WO2018072786A2 - Dispositif et procédé permettant de synchroniser un arbre de transmission et deux pignons fous - Google Patents

Dispositif et procédé permettant de synchroniser un arbre de transmission et deux pignons fous Download PDF

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Publication number
WO2018072786A2
WO2018072786A2 PCT/DE2017/100876 DE2017100876W WO2018072786A2 WO 2018072786 A2 WO2018072786 A2 WO 2018072786A2 DE 2017100876 W DE2017100876 W DE 2017100876W WO 2018072786 A2 WO2018072786 A2 WO 2018072786A2
Authority
WO
WIPO (PCT)
Prior art keywords
gear
idler
synchronizing
actuating
coupling
Prior art date
Application number
PCT/DE2017/100876
Other languages
German (de)
English (en)
Other versions
WO2018072786A3 (fr
Inventor
Oswald Friedmann
Dominik Hans
Original Assignee
Schaeffler Technologies AG & 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 & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to DE112017005290.4T priority Critical patent/DE112017005290A5/de
Publication of WO2018072786A2 publication Critical patent/WO2018072786A2/fr
Publication of WO2018072786A3 publication Critical patent/WO2018072786A3/fr

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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
    • F16D23/025—Synchro rings
    • 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
    • F16D2023/0625—Details of members being coupled, e.g. 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
    • 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
    • F16D2023/0631—Sliding sleeves; 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
    • 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
    • F16D23/02—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
    • F16D2023/0681—Double cone synchromesh clutches

Definitions

  • the invention relates to an apparatus and a method for synchronizing between a transmission shaft and two idler wheels, which are rotatably mounted on the transmission shaft, with an actuating 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.
  • 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.
  • a synchronizing device for a manual transmission with a synchronizer body and at least one synchronizer ring which by means of indexing in the circumferential direction against each other can be fixed, wherein the indexing of at least one arranged on the synchronizer ring and substantially in axial projection extending 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 comprises a sliding sleeve, a synchronizer ring, a coupling body and a synchronizer body, wherein at least one inclined surface is provided on the synchronizer body and on the synchronizer ring, at those engage the synchronizer body and the synchronizer ring surface, and at least one acting between the synchronizer body and the synchronizer ring elastic element is provided which generates a circumferentially acting force that the inclined surfaces of synchronizer body and synchronizer ring press each other so that the synchronizer ring in an Direction of the synchronizer body acting force component arises.
  • the object of the invention is the switching performance in the operation of a transmission with pairs of wheels, each comprising a fixed gear and a loose wheel to represent gears in the transmission, and with a device for synchronizing between a transmission shaft and two loose wheels, rotatably mounted on the transmission shaft are, with an actuator to improve.
  • the object is achieved in a device for synchronizing between a transmission shaft and two idler wheels, which are rotatably mounted on the transmission shaft, with an actuating device, characterized in that the actuating device comprises two relatively rotatable and associated with the idler gears actuating elements with a blocking mechanism which prevents simultaneous insertion of two gears.
  • the device for synchronizing advantageously comprises a planetary gear within the idler gears of the transmission.
  • the planetary gear is preferably arranged axially between the two loose wheels.
  • a relative rotation of an actuating element of the planetary gear so for example a sun 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 one or the other idler gear is released from the stop or the stops only in each case a predetermined direction of rotation.
  • the claimed locking mechanism ensures in a simple manner that only one direction of rotation is possible. This reliably prevents unwanted simultaneous insertion of two gears.
  • a preferred embodiment of the device is characterized in that ramp-shaped stops are provided on the actuators, the rotation of the actuating elements relative to the associated idler gear only in allow one direction of rotation.
  • the ramp-shaped stops cooperate with counter-stops, which are provided on the respective associated idler gear.
  • a further preferred embodiment of the device is characterized in that over a circumference of the actuating elements a plurality of ramp-shaped stops are distributed unevenly. As a result, after a striking of the actuating element on the associated idler gear in a simple manner larger twist angle can be displayed up to a renewed striking.
  • a further preferred embodiment of the device is characterized in that the actuating elements relative to each other are axially displaceable so that an actuating element coupled to the transmission shaft idler gear prevents the simultaneous insertion of a second gear. Due to the axial displacement of the one actuating element, the other actuating element is pressed against the associated idler gear in such a way that the ramp-shaped stops engage in recesses of the associated idler gear with the counterstops.
  • the above object is alternatively or additionally achieved in that the actuating device rotatable relative to each other and two Lossonn associated actuating elements with an anti-rattle device comprises.
  • the actuators are acted upon, for example via a suitable actuator, with a preload moment.
  • a further preferred embodiment of the device is characterized in that the anti-rattle device comprises a biasing device, is biased by the at least one of the actuating elements in an axial direction.
  • the biasing device comprises, for example, a spring device.
  • the spring device comprises, for example, at least one spring which, preferably in one axial direction, is clamped between the actuator to the associated idler gear.
  • the spring device may comprise at least one spring, which is biased between the actuating device, in particular one of the actuating elements, and a stationary housing, for example a gearbox housing.
  • a further preferred embodiment of the device is characterized in that the anti-rattle device comprises a latching device which is arranged between at least one of the actuating elements and a stationary housing body. About the locking device, a desired preload torque can be generated on the actuator or the actuators.
  • a detent on the idler gear and a detent on the actuating element cooperate advantageously according to a further embodiment with a small angular offset to achieve a preload torque on a ramp of one of the two notifications together.
  • a further preferred embodiment of the device is characterized in that the anti-rattle device comprises a biasing device which is effective between at least one of the actuating elements and the associated idler gear.
  • the biasing means advantageously comprises at least one spring.
  • a synchronizing device and a coupling device are arranged overlapping in the axial direction. Due to the overlapping arrangement of the synchronizing device and the coupling device, it is possible in a simple manner to save on axial structural space.
  • a preferred exemplary embodiment of the device is characterized in that the synchronizing device and the coupling device can be actuated via a slotted guide by an actuating device.
  • the slide guide is advantageously used to convert relative rotations in axial movements, which in turn are used for synchronization between the transmission shaft and the idler gear.
  • the slotted guide advantageously comprises at least one sliding block, in particular a guide pin, which is guided in a slot, in particular a slide track or a groove.
  • the actuating device advantageously comprises a planetary gear member, which is defined rotated or pivoted to generate the relative rotation.
  • a further preferred embodiment of the device is characterized in that the coupling device comprises a coupling sleeve, which cooperates with a coupling link.
  • the coupling link advantageously comprises at least one guide groove, at least one thread and / or at least one ramp.
  • the coupling link comprises a thread and a guide groove. The thread is achieved in a simple manner, a better power distribution. However, a similarly good force distribution can also be achieved with a ramp or with a plurality of ramps distributed in the circumferential direction.
  • a further preferred exemplary embodiment of the device is characterized in that the synchronizing device comprises a synchronizing sleeve which cooperates with a synchronizing slide.
  • the Synchronisierkulisse advantageously comprises at least one guide, at least one thread and / or a ramp.
  • the synchronizing link comprises a thread and a guide groove or slide track. In the guide groove or slide track engages a sliding block, in particular a guide pin. Through the sliding block, in particular the guide pin re-threading the thread is considerably simplified.
  • Coupling sleeve and the clutch link are nested. As a result, axial space can be saved in a simple manner.
  • the coupling sleeve is advantageously arranged radially inward.
  • the synchronizing sleeve is advantageously arranged radially on the outside.
  • the coupling sleeve associated with the coupling sleeve is advantageously arranged radially therebetween, together with the synchronizing sleeve associated with the synchronizing sleeve.
  • a further preferred exemplary embodiment of the device is characterized in that the synchronizing link is thus coupled to the coupling link, the synchronizing sleeve can be displaced in the axial direction to a limited extent independently of the coupling sleeve. As a result, a stable operation of the synchronizing device in a transmission is made possible in a simple manner.
  • Another preferred embodiment of the device is characterized in that the coupling sleeve is rotatably connected to the idler gear.
  • the rotationally fixed connection is represented, for example, with at least one sliding toothing. The sliding toothing allows a simple axial movement of the coupling sleeve relative to the idler gear.
  • the transmission is preferably a dual-clutch transmission.
  • the dual-clutch transmission is preferably installed in a front-transverse arrangement in a motor vehicle, in particular in a motor vehicle having a hybrid drive.
  • 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 coupled to the transmission shaft.
  • the synchronizing movement and the coupling movement are carried out particularly advantageously in the same axial space.
  • the coupling of the idler gear with the transmission shaft is advantageously carried out via a rotation transmission element, which is also referred to as a coupling body.
  • a preferred embodiment of the method is characterized in that an actuation of the Synchronisierkulisse and the clutch linkage takes place by a relative rotation relative to the idler gear.
  • the relative rotation is advantageous haft provided by a planetary gear member of a planetary gear, which is associated with the two adjacent to the transmission shaft idler gears of the transmission.
  • the planetary gear elements are advantageously placed to save space radially within teeth of the idler gears.
  • the planetary gear elements are advantageously radially nested between the two adjacent idler gears.
  • a centrally arranged sun gear of the planetary gear is advantageously made hollow.
  • In the cavity advantageously at least one device described above is housed.
  • two devices for synchronization which are described above, are accommodated in a particularly space-saving manner.
  • a biasing torque or preload torque is applied to the idler gears to counteract undesirable noise during operation.
  • the preload torque or prestressing torque is applied, for example, by an actuator system or by a previously described anti-rattle device and / or pretensioning device.
  • the invention also relates to an actuating device, an actuating element, a blocking mechanism, a ratchet device, a prestressing device, a latching device, a synchronizing device, in particular a synchronizing sleeve and / or a synchronizing link, and / or a coupling device, in particular a coupling sleeve and / or a coupling device Coupling link, for a previously described device for synchronization.
  • the parts mentioned are separately tradable.
  • FIG. 1 shows a conventional device for synchronizing
  • Figure 2 is a schematic representation of an axially short device for
  • Figure 18 is a perspective view of an actuating element
  • FIG. 12 is a diagrammatic representation of FIG. 12
  • FIG. 19 is a perspective view of a loose-wheel assigned to the actuating element from FIG. 18;
  • Figure 20 is an exploded view of two idler gears with an actuator and the locking mechanism or locking mechanism;
  • Figure 21 is a similar exploded view as in Figure 20 additionally with a transmission output shaft;
  • Figure 22 is a similar view as in Figure 12 with an additional
  • Anti-rattle device and an additional locking device and Figure 23 shows a loose wheel with an actuating device and an additional spring device in half section.
  • a device 10 for synchronizing between a transmission shaft and a loose wheel, which is rotatably mounted on the transmission shaft shown greatly simplified.
  • the device 10 comprises two sub-devices 1 1, 12, which are radially interleaved and arranged overlapping in the axial direction.
  • the axial direction corresponds to a horizontal line in FIG.
  • the sub-device 1 1 is combined with a synchronizer 15.
  • the sub-device 12 is combined with a coupling device 16.
  • the synchronizer 15 and the coupling device 16 are also radially interleaved and arranged overlapping in the axial direction.
  • An actuating path during synchronization is indicated in FIG. 2 by an arrow 17.
  • an actuating path during coupling is indicated in Figure 2.
  • the corresponding displacements of the sub-devices 1 1, 12 during synchronization and coupling are indicated in Figure 2 by dashed lines.
  • FIG. 1 also shows in principle a conventional device 20 for synchronization for comparison with FIG.
  • the device 20 comprises a synchronizing device 25 and a coupling device 26.
  • the synchronizing device 25 is spaced apart from the coupling device 26 in the axial direction.
  • an arrow 27 an actuating path during synchronization is indicated.
  • an arrow 28 an actuating path during coupling is indicated.
  • a sliding sleeve is first moved axially, wherein the sliding sleeve presses first on a synchronizer ring. Once a synchronism of a loose wheel and a gear shaft is reached, the sliding sleeve can be pushed over the synchronizer ring on a coupling body.
  • a device 30 for synchronization is shown in more detail than in Figure 2, but still simplified.
  • the device 30 serves to synchronize between a gear shaft 31 and a loose wheel 32.
  • the idler gear 32 is rotatably mounted on the gear shaft 31 by means of a bearing device 33.
  • An actuating device 35 for actuating the device 30 advantageously comprises a planetary gear element of a planetary gear (not shown in Figure 3).
  • the device 30 comprises a synchronizer ring package 40, a synchronizer 41 and a coupling device 42.
  • the synchronizer 41 and the coupling device 42 are arranged axially overlapping and radially nested.
  • a sliding block 43 is provided radially inwardly of the synchronizer 41.
  • a sliding block 44 is provided radially on the outside of the coupling device 42.
  • the term axially refers to an axis of rotation 49 of the transmission shaft 31 within the scope of the claimed device 10, 30.
  • the transmission shaft 31 is a transmission output shaft of a gear equipped with the idler gear 32.
  • FIG. 5 roof pitches or guide bevels 51, 52 are indicated on the synchronizer 41 and on the synchronizer ring packet 40.
  • 31 sloping slopes or guide slopes 53, 54 are indicated on the coupling device 42 and the transmission shaft.
  • a spring ring between the synchronizer 41 and the synchronizer ring packet 40 is indicated by a circle 55.
  • a synchronizing ring of the synchronizing ring package 40 can rotate relative to the synchronizing device 41 by the width of a roof slope or guide bevel 51, 52 and thus prevent a further displacement of the synchronizing device 41.
  • the synchronizer 41 rotates a synchronizer ring of the synchronizer ring packet 40 back and shifts further in the axial direction, but only by the amount of a wear reserve.
  • the coupling device 42 can be pushed onto a rotary transmission element 58, which is also referred to as a coupling body.
  • the rotation transmission element 58 is integrally connected in Figure 5 with the transmission shaft or transmission output shaft 31.
  • the axial movements of the synchronizer 41 and the coupling device 42 are controlled by the slide guide (45 in Figure 6).
  • the slide guide 45 in Figure 6
  • pins are attached to the synchronizer 41 and the coupling device 42, which engage in the guide grooves or cam tracks 46, 47 of the slide guide 45.
  • a transmission 60 with an inner transmission input shaft 61 and an outer transmission input shaft 62 is shown partially in section.
  • an output stage 65 is arranged to a differential (not shown).
  • the power amplifier 65 is referred to as Final Drive.
  • the transmission 60 On its right side in FIG. 7, the transmission 60 has two bearing points 66, 67. At the transmission output 64, the transmission 60 has a bearing journal 68. On the inner transmission input shaft 61 two fixed wheels 73, 74 are arranged. On the outer transmission input shaft 62, two fixed wheels 71, 72 are arranged.
  • the fixed gear 71 meshes, for example, to illustrate a first gear, with a loose wheel 75.
  • the fixed gear 72 meshes, for example, to represent a third gear, with a loose wheel 76.
  • the fixed gear 73 meshes, for example, to display a second gear, with
  • the idler gear 74 meshes, for example, to illustrate a fourth gear, with a loose wheel 78.
  • the idler gears 75 to 78 are rotatably mounted by means of suitable storage facilities on a transmission output shaft 80, which is also referred to as transmission shaft 80 shortened.
  • the idler gears 75, 76 represent a first idler gear pair.
  • the idler gears 77, 78 represent a second idler gear pair.
  • the first idler gear pair 75, 76 are associated with two devices 81, 82 for synchronization.
  • the idler gear 77, 78 are associated with corresponding devices which are actuated by an actuator 86.
  • the actuator 85 includes a planetary gear 84.
  • the planetary gear 84 is disposed in a cavity radially inwardly and axially between the adjacent idler gears 75, 76. By the planetary gear 84, the axial space can be reduced via the actuator 85 in the transmission.
  • the planetary gear 84 includes a ring gear 87, a sun gear 90 and planetary gears 91, 92 (see Figure 1 1).
  • the planet gears 91, 92 are rotatably mounted on a planet carrier 93 with a web.
  • the sun gear 90 meshes with the planet gears 91, 92, which in turn mesh with the ring gear 87.
  • the planet carrier 93 with the web rotates in the unactuated state of the devices 81, 82 substantially synchronously with the idler gear 75.
  • the sun gear 90 rotates in the unactuated state of the devices 81, 82 substantially synchronously with the idler gear 76th
  • substantially synchronous in this context also means that the sun gear 90 and the planet carrier 93 can rotate with the web after actuation by the actuator 85 to a limited extent relative to the idler gears 75, 76 to provide a clutch, shift - and / or synchronizing to trigger.
  • the ring gear 87 Upon actuation of the actuator 85, the ring gear 87 is rotated. In the unactuated state of the actuator 85, the ring gear 87 is fixed. Then the ring gear 87 has the same speed as the gear 60, which is fixed. Thus, the ring gear 87 in the unactuated state of the actuator 85 has a speed of zero.
  • the idler gear 75 is rotatably supported by a bearing device 88 on the transmission output shaft 80.
  • the idler gear 76 is rotatably supported by a bearing device 89 on the transmission output shaft 80.
  • the planet carrier 93 with the web is coupled by a coupling element 94 to the device 81.
  • the coupling element 94 is part of the planetary carrier 93, which is also referred to as a web.
  • the sun gear 90 is coupled to the device 82 via a coupling element 95.
  • a rotation transmission element 98 is rotatably connected via a spline 101 to the transmission shaft 80.
  • the spline 101 which is also referred to as a toothing 101 shortened, allows torque transmission between the transmission shaft 80 and the rotation transmission member 98, and vice versa.
  • the rotation transmission member 98 is radially outwardly at its ends with guide slopes 99, 100 equipped.
  • the guide bevels 99, 100 cooperate with complementary guide bevels, which will be explained below.
  • the guide bevel 99 is associated with the left in Figure 8 device 81.
  • the guide slope 100 is assigned to the device 82 arranged on the right in FIG.
  • the rotational transmission member 98 which may also be referred to as a coupling body, extends radially outwardly into a cavity which is recessed between the two idler gears 75, 76. Radially outward, the rotation transmission element 98 between the guide slopes 99, 100 a toothing 102, which is also designed as a sliding toothing.
  • synchronizer rings 121, 131 of synchronizer ring packets 120, 130 mounted in the sliding teeth 102 radially outwardly arranged synchronizer rings 121, 131 of synchronizer ring packets 120, 130 mounted.
  • a torque transmission between the rotation transmission member 98 and the outer synchronizer rings 121, 131 allows, and vice versa.
  • An axial displacement of the outer synchronizer rings 121, 131 relative to the rotation transmission element 98 is prevented by a retaining ring, in particular a spring ring or detonator ring, and axial abutment surfaces on the rotation transmission element or coupling body 98.
  • axial refers to an axis of rotation 103 of the gear shaft 80 or of the loose wheels 75, 76.
  • Axial means in the direction or parallel to the axis of rotation 103.
  • radially extends transversely to the axis of rotation 103.
  • the devices 81, 82 are particularly space-saving in the cavity between the idler gears 75, 76 housed. Only the actuating device 85 for the two devices 81, 82 protrudes radially outward out of the cavity between the idler wheels 75, 76. As a result, a cooperation of the actuating device 85, in particular the ring gear 87 of the planetary gear 84, with a corresponding actuator device, for example a gear, which is driven by an electric motor, in a simple manner allows.
  • the devices 81, 82 each comprise a synchronizing device 104, 106 and a coupling device 105, 107. The device 81 with the synchronizing device 104 and the coupling device 105 arranged on the left in FIG.
  • the device 82 with the synchronizing device 106 and the coupling device 107 arranged on the right in FIG. 8 is assigned to the idler gear 76 likewise arranged on the right in FIG.
  • the synchronizers 104, 106 and the coupling devices 105, 107 are combined with slotted guides 108, 109.
  • the slide guides 108, 109 serve to convert relative rotations defined into axial movements, which are used to synchronize and couple or couple the respective idler gear 75, 76 with the gear shaft 80.
  • the coupling devices 105, 107 each comprise a coupling sleeve 1 10, 1 12 and a coupling link 1 1 1, 1 13.
  • the synchronizers 104, 106 each comprise a synchronizing sleeve 1 14, 1 16 and a synchronizing linkage 1 15, 1 17.
  • the coupling sleeve 1 10, the clutch link 1 1 1, the synchronizing sleeve 1 14 and the Synchronisierkulisse 1 15 of the left in Figure 8 arranged device 81 are radially interleaved and arranged overlapping in the axial direction.
  • the coupling sleeve 1 12, the clutch linkage 1 13, the synchronizing sleeve 1 16 and the synchronizing linkage 17 of the device 82 arranged on the right in FIG. 8 are likewise radially interleaved and arranged in an overlapping manner in the axial direction.
  • the synchronizer ring packets 120, 130 each comprise a total of four synchronizer rings 121 to 124, 131 to 134.
  • the synchronizer rings 121 to 124 of the device 81 arranged on the left in FIG. 8 are arranged radially outside the synchronizer 104 and the clutch device 105. However, the synchronizer rings 121 to 124 are arranged in the axial direction overlapping the clutch device 105 and the synchronizer 104.
  • the synchronizer rings 131 to 134 of the device 82 arranged on the right in FIG. 8 are arranged radially outside the synchronizing device 106 and the coupling device 107. However, the synchronizer rings 131 to 134 are arranged axially overlapping with the synchronizer 106 and the clutch device 107.
  • the radially outer synchronizer rings 121, 131 are in the middle between the devices 81, 82 to each other and engage together in the teeth 102 of the rotation transmission member 98 a.
  • the radially inwardly arranged synchronizer rings 124, 134 of the synchronizer ring packets 120, 130 are, as will be explained below, with the synchronizing sleeves 1 14, 1 16 coupled.
  • a spring means in the form of a spring ring 1 18, 1 19 arranged.
  • the spring means with the spring rings 1 18, 1 19 serve to synchronize, as will be explained below.
  • radially inward guide elements 140 are provided on the radially inner synchronizer ring 134 of the synchronizer ring packet 130 .
  • the guide elements 140 each have two guide slopes 141, 142.
  • complementary trained guide elements 145 each with two guide slopes 146, 147 are provided.
  • the guide elements 140 on the radially inner synchronizer ring 134 are designed as projections which project radially inwards.
  • the guide elements 145 on the synchronizing sleeve 1 16 are designed as recesses in the synchronizing sleeve 1 16, which are open in Figure 9 on their left side.
  • the synchronizing sleeve 16 has a total of four anti-rotation elements 151 to 154.
  • the anti-rotation elements 151 to 154 extend in the axial direction.
  • the coupling sleeve 1 12 has on its right in Figures 9 and 10 page four Umgriffe 155 to 158 on.
  • the Umgriffen 155 to 158 of the coupling sleeve 1 12 are arranged in the circumferential direction between one of the anti-rotation elements 151 to 154 of the synchronizing sleeve 1 16 and one of the driving elements 161 to 164 of the Synchronisierkulisse 1 17.
  • a guide pin 166 is further attached.
  • the guide pin 166 is radially inwardly from the Synchronisierkulisse 1 17 from that he engages in a slide track, which, as seen in Figure 10, outside of the synchronizing sleeve 1 16 is combined with an external thread 171.
  • a complementary trained internal thread 172 is formed radially inwardly of the Synchronisierkulisse 1 17.
  • the external thread 171 is delimited on the synchronizing sleeve 16 on the right-hand side in FIG. 10 by a slide track 173 which, in contrast to the outside wind 171 has no slope.
  • a slide track 173 which, in contrast to the outside wind 171 has no slope.
  • guide pin 166 threading the threads 171, 172 is simplified.
  • the threads 171, 172, together with the guide track 173 and the guide pin 166 166 form part of the slide guide 109.
  • the slide guide 109 may alternatively or additionally include ramps.
  • an external thread 175 is provided, which cooperates with a complementary internal thread 176, which is provided on the coupling link 1 13.
  • a complementary internal thread 176 is provided on the coupling link 1 13.
  • FIG. 11 shows the transmission shaft 80 with the two idler wheels 75, 76, with the Final Drive 65 and with the two devices 81, 82 accommodated between the idler wheels 75, 76 for synchronization in an exploded view.
  • the devices 81, 82 are actuated via the ring gear 87 of the planetary gear.
  • the ring gear 87 has a toothing on the outside.
  • a rotary input via the planetary gear 84 is actuated by the planet carrier 93.
  • the right-hand device 82 for synchronization is actuated by the sun gear 90 of the planetary gear 84.
  • the coupling sleeve 1 10, 1 12 and the respective synchronizing sleeve 1 14, 1 16 are secured on the associated idler gear 75, 76 against rotation. If, for actuation, the planet carrier 93 or the sun gear 90 is rotated relative to the idler gear 75, 76, the synchronizing sleeve 1 14, 1 16 is moved axially in the direction of the radially inner synchronizing ring 124, 134 via the slotted guides 108, 109 and the threaded lamps.
  • the spring ring 1 18, 1 19 initially provides for an axial contact pressure of the radially inner synchronizer ring 124, 134, so that the radially inner synchronizer ring 124, 134 can rotate within a limited circumferential clearance.
  • This is also called Ansynchron equation.
  • the guide bevels 141, 142 on the radially inner synchronizer ring 124 come to lie in front of the guide bevels 146, 147 of the synchronizing sleeve 1 16 during the synchronization.
  • the synchronizing sleeve 16 presses the radially inner synchronizing ring 124 via the guide bevels 146, 147 and 141, 142.
  • An arrow 182 indicates in FIG. 9 that the anti-rotation elements 151 to 154 on the synchronizing sleeve 161 prevent the synchronizing sleeve 16 from being twisted during rotation. By the anti-rotation elements 151 to 154, the synchronizing sleeve 1 16 is practically held.
  • FIG. 12 shows a similar detail as in FIG. 8 with a blocking mechanism 207.
  • the coupling element 94 represents a left-hand actuating element of the actuating device 85 in FIG. 12.
  • the coupling element 95 represents a right-hand actuating element of the actuating device 85 in FIG. 12.
  • the actuating element 94 is assigned the idler gear 75 on the left in FIG.
  • the actuating element 95 is associated with the right idler gear 76 in FIG.
  • FIG. 13 the view of a section along a line 200 in FIG. 12 is shown enlarged, with arrows 201, 202 indicating the viewing direction.
  • the actuating device 85 is designed as an actuating wheel 205 with an external toothing.
  • An inner portion 206 of the idler gear 76 is shown broken away in the illustrated sectional view to make the blocking mechanism 207, also referred to as a locking mechanism, visible.
  • the blocking mechanism or locking mechanism 207 comprises on the actuating element 95 a ramp-shaped stop 208 with a ramp 210.
  • the ramp-shaped stop 208 of the actuating element 95 interacts with a counter-stop 209 in the form of a recess in the inner region 206 of the idler gear 76 ,
  • the interaction between stop 208 and counter-stop 209 is illustrated in FIGS. 14 to 17.
  • the actuators 94, 95 of the synchronizers, here planet carrier or sun with the same rotational speed as the respective idler gears 75, 76.
  • Between the actuators 94, 95 and the idler gears 75, 76 are Stops for both directions of rotation.
  • the right-hand actuator 95 can not escape.
  • the left actuator 94 must therefore drive over the ramp-shaped stop. In this case, the left actuating element 94 displaces in the axial direction by the width of the stop covering, as indicated in FIG. 14 by arrows 21 1, 212.
  • the mutually facing end faces of the actuating elements 94, 95 approach each other.
  • the relative rotation between the actuator 94 and the idler gear 75 is used to actuate the synchronization and engage the gear.
  • the operating wheel 205 is rotated in the opposite direction. Accordingly, the torsional moments in the actuators 94, 95 now also act in the other direction. Now it must be achieved that the first gear is laid out, and not the other gear is additionally inserted.
  • arrows 124, 215 symbolize the peripheral force or the torque in the actuating elements 94, 95.
  • the torque is supported on the ramp-shaped stop 208 or counter-stop 209.
  • the axially displaced left actuating element 94 prevents the right-hand actuating element 95 from being able to drive over the ramp-shaped stop 210, since the two facing end faces of the actuating elements 94, 95 touch each other.
  • the actuator 95 and the idler gear 76 are shown in perspective.
  • double arrows 218 to 220 indicate that stops 221, 222, 223 and 208 are distributed unevenly over a circumference of actuating element 95.
  • a possibly largest possible angle of rotation on the actuating element 95 can be achieved in an advantageous manner, for example one hundred and eighty degrees, which leads to lower tooth forces on the planet.
  • FIG. 20 and 21 show the construction in exploded views.
  • an inner region 226 of the idler gear 75 is provided with counterstops 229 in the same manner as the inner region 206 of the idler gear 76.
  • FIG. 21 shows the associated ramp-shaped stops 228 with the ramps 230 on the actuating element 94, which is associated with the idler gear 75.
  • FIG. 22 shows a similar detail as in FIG. 12 with a latching device 238 and an anti-rattle device 244.
  • the anti-rattle device 244 comprises a biasing device 233, by which the actuating element 95 is biased against the associated idler gear 76 in the axial direction.
  • the biasing device 233 comprises a plate-spring-like spring 234.
  • the spring 234 is radially outwardly supported on a support ring 235, which in turn engages in an annular groove of the idler gear 76.
  • the spring 234 is supported radially inwardly on a support structure 236 which is provided on the actuating element 95.
  • a preload torque is, for example, by an unillustrated Ak- tormotor applied to the actuator 205.
  • the preload torque is supported via the actuating element 205 and the anti-rattle device 244 on the idler gear 76 or via a suitable stop on the idler gear 75.
  • the preload torque may be generated by a detent mechanism 238, also referred to as detent 238.
  • the latching device 238 comprises a latching body 239, which essentially has the shape of a spherical section.
  • the locking body 239 engages in a complementarily shaped recess in the actuating wheel 205 of the actuating device 85.
  • a spring 240 of the locking body 239 is biased against the actuating wheel 205.
  • the spring 240 is supported on a fixed housing (not shown in FIG. 22).
  • An icon to the left of the actuating wheel 205 indicates in FIG. 22 that the actuating wheel 205 can not move to the left in the axial direction.
  • the latching device comprises at least one not shown Rast michsrampe and / or inclined surface.
  • the position of the Rast michsrampe and / or the inclined surface is selected so that the locking body 239 rests in the circumferential direction of the Rastie- rungsrampe or the inclined surface when the anti-rattle device 244 and the biasing means 233 the ramp-shaped stop 208 and the counter-stop 209 together.
  • FIG. 23 shows a pretensioning device 245.
  • the biasing device 245 includes a spring 246 which is attached with its free ends on the idler gear 76.
  • the spring 246 has a centrally projecting nose 247 in FIG.
  • the nose 247 engages in a recess 248, which is recessed in the actuating element 95.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un dispositif servant à synchroniser un arbre de transmission et deux pignons fous (75, 76), montés de manière à pouvoir tourner sur l'arbre de transmission, comportant un système d'actionnement (85). L'invention est caractérisée en ce que le système d'actionnement (85) comprend deux éléments d'actionnement (95) associés aux pignons fous (75, 76), pouvant tourner l'un par rapport à l'autre et comportant un mécanisme de blocage (207) qui empêche le passage simultané de deux rapports.
PCT/DE2017/100876 2016-10-21 2017-10-16 Dispositif et procédé permettant de synchroniser un arbre de transmission et deux pignons fous WO2018072786A2 (fr)

Priority Applications (1)

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DE112017005290.4T DE112017005290A5 (de) 2016-10-21 2017-10-16 Vorrichtung und Verfahren zum Synchronisieren zwischen einer Getriebewelle und zwei Losrädern

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DE102016220709 2016-10-21
DE102016220709.1 2016-10-21

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019114856A1 (fr) * 2017-12-13 2019-06-20 Schaeffler Technologies AG & Co. KG Boîte de vitesses et dispositif de changement de vitesses pour assurer le passage de rapports de la boîte de vitesses

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19982494C1 (de) 1998-11-23 2003-05-22 Ina Schaeffler Kg Anordnung und Ausführung von Synchronringen als spanlos geformte Blechteile
DE102009027438A1 (de) 2009-07-03 2011-01-05 Zf Friedrichshafen Ag Synchronisierung für ein Schaltgetriebe
DE102010002932A1 (de) 2010-03-17 2011-09-22 Zf Friedrichshafen Ag Synchronisierung

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Publication number Priority date Publication date Assignee Title
DE10101864B4 (de) * 2001-01-17 2016-03-31 Zf Friedrichshafen Ag Schaltvorrichtung eines Getriebes
JP5580217B2 (ja) * 2011-01-07 2014-08-27 Ｎｔｎ株式会社 車両用モータ駆動装置および自動車
GB2538695A (en) * 2014-10-10 2016-11-30 Qinetiq Ltd Gearbox improvements
CN105889481B (zh) * 2015-02-16 2017-08-22 博格华纳公司 在运动中切换档位的机电变速箱

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19982494C1 (de) 1998-11-23 2003-05-22 Ina Schaeffler Kg Anordnung und Ausführung von Synchronringen als spanlos geformte Blechteile
DE102009027438A1 (de) 2009-07-03 2011-01-05 Zf Friedrichshafen Ag Synchronisierung für ein Schaltgetriebe
DE102010002932A1 (de) 2010-03-17 2011-09-22 Zf Friedrichshafen Ag Synchronisierung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019114856A1 (fr) * 2017-12-13 2019-06-20 Schaeffler Technologies AG & Co. KG Boîte de vitesses et dispositif de changement de vitesses pour assurer le passage de rapports de la boîte de vitesses

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WO2018072786A3 (fr) 2018-06-21
DE112017005290A5 (de) 2019-07-18

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