopes or operating bevels 43 of the synchronizer ring 26.
  • the blocking element 24 designed as a blocking ring blocks the further movement of the actuating element 19.
  • the actuator 19 rotates back until the entrainment at the upper stop 39 of the recess on the return plate 42 of the actuator 27 abuts the sliding sleeve 25.
  • the sliding sleeve 25 is then withdrawn.
  • the locking element 24 is brought via the tab 49 and the ramps 48 on the return plate 29 in its initial position.
  • the synchronizing device or synchronizing device 21 has a common outer synchronizing ring 81 for the two synchronizing ring packets of the devices 11 and 12.
  • the device 11 associated with the left-hand idler 7 in FIG. 7 comprises in addition to the synchronizing device 21 and the coupling device 20 is a locking device 83.
  • the locking device 83 is combined with a transmission element 84 and cooperates with a sliding sleeve 85.
  • the sliding sleeve 85 is combined with a ball pressure piece 87, which bears against a return ramp 86 which is formed on a hub body 92 of the idler gear 7.
  • the coupling device 20 and the synchronizer 21 are shown enlarged.
  • the coupling element 88 is rotatably connected via an axial toothing with the sliding sleeve 85.
  • the transmission element 84 is arranged in the axial direction between an inner synchronizer ring 89 and the actuating element 9 of the actuating device 9 and firmly connected to the idler gear 7 at least in the circumferential direction (not visible).
  • FIGS. 9 and 10 show an actuating device or movement device 90 for the sliding sleeve 85 in an opened or closed state.
  • the movement means or actuator 90 for the sliding sleeve 85 comprises a ramp 91 of a plurality of ramps on the sliding sleeve 85.
  • the sliding sleeve 85 and the coupling element 88 have an axial toothing 95 for the rotationally fixed connection of the sliding sleeve 85 with the Coupling 88 on.
  • the coupling element 88 is rotatably connected to the shaft 2 via the coupling body 20.
  • the locking device 83 is shown with the synchronizer ring 89 in a plan view.
  • the synchronizer ring 89 is applied to a lower stop 1 13 of the transmission element 84.
  • the roof slopes or operating slopes 101 and 102 are in contact with the complementary roof slopes of the locking element 1 1 1.
  • the blocking element 1 1 1 is moved in the axial direction to the left.
  • the dashed ring ramp ring 106 with the ramp for Ansynchronmaschine 107 comes with its right face on the synchronizer ring 89 to the plant.
  • FIG 12 the moving means for Ansynchronmaschine 1 5 and the moving means for synchronizing 1 12 is shown in a partially sectioned view.
  • One of a plurality of ball thrust pieces 93 is accommodated in a bore in the plane carrier 1 18, which is firmly connected to the planet carrier 18 and forms the actuating element 19.
  • the ball of the ball pressure piece is in an initial state in one of a plurality of detents 1 17 of an actuating ring for the Ansynchronmaschine 120th
  • Ansynchron is taken from the actuator 9, here the planet carrier 18, via the ball pressure piece 93, an actuating ring for the Ansynchronmaschine 20.
  • This actuating ring 120 displaces via a ramp 107 the ramp ring 106, which is indicated transparently in FIG. 11, in the axial direction, which in turn axially displaces the synchronizer ring 89. If the Ansynchronisierkraft is reached, the ball pressure piece 93 disengages from the latch 1 17.
  • the synchronizer ring 89 has been applied to one of the stops 108 or 1 13 of the transmission element 84 depending on the effective direction of the Ansynchronisiermoments. Roof slopes or operating bevels 101 to 103 of a total of three locking elements 1 1 1 of the locking device 83 come to the operating slopes or roof slopes 104 of the synchronizer ring 89 to the plant.
  • Thieves- actuating ramp of the movement device for synchronizing 1 12 on the actuating element 19 comes to the operating ramp 1 10 of the locking element 1 1 1 to the plant.
  • the synchronizing torque is here partially supported by the roof slopes on the blocking element 11, and this in turn by the stop 108, 113 of the transmission element 84, and partially by the synchronizing ring 89 on the transmission element 84.
  • the angles of the roof slopes or operating bevels 101 to 104 are designed so that the axial counterforce generated by the synchronizing torque on the operating slopes is greater than the axial force required to generate the synchronizing torque.
  • the blocking elements 1 1 1 lock the further rotation of the actuating element 19 during the synchronization.
  • the sliding sleeve 85 has a self-opening axial toothing 95. If the coupling device 20 designed as a form-locking coupling is closed, then the sliding sleeve 85, as can be seen in FIG. 10, is locked via a plateau 98 at the end of the ramp 91.
  • FIGS. 13 to 19 show an exemplary embodiment in which the synchronization device 21 comprises two outer synchronizer rings 161, 162.
  • the synchronizer ring 161 is associated with the device 1 1 for the left idler gear 7 in FIG.
  • the synchronizer ring 162 is associated with the device 12 for the right-hand idler 8 in FIG.
  • the devices 1 1, 12 are designed substantially the same, wherein the actuation tion in the device 1 1 via the planet carrier 18 and in the device 12 via the sun gear 15 is introduced.
  • the device 1 1 comprises a sliding sleeve 164 and a locking device 165.
  • the locking device 165 comprises a blocking element 166.
  • the blocking element 166 is assigned a return device 167.
  • the return device 167 cooperates with a counter-ramp (197 in FIG. 16) on the blocking element 166.
  • a ramp 168 on the blocking element 166 interacts with a counter ramp 169 on a planetary carrier part 191.
  • a movement device or actuating device for the sliding sleeve 164 is denoted by 170 in FIGS. 13, 14 and 15. As shown in FIG. 13, the movement device 170 for the sliding sleeve 164 comprises a movement element 171 for the sliding sleeve 164.
  • a movement device for the synchronizing device or synchronization device 21 is designated by 173 in FIG.
  • An anti-rotation is designated in Figure 14 with 178.
  • a recess in the sliding sleeve 164 is designated 179 in FIG.
  • the moving element 71 of the movement device 170 for the sliding sleeve 164 comprises transmission elements 181 and 182.
  • the sliding sleeve 64 has a recess 79.
  • the planet carrier side-flank forms a return ramp 85, and the coupling body-side edge forms an actuating ramp 186.
  • the transmission elements 181, 182 of the movement element 171 engage in the groove 180 of the sliding sleeve 164.
  • a nose 183 is attached to the torque drive.
  • the nose 183 serves to represent the rotation against the planet carrier 18th
  • the positive coupling of the coupling device 20 is shown open.
  • Figure 15B the positive coupling of the coupling device 20 is shown closed and locked.
  • the planet carrier 18 is composed of a planet carrier part 191 and a planet carrier part 192.
  • Return elements 193, 194 and 195 are equipped with ramps 196 which cooperate with counter-ramps 197 on the blocking element 166.
  • the return elements 193 to 195 are fixed in rivet-like manner in the planet carrier 18 between the planet carrier part 191 and 192 with the aid of pins 199.
  • On the blocking element 166 guide slopes or sloping roofs or operating slopes 198 are provided.
  • the actuating ramps 168 provide, in cooperation with the counter ramps 169 on the planet carrier part 191 for an axial displacement of the locking element 166 in Figure 16 to the right.
  • the blocking element 166 is reset via the ramps 196 on the return elements 193 to 195 in cooperation with the counter ramps 197.
  • FIGS. 17 to 19 show how the device 12 assigned to the right-hand gearwheel 8 in FIG. 13 is actuated via the sun gear 15 as an actuating element.
  • the actuation takes place in the same manner as in the exemplary embodiment illustrated in FIGS. 5 and 16 via a movement element 225.
  • the movement element 225 interacts with a blocking device 205, which comprises a blocking element 206 with ramps 207.
  • a blocking device 205 which comprises a blocking element 206 with ramps 207.
  • guide inclines or sloping roofs 209 are provided.
  • the blocking element 206 comprises a plurality of torque supports 21 1, which engage in recesses 228 of the sliding sleeve 204 and serve to prevent rotation of the blocking element 206.
  • the tabs or transmission elements 210 are integral with the moving member 225 and this in turn firmly connected to the sun gear 15.
  • the transmission elements 210 engage in a groove 227 provided in the sliding sleeve 204.
  • FIG. 18 it can be seen that the locking device 205 is combined with a spring device 215.
  • the spring device 215 comprises three wire-form springs 216 to 218.
  • the wire-form springs 216 to 218 each have a hook-like bent end 231, 232.
  • the wire form springs 216 are arranged in the assembled state in the groove 221 in the synchronizer ring 162.
  • the nose 233 of the wire-forming spring 216 to 2 8 engages in a recess 234 of the locking element 206.
  • the nose 233 is biased radially there and thus forms a detent.
  • the locking member 206 is shown with the synchronizer ring 162 in perspective in the assembled state.
  • stops 238, 239 shown with backlash.
  • the actuator, the planet carrier 18, or the sun gear 15 is rotated relative to the idler gears 7 or 8.
  • the counter ramp 169 or 226 is rotated relative to the ramp 168 or 207 of the blocking element 166 or 206 and displaces it in the axial direction until the clearance of the synchronizing ring packet is closed.
  • the spring device 215 prevents the synchronizer ring 161 or 162 from shifting axially relative to the blocking element 166 or 206.
  • the transfer member 181, 182 or 210 of the moving member 171 or 225 moves in this phase in a portion of the groove 80 or 227 of the sliding sleeve 164 or 204, which has no slope.
  • the blocking element 166 or 206 blocks the further rotation of the actuating element. Is a synchronism of idler gear and shaft reached, then the synchronous torque drops to zero, and the actuator can be further rotated relative to the idler gear. In this case, the blocking element 166 or 206 is further displaced in the axial direction via the ramp 168 or 207, wherein the blocking element pushes further on the synchronizer ring, while the idler gear 7 or 8 on the guide slopes 198 or 209 and 220 rotates back by a small angle of rotation.
  • the wire-form springs 216 to 218 thereby snap out of the recess 234 of the locking element 66 or 206.
  • the blocking element 166 or 206 is released in the axial direction.
  • the transmission element 181, 182 or 210 of the movement element 171 or 225 reaches the area of the actuation ramp 186 in the groove 180 or 227 of the sliding sleeve 164 or 204. Further rotation of the actuation element displaces the sliding sleeve 164 or 204 in the axial direction and via the actuation ramp 186 thus creates the positive connection between idler shaft.
  • the sliding sleeve is locked by rotating the plateau 188 of the transmission element 181, 182 or the transmission element 210 into a further section of the groove 180 or 227 of the sliding sleeve 164 or 204, which has no pitch.
  • the actuator, the planet carrier 18, or the sun gear 5 is rotated relative to the idler gears 7 or 8 in the opposite direction.
  • the transmission element 181, 182 or 210 pulls the sliding sleeve 64 or 204 via the return ramp 185 in the direction of the idler gear 7 or 8.
  • the ramp 196 of the return elements 193 to 195, or the return ramp 212 in engagement with the counter ramp 197 or 229.
  • the blocking element 166 or 206 in the axial direction to the idler gear 7 or 8 is pulled.
  • the synchronizer ring 161 or 162 abuts the planet carrier member 191 or the moving member 225.
  • the wire-forming spring 216 to 218 again engages in the recess 234 of the blocking element 166 or 206.

Abstract

L'invention concerne un dispositif (11, 12) servant à synchroniser un arbre (2) et un pignon fou (7) qui est monté rotatif sur l'arbre (2), ledit dispositif comprenant un dispositif d'actionnement (9), un dispositif de synchronisation (21) et un dispositif d'accouplement (20). L'invention vise à optimiser ledit dispositif du point de vue de l'encombrement nécessaire. À cet effet, un dispositif de blocage, qui est placé de manière à exercer un effet de blocage entre le dispositif d'actionnement (9), pouvant être actionné radialement de l'extérieur par rapport au pignon fou (7, 8), et le dispositif de synchronisation (21), placé radialement à l'intérieur d'une denture d'engrènement du pignon fou (7), est logé radialement à l'intérieur de la denture d'engrènement du pignon fou (7).
EP18786665.2A 2017-10-26 2018-10-08 Dispositif et procédé de synchronisation Withdrawn EP3701162A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017125075 2017-10-26
PCT/DE2018/100830 WO2019080960A1 (fr) 2017-10-26 2018-10-08 Dispositif et procédé de synchronisation

Publications (1)

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EP3701162A1 true EP3701162A1 (fr) 2020-09-02

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EP18786665.2A Withdrawn EP3701162A1 (fr) 2017-10-26 2018-10-08 Dispositif et procédé de synchronisation

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EP (1) EP3701162A1 (fr)
CN (1) CN111527320B (fr)
DE (2) DE102018124681A1 (fr)
WO (1) WO2019080960A1 (fr)

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US11454288B2 (en) 2019-01-11 2022-09-27 Gkn Automotive Limited Actuator assembly for clutch assembly for vehicle power train
EP4050239A1 (fr) * 2021-02-24 2022-08-31 Ningbo Geely Automobile Research & Development Co. Ltd. Une unité de différentiel, un véhicule comprenant l'unité de différentiel, et un procédé pour faire fonctionner l'unité de différentiel

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DE102018124681A1 (de) 2019-05-02
CN111527320A (zh) 2020-08-11
WO2019080960A1 (fr) 2019-05-02
DE112018004976A5 (de) 2020-06-18
CN111527320B (zh) 2022-02-22

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