WO2007060356A1 - Fast-transition gearbox - Google Patents

Fast-transition gearbox Download PDF

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Publication number
WO2007060356A1
WO2007060356A1 PCT/FR2006/051181 FR2006051181W WO2007060356A1 WO 2007060356 A1 WO2007060356 A1 WO 2007060356A1 FR 2006051181 W FR2006051181 W FR 2006051181W WO 2007060356 A1 WO2007060356 A1 WO 2007060356A1
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WO
WIPO (PCT)
Prior art keywords
gear
shaft
gearbox
pinion
main
Prior art date
Application number
PCT/FR2006/051181
Other languages
French (fr)
Inventor
Michel Buannec
Marc Picard
Original Assignee
Renault S.A.S.
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 Renault S.A.S. filed Critical Renault S.A.S.
Publication of WO2007060356A1 publication Critical patent/WO2007060356A1/en

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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
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
    • F16H61/684—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive
    • F16H61/688—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive with two inputs, e.g. selection of one of two torque-flow paths by 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
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H2003/0822—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the arrangement of at least one reverse gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0936—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts with multiple countershafts comprising only two idle gears and one gear fixed to the countershaft
    • 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
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts

Definitions

  • the invention relates to the field of gearboxes used in particular in motor vehicles.
  • Such boxes comprise several parallel shafts provided with a plurality of pinions and in particular two primary shafts alternately connected to the motor by two clutches.
  • the clutch must be shifted from the first gear to the neutral position, then trigger the first synchronization system, engage the reverse synchronization system with the incompressible time already noted, and finally reengage the clutch common to the first and in reverse.
  • Such a gearbox has the disadvantage of introducing a significant torque discontinuity between the first gear ratio and the reverse gear ratio, this is particularly disadvantageous for parking maneuvers where the driver of the vehicle has to brake the vehicle at the same time. that it goes from the first to the reverse or vice versa.
  • the invention proposes a gearbox that overcomes these disadvantages, which allows a rapid transition from one gear to another gear and in particular between the first gear and the reverse gear.
  • the motor vehicle gearbox with parallel shafts, provided with a plurality of gears and comprises a solid primary shaft, and a hollow primary shaft, coaxial and alternately connected to the vehicle engine by two clutches.
  • the gearbox also includes a secondary shaft provided with a pinion meshing with a vehicle differential ring, a main pinion meshing with a toothing of one of the primary shafts, and a main synchronization system. adapted to selectively fasten the rotation of the main pinion and the pinion gear.
  • the gearbox also comprises an intermediate shaft provided with a first intermediate gear connected in rotation with the solid primary shaft, a second intermediate gear connected in rotation with the hollow primary shaft, at least one of the two gear wheels. intermediate being free in rotation relative to the intermediate shaft, and an intermediate synchronization system adapted to selectively fasten the rotation of the two intermediate gears. In such a gearbox, it is possible to operate simultaneously the main and intermediate synchronization systems.
  • the gearbox When driving the primary shaft fitted with the gear meshing with the main gear, the gearbox has a certain transmission ratio. When the other intermediate shaft is driven, the gearbox has a different gear ratio.
  • the transition between the two gears does not require a synchronization system and can be very fast. It is enough to switch, the adhesion of one of the two clutches on the other, these being dimensioned to support the skating necessary for a fast transition.
  • one of the intermediate gears is fixedly mounted on the intermediate shaft.
  • the gearbox may also include another secondary shaft, not coaxial with the intermediate shaft, and provided with another pinion meshing with the aforementioned differential ring.
  • the gearbox has, when the main and intermediate synchronization systems are actuated simultaneously, two joint transmission ratios, one between the solid primary shaft and the differential, the other between the hollow primary shaft and the differential.
  • the two links of rotation between each of the two intermediate gears and the corresponding primary shaft are both direct or each put into play an odd number of meshes, the two joint reports being forward gears.
  • the differential being located in a forward zone of the gearbox, the drive pinion or gears are located at the front end of the corresponding secondary shaft, and the aforementioned main pinion is located immediately next to the gear pinion. corresponding attack.
  • the intermediate shaft is equipped with a return gear meshing with a reverse gear mounted on a secondary shaft so as to establish a reverse gear.
  • the rotational link between one of the two intermediate gears and the corresponding primary shaft is direct or involves an odd number of meshes, the rotation link of the gearbox.
  • Another intermediate gear with the corresponding primary shaft being indirect, involving an even number of meshes, so that the two gear ratios are a forward gear ratio and a reverse gear ratio.
  • the main pinion meshes with one of the aforementioned intermediate gears.
  • Another aspect of the invention consists of a method of transmitting engine torque for a motor vehicle, using a gearbox equipped with two primary shafts alternately connected to the engine by two clutches, a main synchronization system adapted to securely selective rotation of one of the primary shafts with a vehicle differential, an intermediate synchronization system capable of selectively joining the rotation of the two primary shafts.
  • Such a process comprises successively the following steps: - Operate the main and intermediate synchronization systems,
  • FIG 1 is a schematic representation of a first embodiment of a gearbox fast transition from first to reverse
  • FIG. 2 is a schematic representation of a second embodiment of a first-to-second fast transition gearbox.
  • a first transmission embodiment comprises a housing, a differential 2 connected to the wheels of the vehicle, a clutch device 3 connected to a driving shaft 4, a primary line 5, a first shaft secondary 6, a second secondary shaft 7 and an intermediate shaft 8.
  • the primary line 5 comprises a solid primary shaft 9 rotated by a hydraulic clutch 10, and a hollow primary shaft 11 rotated by a hydraulic clutch 12.
  • the two hydraulic clutches 10 and 12 and the two shafts Primary 9 and 11 are coaxial.
  • the two secondary shafts 6 and 7 and the intermediate shaft 8 are parallel to the primary line 5.
  • a first pinion gear 13 is fixedly mounted on the first secondary shaft 6.
  • a second pinion gear 14 is fixedly mounted on the second drive shaft 7.
  • the two drive gears mesh with the same differential gear 15.
  • the primary line 5 comprises, from left to right in FIG. 1, successively three sets of teeth 18, 19 and 20 fixedly mounted on the solid primary shaft 9, then three sets of teeth 21, 22 and 23 fixedly mounted on the hollow primary shaft 11. .
  • the first secondary shaft 6 is successively fitted, from left to right in FIG. 1, with a third pinion 24, with a double synchronization system 25, with a fifth pinion 26 and with a reverse pinion. 27.
  • the third pinion 24 and the fifth pinion 26 are rotatably mounted on the first secondary shaft 6 and cooperate with the double synchronization system 25.
  • the reverse pinion 27 is fixedly mounted on the first secondary shaft 6.
  • the second secondary shaft 7 comprises successively, from left to right in FIG. 1, a simple synchronization system
  • a sixth gear 29, a fourth gear 30, a main timing system 31, and a main gear 32 are rotatably mounted on the second gear 32.
  • the main gear 32 and the fourth gear 30 cooperate with the main synchronization system 31.
  • the sixth gear 29 cooperates with the simple synchronizer 28.
  • the intermediate shaft 8 is successively fitted, from left to right in FIG. 1, with a first intermediate gear 33, a second intermediate gear 34, an intermediate synchronization system 35, a idler gear 36.
  • the first intermediate gear 33 is fixedly mounted on the intermediate shaft 8
  • the second intermediate gear 34 and the idler gear 36 are mounted free in rotation on the intermediate shaft 8 and cooperate with the intermediate synchronization system 35.
  • the synchronization systems 25, 31 and 35 can take alternately three positions, namely a neutral position, a position actuated on one side, and a position actuated on the other.
  • a neutral position the two gears with which the synchronization system cooperates remain free in rotation.
  • an actuated position one of the pinions is secured in rotation with the shaft on which the synchronization system is mounted and the other pinion remains free to rotate.
  • the simple synchronization system 28 comprises two positions, a neutral position and a position actuated with the sixth gear 29.
  • the toothing 18 meshes with the third pinion 24.
  • the toothing 19 meshes with the first intermediate pinion 33.
  • the toothing 20 meshes with the fifth pinion 26.
  • the toothing 21 meshes with the second intermediate pinion 34 as well as with the pinion.
  • the gear 22 meshes with the fourth gear 30.
  • the gear 23 meshes with the main gear 32.
  • the reverse gear 27 meshes with the counter gear 36.
  • the second and fourth transmission ratios are established when the hydraulic clutch 12 is engaged and the main synchronization system 31 secures the rotation of the main pinion 32 or the fourth pinion 30.
  • the third and fourth gear ratios fifth are established when the hydraulic clutch 10 is engaged and the synchronization system double 25 secures the rotation of the third pinion 24 or the fifth pinion 26.
  • the sixth gear is established when the hydraulic clutch 12 is engaged and that the single synchronization system 28 secures the rotation of the sixth pinion 29. All the ratios of second, third, fourth, fifth and sixth are direct reports, for which the engine torque passes through a single meshing between a toothing of one of the primary shafts and a pinion of one of the secondary shafts.
  • the first and second ratios are joined in that the kinematic chain, which allows the establishment of each of these ratios, has a common part, namely the primary shaft 11, the toothing 23, the main gear 32 , the main synchronization system 31, the second secondary shaft 7, the drive pinion 14, and the differential ring gear 15.
  • the first gear is an indirect gear, whose kinematic chain requires in addition to the previous common part a succession of meshes passing through the solid primary shaft 9, the toothing 19, the first intermediate gear 33, the intermediate synchronization system 35, the intermediate shaft 8, the second intermediate gear 34, and the toothing 21 of the hollow primary shaft 11.
  • first and second gear The transition between first and second gear is very fast.
  • the main synchronization system 31 secures the main front gear 32 and the intermediate synchronization system 35 secures the two intermediate gears 33 and 34, it is sufficient to switch the engine torque from the hydraulic clutch 10 to the hydraulic clutch 12 or conversely, to change the ratio.
  • the roller bearing 16 could also be located between the main pinion 32 and the pinion gear 14, as well as between the reverse pinion 27 and the pinion gear 13.
  • All the pinions of the second secondary shaft 7 mesh with teeth of the hollow primary shaft 11.
  • the axial dimensions of the solid primary shaft 9, located behind the pinion 29 of the second secondary shaft 7, comprises the size of the teeth 18, 19 and
  • the size of the second secondary shaft 7 behind the pinion 29 is limited to the simple synchronization system 28 and is therefore much shorter than the primary line 5.
  • the gearbox comprises a first secondary shaft 47, provided at its front end with a first drive pinion 48, and a second secondary shaft 49, provided at its front end with a second pinion gear 50.
  • drive gears 48, 50 meshing with the differential ring gear 15.
  • the solid primary shaft 9 successively comprises the teeth 51, 52 and then 53.
  • the hollow primary shaft 11 comprises the teeth 54 and then 55.
  • the first secondary shaft 47 comprises successively, on the left on the right, a main gear 56, a main synchronization system 57, a sixth gear 58.
  • the second secondary shaft 49 comprises, from left to right right, a third gear 59, a dual timing system 60, a fifth gear 61, a fourth gear 62, a dual timing system 63 and a second gear 64.
  • the intermediate shaft 8 includes, from left to right right, a first intermediate gear 65, an intermediate synchronization system
  • the first intermediate gear 65 is fixedly mounted on the intermediate shaft 8
  • the second intermediate gear 67 is rotatably mounted, adapted to be secured to the first intermediate gear by actuating the intermediate synchronization system 66.
  • the main gear 56 meshes with the toothing 51 and with the first intermediate gear 65.
  • the toothing 52 meshes with the third gear 59.
  • the gear 53 meshes with the fifth gear 61.
  • the gear 54 meshes with the fourth gear 62.
  • the toothing 55 meshes with the second gear 64 and with the second intermediate gear 67.
  • the third and fifth ratios are established when the hydraulic clutch 10 is engaged and the dual timing system 60 secures the third gear 59 or the fifth gear 61 with the second secondary shaft 49.
  • the fourth and fourth gear ratios are of second are established when the hydraulic clutch 12 is engaged and the dual synchronization system 63 secures the fourth gear 62 or the second gear 64 with the second secondary shaft 49.
  • the sixth gear is established when the hydraulic clutch 12 is engaged and that the main synchronization system 57 secures the sixth gear with the first secondary shaft 47.
  • the first report is a direct report, established as soon as the main synchronization system 57 secures the main gear 56 with the first secondary shaft 47 and that the hydraulic clutch 10 is engaged, and this whatever the position of the intermediate synchronization system 66.
  • the reverse ratio is an indirect ratio for which the engine torque transits from the hydraulic clutch 10 to the differential 2 through the toothing 55, the second intermediate gear 67, the intermediate timing system 66, the first intermediate gear 65, the main gear 56, the main synchronization system 57, the pinion gear 48 and the differential crown 15.
  • the main synchronization system 57 and the intermediate timing system 66 are actuated, it is possible to switch from the first gear to the reverse gear ratio by switching the grip from the hydraulic clutch 10 to the hydraulic clutch 12 or vice versa. This transition between the two gears is done without interruption of torque and without delay, because no mechanism internal to the gearbox requires to be engaged during the shift phase.

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

Abstract

The invention concerns a motor vehicle gearbox, with parallel shafts, equipped with gear pinions and comprising coaxial solid primary shaft (9), and hollow primary shaft (11) alternately connected to the vehicle engine through two clutches (10, 12), a secondary shaft (7, 47) equipped with a drive pinion (14, 48) meshing with a ring gear (15) of the vehicle differential, with a main gear pinion (32, 56) meshing with teeth (23, 51) of one of the primary shafts (11, 9), and with a main synchronizing system (31, 57) adapted to secure selectively the rotation of the main gear pinion (32, 56) and the drive pinion (14, 48). The invention is characterized in that it comprises an intermediate shaft (8) equipped with a first intermediate gear pinion (33, 65) linked in rotation with the hollow primary shaft (11), at least one (34, 67) of the two intermediate gear pinions freely rotatable with respect to the intermediate shaft (8), and with an intermediate synchronizing system (35, 66) adapted to secure selectively the rotation of the two intermediate gear pinions (33-34, 65-67).

Description

Boîte de vitesses à transition rapide. Gearbox with fast transition.
L'invention concerne le domaine des boîtes de vitesses utilisées en particulier dans les véhicules automobiles. De telles boîtes comprennent plusieurs arbres parallèles munis d'une pluralité de pignons et notamment deux arbres primaires reliés alternativement au moteur par deux embrayages.The invention relates to the field of gearboxes used in particular in motor vehicles. Such boxes comprise several parallel shafts provided with a plurality of pinions and in particular two primary shafts alternately connected to the motor by two clutches.
Dans ce domaine, la demande de brevet DE 198 21 164 (Volkswagen) a décrit une boîte de vitesses à arbres parallèles, comprenant deux arbres primaires coaxiaux entraînés chacun par un embrayage. Chacun des rapports de la boîte de vitesses nécessite l' enclenchement d'un système de synchronisation spécifique ne correspondant qu' à un seul rapport de vitesse.In this field, patent application DE 198 21 164 (Volkswagen) has described a gearbox with parallel shafts, comprising two coaxial primary shafts each driven by a clutch. Each gearbox ratio requires the engagement of a specific timing system corresponding to only one gear ratio.
Dans une telle boîte, l' abandon d'un rapport au profit d'un rapport adjacent suppose trois étapes. Il faut enclencher le système de synchronisation du rapport adjacent puis faire basculer le couple moteur d'un embrayage à l' autre et enfin, déclencher le système de synchronisation du rapport abandonné.In such a box, abandoning a report in favor of an adjacent report requires three steps. The adjacent gear synchronization system must be engaged, the engine torque to be switched from one clutch to the other, and finally the synchronization system of the aborted gear must be triggered.
Le fait de devoir enclencher un système de synchronisation jusqu' alors inactif est une opération particulièrement longue. Le système de synchronisation patine jusqu' à ce qu'une série d' organes jusqu' alors en repos se mette en rotation. Ce patinage doit vaincre l' inertie desdits organes et notamment l' embrayage resté libre. Un système de synchronisation n' est pas prévu pour patiner sous un couple important, or l' embrayage présente une inertie élevée de sorte que l' enclenchement d' un système de synchronisation nécessite un temps incompressible. Une temporisation est nécessaire entre l' ordre de changer un rapport et sa réalisation effective afin de réaliser successivement les trois étapes nécessaires De plus, dans la boîte de vitesses décrite, la transition de première à marche arrière est particulièrement longue et nécessite quatre étapes. Il faut faire passer l' embrayage de première au point mort, puis déclencher le système de synchronisation de première, enclencher le système de synchronisation de marche arrière avec le temps incompressible déjà noté, et enfin remettre en prise l' embrayage commun à la première et à la marche arrière. Une telle boîte de vitesses présente l' inconvénient d' introduire une discontinuité de couple importante entre le rapport de première et le rapport de marche arrière, ceci est particulièrement pénalisant pour les manœuvres en parking où le conducteur du véhicule doit freiner le véhicule en même temps qu' il passe de la première à la marche arrière ou réciproquement.The fact of having to engage a synchronization system until it is inactive is a particularly long operation. The synchronization system slips until a series of organs until then idle is rotated. This skating must overcome the inertia of said bodies and in particular the clutch remained free. A synchronization system is not intended to slip under a large torque, but the clutch has a high inertia so that the engagement of a synchronization system requires an incompressible time. A delay is necessary between the order to change a report and its actual realization in order to successively carry out the three necessary steps In addition, in the gearbox described, the transition from first to reverse is particularly long and requires four steps. The clutch must be shifted from the first gear to the neutral position, then trigger the first synchronization system, engage the reverse synchronization system with the incompressible time already noted, and finally reengage the clutch common to the first and in reverse. Such a gearbox has the disadvantage of introducing a significant torque discontinuity between the first gear ratio and the reverse gear ratio, this is particularly disadvantageous for parking maneuvers where the driver of the vehicle has to brake the vehicle at the same time. that it goes from the first to the reverse or vice versa.
L' invention propose une boîte de vitesses qui résout ces inconvénients, qui permet une transition rapide d'un rapport à un autre rapport et notamment entre le rapport de première et de marche arrière.The invention proposes a gearbox that overcomes these disadvantages, which allows a rapid transition from one gear to another gear and in particular between the first gear and the reverse gear.
Selon un mode de réalisation, la boîte de vitesse de véhicule automobile, à arbres parallèles, munis d'une pluralité de pignons et comprend un arbre primaire plein, et un arbre primaire creux, coaxiaux et reliés alternativement au moteur du véhicule par deux embrayages.According to one embodiment, the motor vehicle gearbox, with parallel shafts, provided with a plurality of gears and comprises a solid primary shaft, and a hollow primary shaft, coaxial and alternately connected to the vehicle engine by two clutches.
La boîte de vitesses comprend également un arbre secondaire muni d'un pignon d' attaque engrenant avec une couronne de différentiel du véhicule, d'un pignon principal engrenant avec une denture d'un des arbres primaires, et d'un système de synchronisation principal apte à solidariser de manière sélective la rotation du pignon principal et du pignon d' attaque. La boîte de vitesses comprend aussi un arbre intermédiaire muni d'un premier pignon intermédiaire lié en rotation avec l' arbre primaire plein, d'un deuxième pignon intermédiaire lié en rotation avec l' arbre primaire creux, au moins l'un des deux pignons intermédiaires étant libre en rotation par rapport à l' arbre intermédiaire, et d'un système de synchronisation intermédiaire apte à solidariser de manière sélective la rotation des deux pignons intermédiaires. Dans une telle boîte de vitesses, on peut actionner simultanément les systèmes de synchronisation principal et intermédiaire. Lorsqu' on entraîne l' arbre primaire équipé de la denture engrenant avec le pignon principal, la boîte de vitesses présente un certain rapport de transmission, Lorsqu' on entraîne l' autre arbre intermédiaire, la boîte de vitesses présente un autre rapport de transmission. La transition entre les deux rapports ne nécessite pas d' enclencher de système de synchronisation et peut être très rapide. Il suffit de basculer, l' adhérence d'un des deux embrayages sur l' autre, ceux-ci étant dimensionnés pour supporter le patinage nécessaire à une transition rapide.The gearbox also includes a secondary shaft provided with a pinion meshing with a vehicle differential ring, a main pinion meshing with a toothing of one of the primary shafts, and a main synchronization system. adapted to selectively fasten the rotation of the main pinion and the pinion gear. The gearbox also comprises an intermediate shaft provided with a first intermediate gear connected in rotation with the solid primary shaft, a second intermediate gear connected in rotation with the hollow primary shaft, at least one of the two gear wheels. intermediate being free in rotation relative to the intermediate shaft, and an intermediate synchronization system adapted to selectively fasten the rotation of the two intermediate gears. In such a gearbox, it is possible to operate simultaneously the main and intermediate synchronization systems. When driving the primary shaft fitted with the gear meshing with the main gear, the gearbox has a certain transmission ratio. When the other intermediate shaft is driven, the gearbox has a different gear ratio. The transition between the two gears does not require a synchronization system and can be very fast. It is enough to switch, the adhesion of one of the two clutches on the other, these being dimensioned to support the skating necessary for a fast transition.
Avantageusement, un des pignons intermédiaires est monté fixe sur l' arbre intermédiaire. La boîte de vitesses peut aussi comprendre un autre arbre secondaire, non coaxial avec l' arbre intermédiaire, et muni d'un autre pignon d' attaque engrenant avec la couronne de différentiel précitée.Advantageously, one of the intermediate gears is fixedly mounted on the intermediate shaft. The gearbox may also include another secondary shaft, not coaxial with the intermediate shaft, and provided with another pinion meshing with the aforementioned differential ring.
Avantageusement, la boîte de vitesses présente, lorsque les systèmes de synchronisation principal et intermédiaire sont actionnés simultanément, deux rapport de transmission joints, l'un entre l' arbre primaire plein et le différentiel, l' autre entre l' arbre primaire creux et le différentiel.Advantageously, the gearbox has, when the main and intermediate synchronization systems are actuated simultaneously, two joint transmission ratios, one between the solid primary shaft and the differential, the other between the hollow primary shaft and the differential.
Selon un mode particulier de réalisation de la boîte de vitesses, les deux liens de rotation entre chacun des deux pignons intermédiaires et l' arbre primaire correspondant, sont tous les deux directs ou mettent chacun en jeu un nombre impair d' engrènements, les deux rapport j oints étant des rapports de marche avant.According to a particular embodiment of the gearbox, the two links of rotation between each of the two intermediate gears and the corresponding primary shaft, are both direct or each put into play an odd number of meshes, the two joint reports being forward gears.
Avantageusement, le différentiel étant situé dans une zone avant de la boîte de vitesses, le ou les pignons d' attaque sont situés à l' extrémité avant de l' arbre secondaire correspondant, et le pignon principal précité est situé immédiatement à côté du pignon d' attaque correspondant.Advantageously, the differential being located in a forward zone of the gearbox, the drive pinion or gears are located at the front end of the corresponding secondary shaft, and the aforementioned main pinion is located immediately next to the gear pinion. corresponding attack.
Avantageusement l' arbre intermédiaire est équipé d'un pignon de renvoi engrenant avec un pignon de marche arrière monté sur un arbre secondaire de manière à établir un rapport de marche arrière.Advantageously, the intermediate shaft is equipped with a return gear meshing with a reverse gear mounted on a secondary shaft so as to establish a reverse gear.
Selon un autre mode particulier de réalisation de la boîte de vitesses, le lien de rotation entre l'un des deux pignons intermédiaires et l' arbre primaire correspondant est direct ou met en jeu un nombre impair d' engrènements, le lien de rotation de l' autre pignon intermédiaire avec l' arbre primaire correspondant étant indirect, mettant en jeu un nombre pair d' engrènements, de sorte que les deux rapports joints sont un rapport de marche avant et un rapport de marche arrière.According to another particular embodiment of the gearbox, the rotational link between one of the two intermediate gears and the corresponding primary shaft is direct or involves an odd number of meshes, the rotation link of the gearbox. Another intermediate gear with the corresponding primary shaft being indirect, involving an even number of meshes, so that the two gear ratios are a forward gear ratio and a reverse gear ratio.
Avantageusement le pignon principal engrène avec l'un des pignons intermédiaires précités.Advantageously, the main pinion meshes with one of the aforementioned intermediate gears.
Un autre aspect de l' invention consiste en un procédé de transmission de couple moteur pour véhicule automobile, utilisant une boîte de vitesses équipée de deux arbres primaires alternativement reliés au moteur par deux embrayages, d'un système de synchronisation principal apte à solidariser de manière sélective la rotation d'un des arbres primaires avec un différentiel du véhicule, d'un système de synchronisation intermédiaire apte à solidariser de manière sélective la rotation des deux arbres primaires. Un tel procédé comprend successivement les étapes suivantes : - Actionner les systèmes de synchronisation principal et intermédiaire,Another aspect of the invention consists of a method of transmitting engine torque for a motor vehicle, using a gearbox equipped with two primary shafts alternately connected to the engine by two clutches, a main synchronization system adapted to securely selective rotation of one of the primary shafts with a vehicle differential, an intermediate synchronization system capable of selectively joining the rotation of the two primary shafts. Such a process comprises successively the following steps: - Operate the main and intermediate synchronization systems,
- Faire adhérer l'un des embrayages pour établir l'un des rapports de transmission, - Basculer l' adhérence d'un embrayage sur l' autre pour changer de rapport de transmission.- Adhere one of the clutches to establish one of the transmission ratios, - Toggle the grip of one clutch on the other to change gear ratio.
D' autres caractéristiques et avantages de l'invention apparaîtront à la lecture de la description détaillée de deux modes de réalisation du moteur pris à titre d' exemples non limitatifs et illustrés par les dessins annexés, sur lesquels :Other features and advantages of the invention will appear on reading the detailed description of two embodiments of the motor taken as non-limiting examples and illustrated by the appended drawings, in which:
-la figure 1 est une représentation schématique d'un premier mode de réalisation d'une boîte de vitesses à transition rapide de première à marche arrière ; etFIG 1 is a schematic representation of a first embodiment of a gearbox fast transition from first to reverse; and
-la figure 2 est une représentation schématique d'un deuxième mode de réalisation d'une boîte de vitesses à transition rapide de première à seconde.FIG. 2 is a schematic representation of a second embodiment of a first-to-second fast transition gearbox.
Comme illustré sur la figure 1 , un premier mode de réalisation de boîte de vitesses comprend un carter, un différentiel 2 relié aux roues du véhicule, un dispositif d' embrayage 3 relié à un arbre moteur 4, une ligne primaire 5, un premier arbre secondaire 6, un deuxième arbre secondaire 7 et un arbre intermédiaire 8.As illustrated in FIG. 1, a first transmission embodiment comprises a housing, a differential 2 connected to the wheels of the vehicle, a clutch device 3 connected to a driving shaft 4, a primary line 5, a first shaft secondary 6, a second secondary shaft 7 and an intermediate shaft 8.
Conventionnellement, dans la présente description, on appellera « avant », le côté droit de la figure correspondant au côté de la boîte de vitesses où est implanté le différentiel 2, et « arrière » le côté opposé.Conventionally, in the present description, will be called "before", the right side of the figure corresponding to the side of the gearbox where is implanted the differential 2, and "back" the opposite side.
La ligne primaire 5 comprend un arbre primaire plein 9 entraîné en rotation par un embrayage hydraulique 10, et un arbre primaire creux 11 entraîné en rotation par un embrayage hydraulique 12. Les deux embrayages hydrauliques 10 et 12 et les deux arbres primaires 9 et 11 sont coaxiaux. Les deux arbres secondaires 6 et 7 et l' arbre intermédiaire 8 sont parallèles à la ligne primaire 5. Un premier pignon d' attaque 13 est monté fixe sur le premier arbre secondaire 6. Un deuxième pignon d' attaque 14 est monté fixe sur le deuxième arbre secondaire 7. Les deux pignons d' attaque engrènent une même couronne de différentiel 15.The primary line 5 comprises a solid primary shaft 9 rotated by a hydraulic clutch 10, and a hollow primary shaft 11 rotated by a hydraulic clutch 12. The two hydraulic clutches 10 and 12 and the two shafts Primary 9 and 11 are coaxial. The two secondary shafts 6 and 7 and the intermediate shaft 8 are parallel to the primary line 5. A first pinion gear 13 is fixedly mounted on the first secondary shaft 6. A second pinion gear 14 is fixedly mounted on the second drive shaft 7. The two drive gears mesh with the same differential gear 15.
La ligne primaire 5 comprend, de gauche à droite sur la figure 1 , successivement trois dentures 18 , 19 et 20 montées fixes sur l' arbre primaire plein 9, puis trois dentures 21 , 22 et 23 montées fixes sur l' arbre primaire creux 11.The primary line 5 comprises, from left to right in FIG. 1, successively three sets of teeth 18, 19 and 20 fixedly mounted on the solid primary shaft 9, then three sets of teeth 21, 22 and 23 fixedly mounted on the hollow primary shaft 11. .
Le premier arbre secondaire 6 est équipé successivement, de gauche à droite sur la figure 1 , d'un pignon de troisième 24, d'un système de synchronisation double 25, d'un pignon de cinquième 26 et d'un pignon de marche arrière 27. Le pignon de troisième 24 et le pignon de cinquième 26 sont montés libres en rotation sur le premier arbre secondaire 6 et coopèrent avec le système de synchronisation double 25. Le pignon de marche arrière 27 est monté fixe sur le premier arbre secondaire 6.The first secondary shaft 6 is successively fitted, from left to right in FIG. 1, with a third pinion 24, with a double synchronization system 25, with a fifth pinion 26 and with a reverse pinion. 27. The third pinion 24 and the fifth pinion 26 are rotatably mounted on the first secondary shaft 6 and cooperate with the double synchronization system 25. The reverse pinion 27 is fixedly mounted on the first secondary shaft 6.
Le deuxième arbre secondaire 7 comporte successivement, de gauche à droite sur la figure 1 , un système de synchronisation simpleThe second secondary shaft 7 comprises successively, from left to right in FIG. 1, a simple synchronization system
28, un pignon de sixième 29, un pignon de quatrième 30, un système de synchronisation principal 31 , et un pignon principal 32. Les pignons de sixième 29, de quatrième 30 et le pignon principal 32, sont montés libres en rotation sur le deuxième arbre secondaire 7. Le pignon principal 32 et le pignon de quatrième 30 coopèrent avec le système de synchronisation principal 31. Le pignon de sixième 29 coopère avec le synchroniseur simple 28.28, a sixth gear 29, a fourth gear 30, a main timing system 31, and a main gear 32. The sixth 29, fourth gear 30 and the main gear 32 are rotatably mounted on the second gear 32. secondary shaft 7. The main gear 32 and the fourth gear 30 cooperate with the main synchronization system 31. The sixth gear 29 cooperates with the simple synchronizer 28.
L' arbre intermédiaire 8 est équipé successivement, de gauche à droite sur la figure 1 , d'un premier pignon intermédiaire 33, d'un deuxième pignon intermédiaire 34, d'un système de synchronisation intermédiaire 35 , d'un pignon de renvoi 36. Le premier pignon intermédiaire 33 est monté fixe sur l' arbre intermédiaire 8, le deuxième pignon intermédiaire 34 et le pignon de renvoi 36 sont montés libres en rotation sur l' arbre intermédiaire 8 et coopèrent avec le système de synchronisation intermédiaire 35.The intermediate shaft 8 is successively fitted, from left to right in FIG. 1, with a first intermediate gear 33, a second intermediate gear 34, an intermediate synchronization system 35, a idler gear 36. The first intermediate gear 33 is fixedly mounted on the intermediate shaft 8, the second intermediate gear 34 and the idler gear 36 are mounted free in rotation on the intermediate shaft 8 and cooperate with the intermediate synchronization system 35.
Les systèmes de synchronisation 25, 31 et 35 peuvent prendre alternativement trois positions, à savoir une position neutre, une position actionnée d'un côté, et une position actionnée de l' autre. Dans la position neutre, les deux pignons avec lesquels le système de synchronisation coopère, restent libres en rotation. Dans une position actionnée, l'un des pignons est solidarisé en rotation avec l' arbre sur lequel le système de synchronisation est monté et l' autre pignon reste libre en rotation. Le système de synchronisation simple 28 comprend deux positions, une position neutre et une position actionnée avec le pignon de sixième 29.The synchronization systems 25, 31 and 35 can take alternately three positions, namely a neutral position, a position actuated on one side, and a position actuated on the other. In the neutral position, the two gears with which the synchronization system cooperates remain free in rotation. In an actuated position, one of the pinions is secured in rotation with the shaft on which the synchronization system is mounted and the other pinion remains free to rotate. The simple synchronization system 28 comprises two positions, a neutral position and a position actuated with the sixth gear 29.
La denture 18 engrène avec le pignon de troisième 24. La denture 19 engrène avec le premier pignon intermédiaire 33. La denture 20 engrène avec le pignon de cinquième 26. La denture 21 engrène avec le deuxième pignon intermédiaire 34 ainsi qu' avec le pignon de sixième 29. La denture 22 engrène avec le pignon de quatrième 30. La denture 23 engrène avec le pignon principal 32. Le pignon de marche arrière 27 engrène avec le pignon de renvoi 36.The toothing 18 meshes with the third pinion 24. The toothing 19 meshes with the first intermediate pinion 33. The toothing 20 meshes with the fifth pinion 26. The toothing 21 meshes with the second intermediate pinion 34 as well as with the pinion. The gear 22 meshes with the fourth gear 30. The gear 23 meshes with the main gear 32. The reverse gear 27 meshes with the counter gear 36.
Les rapports de transmission de seconde et de quatrième sont établis lorsque l' embrayage hydraulique 12 est en prise et que le système de synchronisation principal 31 solidarise la rotation du pignon principal 32 ou du pignon de quatrième 30. De même, les rapports de troisième et de cinquième sont établis lorsque l' embrayage hydraulique 10 est en prise et que le système de synchronisation double 25 solidarise la rotation du pignon de troisième 24 ou du pignon de cinquième 26. Le rapport de sixième est établi lorsque l' embrayage hydraulique 12 est en prise et que le système de synchronisation simple 28 solidarise la rotation du pignon de sixième 29. Tous les rapports de seconde, de troisième, de quatrième, de cinquième et de sixième sont des rapports directs, pour lesquels le couple moteur transite par un seul engrènement entre une denture d'un des arbres primaires et un pignon d'un des arbres secondaires.The second and fourth transmission ratios are established when the hydraulic clutch 12 is engaged and the main synchronization system 31 secures the rotation of the main pinion 32 or the fourth pinion 30. Similarly, the third and fourth gear ratios fifth are established when the hydraulic clutch 10 is engaged and the synchronization system double 25 secures the rotation of the third pinion 24 or the fifth pinion 26. The sixth gear is established when the hydraulic clutch 12 is engaged and that the single synchronization system 28 secures the rotation of the sixth pinion 29. All the ratios of second, third, fourth, fifth and sixth are direct reports, for which the engine torque passes through a single meshing between a toothing of one of the primary shafts and a pinion of one of the secondary shafts.
Les rapports de première et de seconde sont joints, en ce sens que la chaîne cinématique, qui permet l' établissement de chacun de ces rapports, possède une partie commune, à savoir l' arbre primaire 11 , la denture 23, le pignon principal 32, le système de synchronisation principal 31 , le deuxième arbre secondaire 7, le pignon d' attaque 14, et la couronne 15 de différentiel 2. Le rapport de première est un rapport indirect, dont la chaîne cinématique nécessite en plus de la précédente partie commune une succession d' engrènements passant par l' arbre primaire plein 9, la denture 19, le premier pignon intermédiaire 33, le système de synchronisation intermédiaire 35, l' arbre intermédiaire 8, le deuxième pignon intermédiaire 34, et la denture 21 de l' arbre primaire creux 11.The first and second ratios are joined in that the kinematic chain, which allows the establishment of each of these ratios, has a common part, namely the primary shaft 11, the toothing 23, the main gear 32 , the main synchronization system 31, the second secondary shaft 7, the drive pinion 14, and the differential ring gear 15. The first gear is an indirect gear, whose kinematic chain requires in addition to the previous common part a succession of meshes passing through the solid primary shaft 9, the toothing 19, the first intermediate gear 33, the intermediate synchronization system 35, the intermediate shaft 8, the second intermediate gear 34, and the toothing 21 of the hollow primary shaft 11.
La transition entre les rapports de première et de seconde est très rapide. Lorsque le système de synchronisation principal 31 solidarise le pignon principal avant 32 et que le système de synchronisation intermédiaire 35 solidarise les deux pignons intermédiaires 33 et 34, il suffit de basculer le couple moteur depuis l' embrayage hydraulique 10 vers l' embrayage hydraulique 12 ou inversement, pour changer de rapport. Le palier à rouleaux 16 pourrait également être situé entre le pignon principal 32 et le pignon d' attaque 14, de même qu' entre le pignon de marche arrière 27 et le pignon d' attaque 13.The transition between first and second gear is very fast. When the main synchronization system 31 secures the main front gear 32 and the intermediate synchronization system 35 secures the two intermediate gears 33 and 34, it is sufficient to switch the engine torque from the hydraulic clutch 10 to the hydraulic clutch 12 or conversely, to change the ratio. The roller bearing 16 could also be located between the main pinion 32 and the pinion gear 14, as well as between the reverse pinion 27 and the pinion gear 13.
Tous les pignons du deuxième arbre secondaire 7 engrènent avec des dentures de l' arbre primaire creux 11. L' encombrement axial de l' arbre primaire plein 9, situé en arrière du pignon 29 du deuxième arbre secondaire 7, comprend l' encombrement des dentures 18, 19 etAll the pinions of the second secondary shaft 7 mesh with teeth of the hollow primary shaft 11. The axial dimensions of the solid primary shaft 9, located behind the pinion 29 of the second secondary shaft 7, comprises the size of the teeth 18, 19 and
20 et du système de synchronisation double 25. L'encombrement du deuxième arbre secondaire 7 en arrière du pignon 29 est limité au système de synchronisation simple 28 et est donc beaucoup plus court que la ligne primaire 5.20 and the dual synchronization system 25. The size of the second secondary shaft 7 behind the pinion 29 is limited to the simple synchronization system 28 and is therefore much shorter than the primary line 5.
On va maintenant décrire un deuxième mode de réalisation de l' invention illustré sur la figure 2 sur laquelle les éléments similaires portent sur les mêmes références. Les arbres primaires 9, 11 , les embrayages 10, 12, l' arbre intermédiaire 8 , et la couronne 15 de différentiel 2 qui portent les mêmes références ont les mêmes fonctions que dans le mode de réalisation précédent.We will now describe a second embodiment of the invention illustrated in Figure 2 in which the similar elements relate to the same references. The primary shafts 9, 11, the clutches 10, 12, the intermediate shaft 8, and the differential ring 15 which bear the same references have the same functions as in the previous embodiment.
La boîte de vitesses comprend un premier arbre secondaire 47, muni à son extrémité avant d'un premier pignon d' attaque 48, et un deuxième arbre secondaire 49, muni à son extrémité avant d'un deuxième pignon d' attaque 50. Les deux pignons d' attaque 48, 50 engrènent avec la couronne 15 de différentiel 2.The gearbox comprises a first secondary shaft 47, provided at its front end with a first drive pinion 48, and a second secondary shaft 49, provided at its front end with a second pinion gear 50. drive gears 48, 50 meshing with the differential ring gear 15.
De gauche à droite sur la figure 2, l' arbre primaire plein 9 comprend successivement les dentures 51 , 52, puis 53. L' arbre primaire creux 11 comprend les dentures 54, puis 55. Le premier arbre secondaire 47 comprend successivement, de gauche à droite, un pignon principal 56, un système de synchronisation principal 57, un pignon de sixième 58. Le deuxième arbre secondaire 49 comprend, de gauche à droite, un pignon de troisième 59, un système de synchronisation double 60, un pignon de cinquième 61 , un pignon de quatrième 62, un système de synchronisation double 63 et un pignon de seconde 64. L' arbre intermédiaire 8 comprend, de gauche à droite, un premier pignon intermédiaire 65, un système de synchronisation intermédiaireFrom left to right in FIG. 2, the solid primary shaft 9 successively comprises the teeth 51, 52 and then 53. The hollow primary shaft 11 comprises the teeth 54 and then 55. The first secondary shaft 47 comprises successively, on the left on the right, a main gear 56, a main synchronization system 57, a sixth gear 58. The second secondary shaft 49 comprises, from left to right right, a third gear 59, a dual timing system 60, a fifth gear 61, a fourth gear 62, a dual timing system 63 and a second gear 64. The intermediate shaft 8 includes, from left to right right, a first intermediate gear 65, an intermediate synchronization system
66 et un deuxième pignon intermédiaire 67. Le premier pignon intermédiaire 65 est monté fixe sur l' arbre intermédiaire 8 , et le deuxième pignon intermédiaire 67 est monté libre en rotation, apte à être solidarisé avec le premier pignon intermédiaire grâce à l' actionnement du système de synchronisation intermédiaire 66.66 and a second intermediate gear 67. The first intermediate gear 65 is fixedly mounted on the intermediate shaft 8, and the second intermediate gear 67 is rotatably mounted, adapted to be secured to the first intermediate gear by actuating the intermediate synchronization system 66.
Le pignon principal 56 engrène avec la denture 51 et avec le premier pignon intermédiaire 65. La denture 52 engrène avec le pignon de troisième 59. La denture 53 engrène avec le pignon de cinquième 61. La denture 54 engrène avec le pignon de quatrième 62. La denture 55 engrène avec le pignon de seconde 64 et avec le deuxième pignon intermédiaire 67.The main gear 56 meshes with the toothing 51 and with the first intermediate gear 65. The toothing 52 meshes with the third gear 59. The gear 53 meshes with the fifth gear 61. The gear 54 meshes with the fourth gear 62. The toothing 55 meshes with the second gear 64 and with the second intermediate gear 67.
Les rapports de troisième et de cinquième sont établis lorsque l' embrayage hydraulique 10 est en prise et que le système de synchronisation double 60 solidarise le pignon de troisième 59 ou le pignon de cinquième 61 avec le deuxième arbre secondaire 49. Les rapports de quatrième et de seconde sont établis lorsque l' embrayage hydraulique 12 est en prise et que le système de synchronisation double 63 solidarise le pignon de quatrième 62 ou bien le pignon de seconde 64 avec le deuxième arbre secondaire 49. Le rapport de sixième est établi lorsque l' embrayage hydraulique 12 est en prise et que le système de synchronisation principal 57 solidarise le pignon de sixième avec le premier arbre secondaire 47.The third and fifth ratios are established when the hydraulic clutch 10 is engaged and the dual timing system 60 secures the third gear 59 or the fifth gear 61 with the second secondary shaft 49. The fourth and fourth gear ratios are of second are established when the hydraulic clutch 12 is engaged and the dual synchronization system 63 secures the fourth gear 62 or the second gear 64 with the second secondary shaft 49. The sixth gear is established when the hydraulic clutch 12 is engaged and that the main synchronization system 57 secures the sixth gear with the first secondary shaft 47.
Le rapport de première est un rapport direct, établi dès que le système de synchronisation principal 57 solidarise le pignon principal 56 avec le premier arbre secondaire 47 et que l' embrayage hydraulique 10 est en prise, et ceci quelle que soit la position du système de synchronisation intermédiaire 66. Le rapport de marche arrière est un rapport indirect pour lequel le couple moteur transite depuis l' embrayage hydraulique 10 vers le différentiel 2 en passant par la denture 55 , le deuxième pignon intermédiaire 67, le système de synchronisation intermédiaire 66, le premier pignon intermédiaire 65, le pignon principal 56, le système de synchronisation principal 57, le pignon d' attaque 48 et la couronne de différentiel 15. Lorsque le système de synchronisation principal 57 et le système de synchronisation intermédiaire 66 sont actionnés, il est possible de passer du rapport de première au rapport de marche arrière en basculant l' adhérence depuis l' embrayage hydraulique 10 vers l' embrayage hydraulique 12 ou inversement. Cette transition entre les deux rapports se fait sans interruption du couple et sans temporisation, car aucun mécanisme interne à la boîte de vitesses ne nécessite d' être enclenché durant la phase de changement de rapport.The first report is a direct report, established as soon as the main synchronization system 57 secures the main gear 56 with the first secondary shaft 47 and that the hydraulic clutch 10 is engaged, and this whatever the position of the intermediate synchronization system 66. The reverse ratio is an indirect ratio for which the engine torque transits from the hydraulic clutch 10 to the differential 2 through the toothing 55, the second intermediate gear 67, the intermediate timing system 66, the first intermediate gear 65, the main gear 56, the main synchronization system 57, the pinion gear 48 and the differential crown 15. When the main synchronization system 57 and the intermediate timing system 66 are actuated, it is possible to switch from the first gear to the reverse gear ratio by switching the grip from the hydraulic clutch 10 to the hydraulic clutch 12 or vice versa. This transition between the two gears is done without interruption of torque and without delay, because no mechanism internal to the gearbox requires to be engaged during the shift phase.
Il serait possible d' implanter le système de synchronisation intermédiaire 66 sur l'un des arbres secondaires, dès lors que la synchronisation des deux pignons intermédiaires 65 et 67 reste indépendante de la rotation dudit arbre secondaire. It would be possible to implement the intermediate synchronization system 66 on one of the secondary shafts, since the synchronization of the two intermediate gears 65 and 67 remains independent of the rotation of said secondary shaft.

Claims

REVENDICATIONS
1 -Boîte de vitesses de véhicule automobile, à arbres parallèles munis d'une pluralité de pignons et comprenant un arbre primaire plein (9), et un arbre primaire creux ( 11 ), coaxiaux et reliés alternativement au moteur du véhicule par deux embrayages ( 10, 12), un arbre secondaire (7, 47) muni d'un pignon d' attaque (14, 48) engrenant avec une couronne ( 15) de différentiel (2) du véhicule, d'un pignon principal (32, 56) engrenant avec une denture (23 , 51 ) d'un des arbres primaires ( 11 , 9), et d'un système de synchronisation principal (31 , 57) apte à solidariser de manière sélective la rotation du pignon principal (32, 56) et du pignon d' attaque ( 14, 48), caractérisée par le fait qu' elle comprend un arbre intermédiaire (8) muni d'un premier pignon intermédiaire (33 , 65) lié en rotation avec l' arbre primaire plein (9), d'un deuxième pignon intermédiaire (34, 67) lié en rotation avec l' arbre primaire creux ( 11 ), au moins l'un (34, 67) des deux pignons intermédiaires étant libre en rotation par rapport à l' arbre intermédiaire (8), et d'un système de synchronisation intermédiaire (35, 66) apte à solidariser de manière sélective la rotation des deux pignons intermédiaires (33-34, 65-67). 2-Boîte de vitesses selon la revendication 1 , dans laquelle un des pignons intermédiaires (33, 65) est monté fixe sur l' arbre intermédiaire (8).1 -A motor vehicle gearbox, with parallel shafts provided with a plurality of gears and comprising a solid primary shaft (9), and a hollow primary shaft (11), coaxial and alternately connected to the vehicle engine by two clutches ( 10, 12), a secondary shaft (7, 47) having a driving pinion (14, 48) meshing with a gear differential ring (15) (2) of a main gear (32, 56). ) meshing with a toothing (23, 51) of one of the primary shafts (11, 9), and a main synchronization system (31, 57) adapted to selectively join the rotation of the main gear (32, 56). ) and the pinion gear (14, 48), characterized in that it comprises an intermediate shaft (8) provided with a first intermediate pinion (33, 65) rotatably connected to the solid primary shaft (9). ), a second intermediate gear (34, 67) rotatably connected to the hollow primary shaft (11), at least one (34, 67) of the two pinions intermediate being free in rotation relative to the intermediate shaft (8), and an intermediate synchronization system (35, 66) adapted to selectively join the rotation of the two intermediate gears (33-34, 65-67) . 2-gearbox according to claim 1, wherein one of the intermediate gears (33, 65) is fixedly mounted on the intermediate shaft (8).
3-Boîte de vitesses selon la revendication 1 ou 2, comprenant un autre arbre secondaire (6, 49), non coaxial avec l' arbre intermédiaire (8), et muni d'un autre pignon d' attaque ( 13, 50) engrenant avec la couronne de différentiel ( 15) précitée.3-gearbox according to claim 1 or 2, comprising another secondary shaft (6, 49), non-coaxial with the intermediate shaft (8), and provided with another pinion gear (13, 50) meshing with the aforementioned differential ring (15).
4-Boîte de vitesses selon l'une quelconque des revendications 1 à 3, présentant, lorsque les systèmes de synchronisation principal (31 , 57) et intermédiaire (35, 66) sont actionnés simultanément, deux rapport de transmission joints, l'un entre l' arbre primaire plein (9) et le différentiel (2), l' autre entre l' arbre primaire creux ( 11 ) et le différentiel (2).4-Gearbox according to any one of claims 1 to 3, having, when the main synchronization systems (31, 57) and intermediate (35, 66) are operated simultaneously, two transmission ratio, one between the solid primary shaft (9) and the differential (2), the other between the hollow primary shaft (11) and the differential (2).
5-Boîte de vitesses selon l'une quelconque des revendications 1 à 4, dans laquelle les deux liens de rotation entre chacun des deux pignons intermédiaires (33, 34) et l' arbre primaire correspondant (9, 11 ), sont tous les deux directs ou mettent chacun en jeu un nombre impair d' engrènements, les deux rapports joints étant des rapports de marche avant. 6-Boîte de vitesses selon la revendication 5, dans laquelle, le différentiel (2) étant situé dans une zone avant de la boîte de vitesses, le ou les ( 13 , 14) pignons d' attaque sont situés à l' extrémité avant de l' arbre secondaire correspondant (6, 7), et le pignon principal (32) précité est situé immédiatement à côté du pignon d' attaque ( 14) correspondant.5-gearbox according to any one of claims 1 to 4, wherein the two links of rotation between each of the two intermediate gears (33, 34) and the corresponding primary shaft (9, 11), are both direct or each involve an odd number of meshes, the two ratios attached being forward gears. The gearbox of claim 5, wherein, the differential (2) being located in a forward zone of the gearbox, the at least one (13, 14) drive gears are located at the front end of the gearbox. the corresponding secondary shaft (6, 7), and the aforementioned main pinion (32) is located immediately adjacent to the corresponding pinion gear (14).
7-Boîte de vitesses selon la revendication 5 ou 6, dans laquelle l' arbre intermédiaire est équipé d'un pignon de renvoi (36) engrenant avec un pignon de marche arrière (27) monté sur un arbre secondaire (6) de manière à établir un rapport de marche arrière. 8-Boîte de vitesses selon l'une quelconque des revendications 1 à 4, dans laquelle le lien de rotation entre l'un (67) des deux pignons intermédiaires (65, 67) et l' arbre primaire correspondant ( 11 ), est direct ou met en jeu un nombre impair d' engrènements, le lien de rotation de l' autre (65) pignon intermédiaire avec l' arbre primaire correspondant (9) étant indirect, mettant en jeu un nombre pair d' engrènements, de sorte que les deux rapports joints sont un rapport de marche avant et un rapport de marche arrière.7-gearbox according to claim 5 or 6, wherein the intermediate shaft is equipped with a pinion gear (36) meshing with a reverse gear (27) mounted on a secondary shaft (6) so as to establish a reverse gear. 8-gearbox according to any one of claims 1 to 4, wherein the rotational link between one (67) of the two intermediate gears (65, 67) and the corresponding primary shaft (11) is direct or involves an odd number of meshes, the rotation link of the other intermediate gear (65) with the corresponding primary shaft (9) being indirect, involving an even number of meshes, so that the two gear ratios are a forward gear and a reverse gear.
9-Boîte de vitesses selon la revendication 8, dans laquelle le pignon principal (56) engrène avec l'un (65) des pignons intermédiaires précités (65 , 67). 10-Procédé de transmission de couple moteur pour véhicule automobile, utilisant une boîte de vitesses équipée de deux arbres primaires (9, 11 ) alternativement reliés au moteur par deux embrayages ( 10, 12), d'un système de synchronisation principal (31 , 57) apte à solidariser de manière sélective la rotation d'un des arbres primaires ( 11 , 9) avec un différentiel (2) du véhicule, d'un système de synchronisation intermédiaire (35, 66) apte à solidariser de manière sélective la rotation des deux arbres primaires (9, 11 ), comprenant successivement les étapes suivantes : - Actionner les systèmes de synchronisation principal (31 , 57), et intermédiaire (35, 66),The gearbox of claim 8, wherein the main gear (56) meshes with one (65) of the aforementioned intermediate gears (65, 67). 10-Motor torque transmission method for a motor vehicle, using a gearbox equipped with two primary shafts (9, 11) alternately connected to the motor by two clutches (10, 12), of a main synchronization system (31, 57) adapted to selectively join the rotation of one of the primary shafts (11, 9) with a differential (2) of the vehicle, an intermediate synchronization system (35, 66) adapted to selectively join the rotation of the two primary shafts (9, 11), successively comprising the following steps: - Actuate the main synchronization systems (31, 57), and intermediate (35, 66),
- Faire adhérer l'un des embrayages ( 10, 12) pour établir l'un des rapports de transmission,- Adhering one of the clutches (10, 12) to establish one of the transmission ratios,
- Basculer l' adhérence d'un embrayage sur l' autre pour changer de rapport de transmission. - Switch the clutch on the other to change the transmission ratio.
PCT/FR2006/051181 2005-11-22 2006-11-16 Fast-transition gearbox WO2007060356A1 (en)

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FR0511785 2005-11-22
FR0511785A FR2893689B1 (en) 2005-11-22 2005-11-22 QUICK TRANSITION GEARBOX.

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DE102010037451A1 (en) * 2010-09-10 2012-03-15 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Drive system for a motor vehicle and motor vehicle with such a drive system

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JP2003120764A (en) * 2001-10-15 2003-04-23 Toyota Motor Corp Twin clutch transmission

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