EP3707402A1 - Arrangement de changement de rapport pour une boîte de vitesses - Google Patents

Arrangement de changement de rapport pour une boîte de vitesses

Info

Publication number
EP3707402A1
EP3707402A1 EP18806967.8A EP18806967A EP3707402A1 EP 3707402 A1 EP3707402 A1 EP 3707402A1 EP 18806967 A EP18806967 A EP 18806967A EP 3707402 A1 EP3707402 A1 EP 3707402A1
Authority
EP
European Patent Office
Prior art keywords
gear
rotatably mounted
transmission element
housing
transmission
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Withdrawn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
EP18806967.8A
Other languages
German (de)
English (en)
Inventor
Burkhart Breinesberger
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.)
AVL Commercial Driveline and Tractor Engineering GmbH
Original Assignee
AVL Commercial Driveline and Tractor Engineering GmbH
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 AVL Commercial Driveline and Tractor Engineering GmbH filed Critical AVL Commercial Driveline and Tractor Engineering GmbH
Publication of EP3707402A1 publication Critical patent/EP3707402A1/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Withdrawn legal-status Critical Current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
    • 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
    • F16H3/78—Special adaptation of synchronisation mechanisms to these gearings
    • 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
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • 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
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • 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
    • 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
    • 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
    • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
    • 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
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/34—Locking or disabling mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/38—Detents
    • 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
    • F16D67/00—Combinations of couplings and brakes; Combinations of clutches and brakes
    • F16D67/02—Clutch-brake combinations
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one sets of orbital 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means

Definitions

  • the invention relates to a switching device for a transmission, in particular for a planetary gear with at least one rotatably mounted transmission element, at least one housing-fixed transmission element, with at least one braking device for holding the at least one rotatably mounted transmission element, wherein the braking device comprises a sliding sleeve, which rotatably, but - with respect to an axis of rotation of the at least one rotatably mounted transmission element - axially slidably connected to a transmission element of the transmission, and wherein in a first switching position of the sliding sleeve, a rotatably mounted first transmission element rotatably connected to the housing-fixed transmission element and rotatable in a second switching position of the sliding sleeve mounted first gear element is separated from the housing-fixed gear element.
  • a transmission system with a designed as Ravigneaux planetary gear planetary gear is known, which a small sun gear, a large sun gear, a planet carrier with a first planetary gear set and a second planetary gear set, and a ring gear known, the small sun gear with the first planetary gears of the first planetary gear set, the first planetary gears with second planetary gears of the second planetary gear set, and the second planetary gears with the large sun gear and the ring gear are in meshing engagement.
  • the large sun gear can be held on a first brake and the planet carrier via a second brake.
  • the US 2,582,487 A describes a gear arrangement with a planetary gear, wherein either a rotatably mounted first gear element or a rotatably mounted second gear element held on a sliding sleeve, so it can be connected to a housing-fixed gear element.
  • the sliding sleeve is axially displaceable on its outer jacket and rotatably guided in the gear housing.
  • a synchronizer is not provided, which is why the gear assembly is particularly suitable for standstill circuits.
  • the documents DE 198 06 031 AI and EP 0 086 875 AI disclose synchronizer with switching devices in which a first shaft can be connected by means of a sliding sleeve either with a second or third shaft.
  • the object of the invention is to allow with the least possible effort and in a compact manner, at least two switching positions in a planetary gear of the type mentioned.
  • the braking device has at least one first synchronizer ring, which cooperates via a first friction surface with a corresponding first mating surface of a first rotatably mounted with the rotatably mounted first gear element or the housing-fixed gear element first clutch body, and / or the braking device at least a second Synchronizer ring which cooperates via a second friction surface with a corresponding second mating surface of a rotatably mounted with the rotatably mounted second transmission element second coupling body, wherein adjacent to at least one coupling body via the sliding sleeve with the housing rotatably connected synchronizer body is arranged.
  • a transmission element is understood here as an element of the transmission, which is necessary to change torque, speed and / or direction of rotation between a drive and an output.
  • rotating elements for example, coupling partners of waves or in the case of a planetary gear, for example sun gear, planet carrier and ring gear - as well as housing-fixed elements which exert reaction forces during braking or holding a rotatable element on this.
  • the housing-fixed transmission element is either attached to the housing of the transmission or formed integrally therewith.
  • the fact that a rotatably mounted gear element is separated from the housing-fixed gear element means according to the invention that the rotatably mounted gear element is rotatable relative to the housing.
  • the synchronizer body is rotatable relative to the first and / or second transmission element. It is preferably provided that the synchronizer body is rotatably mounted on the rotatably mounted first or rotatably mounted second transmission element.
  • the sliding sleeve can be easily switched between a first switching position and a second switching position, wherein in the first switching position, the rotatably mounted first transmission element is braked or held.
  • a first variant of the invention according to the invention provides that in the first switching position a rotatably mounted second transmission element is separated from the housing and in the second switching position, the second transmission element rotatably connected to the housing-fixed transmission element.
  • the sliding sleeve is rotatably, but - in relation to a rotation axis of at least one rotatably mounted gear element - axially slidably connected to the housing-fixed gear member.
  • the rotatably mounted first gear element is rotatably connected to the housing-fixed gear element and the rotatably mounted second gear element separated from the housing.
  • the second switching position of the sliding sleeve the rotatably mounted first gear element is separated from the housing-fixed gear element and the rotatably mounted second gear element rotatably connected to the housing-fixed gear element.
  • a neutral position is formed between the first and the second switching position of the sliding sleeve, in which neither the rotatably mounted first nor the rotatably mounted second transmission element is braked or held. In the neutral position, the rotatably mounted first gear element and the rotatably mounted second gear element are thus completely separated from the housing.
  • the sliding sleeve via at least one synchronizer ring with the rotatably mounted first transmission element or the rotatably mounted second transmission element and the housing-fixed transmission element is fverbindbar.
  • the synchronizer ring allows in a simple manner and with minimal space brake or holding the rotatably mounted first gear element or the rotatably mounted second of the transmission element.
  • disposed on a side facing away from the first coupling body side of the first synchronizer ring and adjacent to this and / or on a side facing away from the second coupling body side of the second synchronizer ring and adjacent to this via the sliding sleeve connected to the housing synchronizer body is.
  • the synchronizer prevents the sliding of the shift sleeve as long as no synchronization of the speed of the coupling body and the shift sleeve is achieved, so long as the clutch body does not stand still.
  • the synchronizer body is conveniently arranged between the first and the second clutch body and preferably rotatably mounted on the rotatably mounted first transmission element.
  • the rotational speed of the rotatably mounted first or rotatably mounted second transmission element is reduced.
  • the slide sleeve is further axially displaced via synchronizer ring and coupling body, wherein an internal toothing of the slide sleeve engages in external teeth of the synchronizer ring and the coupling body.
  • the second coupling body is rotatably mounted on the first gear element or on the housing-fixed gear element.
  • a particularly compact and easily assembled design can be achieved if the braking device and the transmission are formed as a unit, wherein preferably the braking device is integrated in the planetary gear set.
  • the transmission may for example be a planetary gear with at least one rotatably mounted first gear element, at least one rotatably mounted second gear element and at least a third gear element from the group sun gear, planet carrier and ring gear.
  • the planetary gear as Ravigneaux planetary gear with a first sun gear, a second sun gear, a planetary gear carrier with a first planetary gear having first planetary gear and a second planetary gear having second planetary gear and a ring gear, is formed the first sun gear with the first planetary gears, the first planetary gears with second planetary gears, and the second planetary gears with the second sun gear and the ring gear are in meshing engagement.
  • the second sun gear may have a larger diameter than the first sun gear.
  • the rotatably mounted first gear element is formed by a sun gear - preferably the second sun gear - and the rotatably mounted second gear element by a planet carrier.
  • FIG. 1 shows a planetary gear with a switching device according to the invention in a first embodiment in an oblique view.
  • Fig. 2 is a transmission diagram for a known transmission arrangement
  • FIG. 4 shows the planetary gear of FIG. 1 in a detailed view of the switching element device according to the invention
  • FIG 5 shows the switching device of the planetary gear in a first switching position.
  • FIG. 6 shows the switching device of the planetary gear in a second switching position.
  • FIG. 8 shows a switching device according to the invention in a second embodiment in a longitudinal section
  • Fig. 9 shows a switching device according to the invention in a third embodiment in a longitudinal section.
  • planetary gear 1 shows a gear arrangement 10 with a planetary gear 1 designed as a Ravigneaux planetary gear, which has the gear elements first sun gear 2, second sun gear 3, planet wheel carrier 4 and ring gear 5.
  • the Planet carrier 4 has a first planetary gear set with first planetary gears 6 and second planetary gear set with second planetary gears 7.
  • first sun gear 2 is in meshing with the first planet gears 6.
  • the first planetary gears 6 are connected to the second planetary gears 7, and the second planetary gears 7 to the second sun gear 3 and the ring gear 5 in meshing engagement.
  • the ring gear 5 is connected to an output 12.
  • reference numeral 8 is a fixed housing, and designated by reference numeral 80 a housing-fixed gear member, which may be formed integrally with the housing, for example.
  • reference numeral 80 a housing-fixed gear member, which may be formed integrally with the housing, for example.
  • at least one rotatably mounted gear member 30, 40 are braked or held.
  • the second sun gear 3 is also referred to here as a rotatably mounted first gear element 30 and the planet carrier 4 as a rotatably mounted second gear element 40.
  • the second sun gear 3 has a larger diameter than the first sun gear 2.
  • the planet gears 6, 7 of the planetary gear 1 are about axes parallel to the axes of rotation 2a, 3a of the first sun gear 2 and the second sun gear 3 and the axes of rotation 30a, 40a of rotatably mounted first gear member 30 and rotatably mounted second gear member 40 rotatably supported.
  • Fig. 2 shows schematically a transmission diagram for a known gear assembly 110 with a, a Ravigneaux planetary gear forming planetary gear 101, the transmission elements via clutch devices Kl, K2, K3 and brakes Bl, B2 a braking device 13 can be switched.
  • the drive 111 can be connected to the planet carrier 104 via the first clutch device K1, via the clutch device K2 to the first sun gear 102, and via the clutch device K3 to the second sun gear
  • the second sun gear 103 are drive-connected. About the first brake Bl, the second sun gear 103 is held and on the second brake B2 of the planet
  • the brakes Bl, B2 of the brake device 13 are formed with synchronizing rings 24, 25.
  • a sliding sleeve 14 is provided which rotatably, but - with respect to the axis of rotation 3a of the second sun gear 3 - axially slidably connected to the housing 8 of the planetary gear 1 is connected.
  • a first switching position S1 of the sliding sleeve 14 formed, for example, by a first end position, a rotatably mounted first gear element 30 - in the present case the second sun gear 3 - is connected in a rotationally fixed manner to the housing 8 and a rotatably mounted second gear element 40 - in the present case the planet carrier 4 - Separated from the housing 8.
  • a second switching position S2 of the sliding sleeve 14 formed, for example, by a second end position, the rotatably mounted first gear element 30 - here the second sun gear 3 - is separated from the housing 8 and the rotatably mounted second gear element 40 - in this case the planet carrier 4 - is rotationally fixed to the housing Housing 8 connected.
  • the sliding sleeve 14 has in the region of its outer jacket 15 at least partially outer teeth 16 which engages in a corresponding internal toothing 17 of the housing 8 and axially - ie parallel to the axes of rotation 30a, 40a of the first and second gear element 30, 40 -. Slidably is.
  • a substantially annular synchronizer body 18 is arranged, which is rotatably connected via an external toothing 19 with an internal toothing 20 of the sliding sleeve 14.
  • the synchronizer body 18 is rotatably supported on the second sun gear shaft 3b of the second sun gear 3 via a bearing 21 and disposed between a first clutch body 22 and a second clutch body 23.
  • the second sun gear shaft 3b is rotatably supported via bearings 28 on the first sun gear 2b, the first sun gear 2b supported by bearing 29 in the housing 8.
  • the first clutch body 22 is rotatably connected to the sun gear 3b of the second sun gear 3.
  • the second coupling body 23 is rotatably connected to the planet carrier 4.
  • first synchronizer ring 24 Between the first clutch body 22 and the synchronizer body 18, a first synchronizer ring 24, between the second clutch body 23 and the synchronizer body 18, a second synchronizer ring 25 is rotatably arranged.
  • Each first 24 or second synchronizer ring 25 has on its inside a conically shaped first friction surface 24a and second friction surface 25a, which cooperates with a corresponding conically shaped outer counter surface 22a, 23a of the first 22 and second clutch body 23.
  • the sliding sleeve 14 can only after synchronization of the corresponding synchronizer ring 24, 25 and the corresponding coupling body 22, 23 via the corresponding external teeth 24b, 25b of the first 24 and second synchronizer ring 25 and the external teeth 22b 23b, the first or second clutch body 22, 23 are pushed into their respective first Sl or second shift position S2.
  • Fig. 5 shows the planetary gear 1 in a first switching position Sl of the sliding sleeve 14, wherein the synchronization between the first synchronizer ring 24 and the first coupling body 22 is completed.
  • dashed lines of current via the shift sleeve 14 power flow Fl between the second 3 sun gear and the housing 8 is entered.
  • the second sun gear 3 is braked, thus the second gear G2 inserted.
  • the parts sliding sleeve 14, synchronizer body 18, first synchronizer ring 24 and first coupling body 22 thus form the function of the first brake Bl of the brake device 13.
  • Fig. 6 shows the planetary gear 1 in a second switching position S2 of the sliding sleeve 14, wherein the synchronization between the second synchronizer ring 25 and the second coupling body 23 is completed.
  • Arrows indicated on the shift sleeve 14 current flow F2 between the planet carrier 4 and the housing 8 is indicated.
  • the planet carrier 4 is thus braked and the first gear Gl inserted.
  • the parts sliding sleeve 14, synchronizer body 18, second synchronizer ring 25 and second coupling body 23 thus form the function of the second brake B2 of the braking device 13.
  • FIG. 8 shows a shifting device 9 for a transmission 10, which has a first transmission element 30 and a second transmission element 40. Brakes Bl, B2 having Brems recognizedl3 a switching device 9 according to the invention, either the first transmission element 30 or the second transmission element 40 can be braked or held.
  • the switching device 9 has a sliding sleeve 14, which rotatably, but - with respect to the rotational axis 30a and 40a of the rotatably mounted first gear element 30 and the rotatably mounted second gear element 40 - axially slidably connected to the housing 8 of the transmission 10.
  • the brakes Bl, B2 of the braking device 13 of the switching device 9 are also formed here with synchronizing rings 24, 25.
  • a first end position first shift position Sl of the sliding sleeve 14 the rotatably mounted first transmission element 30 - in the present case, a hollow shaft 33 - rotatably connected to the housing 8 and the rotatably mounted second transmission element 40 - in the present case, a shaft 44 - separated from the housing 8.
  • a second switching position S2 of the sliding sleeve 14 formed, for example, by a second end position, the rotatably mounted first gear element 30 - here the hollow shaft 33 - is separated from the housing 8 and the rotatably mounted second gear element 40 - in this case the shaft 44 - is rotationally fixed to the housing 8 connected.
  • the structure of the switching device 9 is analogous to the first embodiment shown in FIGS. 1 and 4 to 7.
  • a substantially annular synchronizer body 18 is arranged, which is rotatably but slidably connected to the sliding sleeve 14 - via a not visible in Fig. 8 toothing.
  • the synchronizer body 18 is rotatably mounted on the hollow shaft 33 via a bearing 21 and arranged between a first coupling body 22 and a second coupling body 23.
  • the hollow shaft 33 is rotatably supported relative to the shaft 44 via bearings, not shown in Fig. 8.
  • the hollow shaft 33 and the shaft 44 are rotatably supported with respect to the housing 8.
  • the first coupling body 22 is rotatably connected to the hollow shaft 33.
  • the second coupling body 23 is rotatably connected to the shaft 44.
  • first synchronizer ring 24 Between the first clutch body 22 and the synchronizer body 18, a first synchronizer ring 24, between the second clutch body 23 and the synchronizer body 18, a second synchronizer ring 25 is rotatably arranged.
  • Each first 24 or second synchronizer ring 25 has on its inside a conically shaped first friction surface 24a and second friction surface 25a, which cooperates with a corresponding conically shaped outer counter surface 22a, 23a of the first 22 and second clutch body 23.
  • the sliding sleeve 14 can only after synchronization of the corresponding synchronizer ring 24, 25 and the corresponding coupling body 22, 23 via the corresponding external teeth 24b, 25b of the first 24 and second synchronizer ring 25 and the external teeth 22b 23b, the first or second clutch body 22, 23 are pushed into their respective first Sl or second shift position S2.
  • Fig. 9 shows a further embodiment of a transmission 10, which differs from the embodiment shown in FIG. 8 in that the switched transmission elements 30, 40, and the synchronizer body 18 rotatably on neither one with the first transmission element nor one with the second transmission element connected wave are stored, and therefore no power flow takes place on this separate shaft.
  • the gear elements 30, 40 and the synchronizer body 18 are mounted on a separate shaft, for example on a shaft 200.

Landscapes

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

Abstract

L'invention concerne un arrangement de changement de rapport (9) pour une boîte de vitesses (10), comprenant au moins un élément de boîte de vitesses monté rotatif (30, 40) et au moins un élément de boîte de vitesses fixe sur le carter (80), comprenant au moins un dispositif de freinage (13) destiné à retenir ledit élément de boîte de vitesses monté rotatif (30, 40). Le dispositif de freinage (13) possède un manchon coulissant (14) qui est relié solidaire en rotation à un élément de boîte de vitesses (30, 80) de la boîte de vitesses (10), mais de manière à pouvoir coulisser dans le sens axial par rapport à un axe de rotation (30a, 40a) dudit élément de boîte de vitesses monté rotatif (30, 40). Dans une première position de changement de rapport (S1) du manchon coulissant (14), un premier élément de boîte de vitesses monté rotatif (30) est relié solidaire en rotation à l'élément de boîte de vitesses fixe sur le carter (80) et, dans une deuxième position de changement de rapport (S2) du manchon coulissant (14), le premier élément de boîte de vitesses monté rotatif (30) est séparé de l'élément de boîte de vitesses fixe sur le carter (80). Le dispositif de freinage (13) possède au moins une première et/ou une deuxième bague de synchroniseur (24, 25), laquelle coopère par le biais d'une première ou d'une deuxième surface de friction (24a, 25a) avec une première ou une deuxième surface homologue (22a, 23a) correspondante d'un premier ou d'un deuxième corps d'accouplement (22, 23) relié solidaire en rotation au premier ou au deuxième élément de boîte de vitesses monté rotatif (30, 40) ou à l'élément de boîte de vitesses fixe sur le carter (80). Un corps de synchronisation (18) relié solidaire en rotation au carter (8) par le biais du manchon coulissant (14) est disposé adjacent à au moins un corps d'accouplement (22, 23).
EP18806967.8A 2017-11-10 2018-11-09 Arrangement de changement de rapport pour une boîte de vitesses Withdrawn EP3707402A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA50942/2017A AT520296B1 (de) 2017-11-10 2017-11-10 Schaltvorrichtung für ein getriebe
PCT/AT2018/060267 WO2019090375A1 (fr) 2017-11-10 2018-11-09 Arrangement de changement de rapport pour une boîte de vitesses

Publications (1)

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EP3707402A1 true EP3707402A1 (fr) 2020-09-16

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EP18806967.8A Withdrawn EP3707402A1 (fr) 2017-11-10 2018-11-09 Arrangement de changement de rapport pour une boîte de vitesses

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US (1) US20200271198A1 (fr)
EP (1) EP3707402A1 (fr)
CN (1) CN111386406A (fr)
AT (1) AT520296B1 (fr)
WO (1) WO2019090375A1 (fr)

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DE102022003864A1 (de) * 2022-10-19 2024-04-25 Borgwarner Inc. Antriebsstrang für ein Kraftfahrzeug mit einem Planetenradgetriebe

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Publication number Publication date
AT520296A4 (de) 2019-03-15
CN111386406A (zh) 2020-07-07
US20200271198A1 (en) 2020-08-27
AT520296B1 (de) 2019-03-15
WO2019090375A1 (fr) 2019-05-16

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