WO2011148065A1 - Dual clutch transmission comprising a transfer link and a reverse gear - Google Patents

Dual clutch transmission comprising a transfer link and a reverse gear Download PDF

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Publication number
WO2011148065A1
WO2011148065A1 PCT/FR2011/000313 FR2011000313W WO2011148065A1 WO 2011148065 A1 WO2011148065 A1 WO 2011148065A1 FR 2011000313 W FR2011000313 W FR 2011000313W WO 2011148065 A1 WO2011148065 A1 WO 2011148065A1
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WO
WIPO (PCT)
Prior art keywords
shaft
gear
primary
gear ratio
transfer
Prior art date
Application number
PCT/FR2011/000313
Other languages
French (fr)
Inventor
Pascal Thery
Matthieu Rihn
Pierre Adolf
Nicolas Funalot
Original Assignee
Pascal Thery
Matthieu Rihn
Pierre Adolf
Nicolas Funalot
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 Pascal Thery, Matthieu Rihn, Pierre Adolf, Nicolas Funalot filed Critical Pascal Thery
Publication of WO2011148065A1 publication Critical patent/WO2011148065A1/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
    • 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
    • F16H2003/0826—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 wherein at least one gear on the input shaft, or on a countershaft is used for two different forward gear ratios
    • 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
    • F16H2003/0931—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 each countershaft having an output gear meshing with a single common gear on the output shaft
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds

Definitions

  • the present invention relates to a gearbox for a transmission of a motor vehicle.
  • a type of automatic gearbox known as a double-clutch transmission comprises two input primary shafts arranged along the same axis, and each connected to the shaft of an engine by a clutch that can operate dry or in the oil. .
  • Each primary shaft can transmit the movement received from the engine to one or more secondary trees in different gear ratios. These secondary shafts drive the drive wheels of the vehicle by a differential.
  • Each gear ratio comprises a pair of gear wheels forming a gear, transmitting the movement of a primary shaft to a secondary shaft in a gear ratio, to achieve a transmission speed ratio, hereafter called speed.
  • a pinion of each gear is fixed on its shaft, the other pinion mounted free in rotation, can be secured to its shaft by the axial sliding of a synchronizing sleeve making a synchronization of the speed of the free pinion, then a dog clutch of this pinion on his shaft engaging the gear ratio.
  • the speeds depend alternately on one and the other of the primary trees. By passing the torque gradually from one clutch to another, it ensures a continuity of transmission of the engine torque to the drive wheels during gear changes.
  • the clutch and gear controls include computer-controlled actuators receiving information about the operation of the vehicle and the demands of the driver.
  • An improvement to this type of gearbox presents a transmission comprising a transfer link between the two primary shafts, which reduces the speed of the second primary shaft relative to the first primary shaft, and at least five gear ratios to achieve at least six gears.
  • the first gear is performed by the transfer link arranged in series with the gear ratio giving the largest gear ratio, hereinafter called the second gear ratio,
  • a second reverse transfer link comprising a free intermediate gear between the transfer shaft and the second primary shaft, performs a speed reduction with a reversal of the direction of rotation of the second primary shaft, relative to the first primary shaft. driven by the engine.
  • the second primary shaft then drives a secondary shaft by the second gear ratio, to perform a reverse gear with a total gear that is close to that of the first gear, with generally a gear ratio a little lower.
  • the intermediate free gear having a specific axis has a size that can be inconvenient for the design of the gearbox, and entails costs.
  • these transmissions must include a range of speeds with a good staging, and a reverse gear with a suitable ratio.
  • the present invention is intended to avoid these disadvantages of the prior art.
  • a gearbox comprising a first and a second primary shaft disposed along a common axis and each connected by a clutch to a motor, and at least one secondary shaft driving the driving wheels of the vehicle, each primary shaft can be connected to the secondary shafts by gear ratios each comprising a driving pinion carried by a primary shaft, which meshes with a driven pinion carried by a secondary shaft, a second gear ratio realizing from the second primary shaft the second gear by driving the first secondary shaft, this gearbox further comprising a transfer link that can connect the two primary shafts together through a transfer shaft disposed parallel to these primary shafts, reducing the speed of the second primary shaft relative to that of the first primary shaft, characterized in that a pinion of a reverse ratio disposed on the second secondary shaft or on the transfer shaft meshes directly with the driven gear of the second gear ratio to perform reverse gearing .
  • An advantage of the gearbox according to the invention is that after the transfer link making a first reduction, by directly connecting a pinion disposed on the second secondary shaft or on the transfer shaft, with the driven pinion of the second gear ratio, one can drive the first secondary shaft with sufficient gear, and reversing its direction of rotation in a simple way, without using an intermediate idle gear.
  • the gearbox according to the invention may further comprise one or more of the following features, which may be combined with each other.
  • the gearbox comprises two secondary shafts, the transfer shaft comprising a longitudinal hollow, being traversed and supported by the first secondary shaft.
  • a dual synchronization sleeve controls on one side the reverse ratio, and on the other one of the gear ratios.
  • a dual sync sleeve can control on one side the second gear ratio, and on the other a sixth gear ratio.
  • this box comprising at least one fixed gear borne by a primary shaft which is common for two gear ratios.
  • the gearbox may include a drive gear of the third gear ratio, linked to the first input shaft, which meshes with a drive pinion of the transfer shaft.
  • the transfer shaft drives the second primary shaft, by driving gears and led a sixth gear ratio.
  • the gearbox comprises a single secondary shaft, supporting a dual synchronization sleeve which controls the transfer link on one side and the reverse gear on the other.
  • the invention also relates to a method of operating a gearbox comprising any one of the preceding characteristics, comprising a fifth gear made by simultaneously engaging a third gear ratio linked to the first primary shaft, and the transfer link. , and closing the second clutch driving the second primary shaft.
  • the gearbox may include a last gear ratio linked to the first primary shaft, which carries the sixth gear.
  • FIG. 1 is a diagram of a gearbox according to the invention comprising five gear ratios, which can achieve six or seven speeds;
  • FIGS. 2 and 3 are diagrams of similar gearboxes, comprising variants
  • FIG. 4 is a diagram of a gearbox with four gear ratios, can achieve six speeds
  • FIGS. 5 and 6 are diagrams of similar gearboxes, comprising variants
  • FIG. 7 is a diagram of a gearbox with three gear ratios, can achieve five speeds.
  • FIG. 1 represents a gearbox 1 receiving the movement of a motor M, driving two clutches C1, C2 arranged along the same axis.
  • Reduction ratios denoted II to VI each formed by a pair of pinions comprising a fixed pinion linked to a primary shaft 2, 4, and a free pinion carried by a secondary shaft 6, 10, which is engaged with the shaft on carrying a synchronizing sleeve, can directly connect these primary shafts to one of the secondary shafts to achieve the speeds noted in the same manner II to VI.
  • On the second primary shaft 4 is successively starting from the front side, a fixed gear 14 of the second gear ratio II, and a fixed gear 18 of the fourth IV and sixth VI gear ratio.
  • On the first primary shaft 2 is successively starting from the front side, fixed gears 24, 28 of the fifth V and the third III gear ratio.
  • first secondary shaft 6 there are successively starting from the front side, free gears 16, 20 of the second II and the sixth VI gear ratio, a double synchronizing sleeve 22 interposed between these free gears, allowing to craboter one either of these gears to engage the second II or the sixth VI speed.
  • a single synchronizing sleeve 42 placed in front of the free pinion 40 of the transfer link T comprises a hub connected to a hollow transfer shaft 44 crossed and carried by the first secondary shaft 6, and which is connected to the free pinion 20 of the sixth gear ratio VI.
  • the control of the single synchronizing sleeve 42 engages the transfer link T by linking the free pinion 40 to the transfer shaft 44, which connects the second primary shaft 4 to the first primary shaft 2 via this transfer shaft, with a reduction in the speed corresponding to the ratio of the transfer link T.
  • a free gear 36 of reverse ratio R which meshes directly with the free pinion 16 of the second gear ratio II carried by the first secondary shaft 6, and a free pinion 34 of the fourth gear ratio IV.
  • a double synchronizing sleeve 38 interposed between these free pinions 34, 36, for engaging one or the other of these pinions to engage the reverse ratio R or the fourth speed IV.
  • the operation of the gearbox 1 is as follows.
  • the transfer link T and the second gear ratio II are engaged simultaneously, then the first clutch C1 is closed.
  • the transfer link T and the second gear ratio II successively perform two speed reductions, to achieve the first speed I. It will be noted that the difference between the first I and the second II speed, is given by the ratio of the link T transfer.
  • a calculation made from the characteristics usually used for the gear ranges shows that the reduction ratio of the transfer link T which connects the fixed gear 28 of the third gear ratio III driving the second secondary shaft 10 to the fixed gear 18 of the sixth gear ratio VI driving the first secondary shaft 6, the transfer shaft 44 carried by the first secondary shaft being transversally closer to the primary shafts 2, 4 than the second secondary shaft, gives a gap between the first and second speed that suits well.
  • the engine torque of the first clutch C1 to the second clutch C2 to use only the second gear ratio II.
  • the engine M maintains a torque on the drive wheels during these different shifts.
  • a seventh speed VII can be achieved by simultaneously engaging the fifth gear ratio V and the transfer link T, then closing the second clutch C2.
  • the transfer link T then realizes an increase in the speed of the first primary shaft 2 relative to the second 4, which gives a seventh speed VII higher than the sixth speed VI. It will be noted that the transition from the sixth VI to the seventh VII speed is done with an interruption of the engine torque.
  • This arrangement avoids the installation of an additional intermediate gear, comprising a shaft disposed on a specific axis which would be laterally offset from the other axes of the primary and secondary shafts.
  • the total reduction of the reverse gear R comprises two successive reductions, given by the transfer link T, and by the ratio between the fixed gear 14 of the second gear ratio II, and the driven free gear 36 of the gear ratio.
  • Rear R This last gear ratio must not be very high, can be easily achieved with a free pinion 36 not too large, which allows to define a transverse distance between the two secondary shafts 6, 10 similar to those generally used.
  • the free gear 36 of the reverse ratio R must have a diameter a little smaller than the free gear 16 of the second gear ratio II, to obtain a gear ratio R a little lower than that of the first gear I.
  • this gearbox could include a seventh reduction ratio, the fixed gear 24 of the fifth gear ratio V meshing with a free gear of the seventh gear ratio carried by the first secondary shaft 6.
  • the fourth and sixth IV VI gear ratios can then comprise two separate fixed gears, carried by the second primary shaft 4.
  • FIG. 2 shows a gearbox 61 having the following differences with respect to the gearbox 1 shown in FIG.
  • a fixed gear 60 of the transfer link T carried by the first primary shaft 2 and disposed in front of the fixed gear 28 of the third gear ratio III, meshes with the free gear 40 of the transfer link T.
  • the hub of the single synchronization sleeve 42 is connected to the free pinion 40 of the transfer link T.
  • FIG. 3 presents a gearbox 71 having the following differences with respect to the gearbox 1 presented in FIG.
  • the transfer link T and the reverse gear R are engaged simultaneously, then the first clutch C1 is closed.
  • the first primary shaft 2 drives the transfer shaft 44 and then the second primary shaft 4, which drives the second secondary shaft 10 via the intermediate idle gear 70.
  • This particular arrangement requires an additional pinion to perform the reverse gear R, but does not set a distance between the two secondary shafts 6, 10 which no longer have pinion meshing directly between them.
  • Figure 4 shows a gearbox 81 having a single secondary shaft 6, and a transfer shaft 44 disposed parallel to the secondary shaft, which is carried directly by the housing of the gearbox.
  • a fixed gear 82 of the sixth gear ratio VI On the first primary shaft 2 is successively starting from the front side, a fixed gear 82 of the sixth gear ratio VI, a fixed gear 60 of the transfer link T, and a fixed gear 28 of the third gear ratio III.
  • a synchronizing double sleeve 94 interposed between the free pinions 90, 92 of the transfer shaft 44 makes it possible to link one or the other of these idle gears with the transfer shaft, to engage the reverse ratio. R or the transfer link T.
  • the operation of the gearbox 81 is as follows.
  • the first gear I simultaneously uses the transfer link T and the second gear ratio II.
  • the second II, third III and fourth IV speeds one directly uses the . corresponding gear ratio.
  • the third gear ratio III is simultaneously engaged with the transfer link T.
  • the speed of the first primary shaft 2 is increased by the transfer link T.
  • the sixth VI and last speed which generally achieves the majority of kilometers, implements a single meshing to drive the secondary shaft 6, which limits losses and provides a good performance at this speed.
  • the reverse ratio R and the second gear ratio II are engaged simultaneously, then the first clutch C1 is closed. This is done from the first primary shaft 2 a drive of the transfer shaft 44, then a direct drive of the secondary shaft 6 by the free gear 90 of reverse ratio R meshing with the free gear 16 of the second report of reduction II.
  • This gearbox 81 comprises only three sleeves 84, 86, 94 each performing a double synchronization, controlled by three forks, which reduces the number of actuators to perform these commands, as well as the size and mass of this gearbox.
  • FIG. 5 shows a gearbox 101 having the following differences with respect to the gearbox 81 shown in FIG. 4.
  • the fixed gear 40 of the transfer shaft 44 meshes with the fixed gear 28 of the third gear ratio III, carried by the first primary shaft 2. This saves a pinion.
  • the ratio of the transfer link T can not be set independently of the third III and the fourth IV gear ratio.
  • FIG. 6 shows a gearbox 111 having the following differences with respect to the gearbox 81 shown in FIG. 4.
  • the transfer link T and the reverse ratio R are engaged simultaneously, then the first clutch C1 is closed.
  • the first primary shaft 2 drives the transfer shaft 44, which drives the secondary shaft 6 via the intermediate idle gear 70, then the second secondary shaft 4.
  • FIG. 7 shows a gearbox 121 comprising the following difference with respect to the gearbox 81 shown in FIG. 4, the sixth gear ratio VI is eliminated, the gearwheels 82, 20 of this ratio and the synchronizer of the free gear being removed.
  • gearbox 121 comprising three gear ratios, which can achieve five times, the fifth gear V being obtained by the transfer T used in series with the third gear ratio III, the clutch C2 being closed.
  • FIG. 8 shows a gearbox 131 having the following difference with respect to the gearbox 121 shown in FIG. 7, an intermediate gear 70 mounted freely on a shaft 72 meshes with the free gear 90 of the gear ratio. rear R, and secondly with the fixed gear 14 of the second gear ratio II.
  • FIG. 9 shows a gearbox 141 having the following difference with respect to the gearbox 131 shown in FIG. 8.
  • the gears 28, 30 of the third gear ratio III are arranged on the front side with respect to the synchronization sleeve 86, and fixed gears 40, 60 of the transfer link T.

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

Abstract

Disclosed is a transmission comprising a first (2) and a second (4) input shaft and at least one output shaft (6, 10) that drive the drive wheels of the vehicle. Each input shaft (2, 4) can be connected to the output shafts (6, 10) using step-down gears, each of which comprises a driving pinion that is supported on an input shaft and meshes with a driven pinion. A second step-down gear (II) implements the second speed (II) using the second input shaft (4) by driving the first output shaft (6). The disclosed transmission further comprises a transfer link (T) that can interconnect the two input shafts (2, 4) via a transfer shaft (44) which extends parallel to the input shafts, the transfer link (T) interconnecting the input shafts (2, 4) by reducing the speed of the second input shaft (4) in relation to the speed of the first input shaft (2). Said transmission is characterized in that a pinion (16) of a reverse gear (R) which is disposed on the second output shaft (10) or on the transfer shaft (44) directly meshes with the driven pinion (16) of the second step-down gear (II) to implement the reverse speed.

Description

BOITE DE VITESSES A DOUBLE EMBRAYAGE COMPORTANT UNE LIAISON DE TRANSFERT ET UN RAPPORT DE MARCHE ARRIERE  DOUBLE CLUTCH GEARBOX COMPRISING A TRANSFER LINK AND A REVERSE RATE
La présente invention concerne une boîte de vitesses pour une transmission d'un véhicule automobile. The present invention relates to a gearbox for a transmission of a motor vehicle.
Un type de boîte de vitesses automatique connu appelé transmission à double embrayage, comporte deux arbres primaires d'entrée disposés suivant un même axe, et reliés chacun à l'arbre d'un moteur par un embrayage pouvant fonctionner à sec ou dans l'huile. Chaque arbre primaire peut transmettre le mouvement reçu du moteur, à un ou plusieurs arbres secondaires suivant différents rapports de démultiplication. Ces arbres secondaires entraînent par un différentiel les roues motrices du véhicule.  A type of automatic gearbox known as a double-clutch transmission comprises two input primary shafts arranged along the same axis, and each connected to the shaft of an engine by a clutch that can operate dry or in the oil. . Each primary shaft can transmit the movement received from the engine to one or more secondary trees in different gear ratios. These secondary shafts drive the drive wheels of the vehicle by a differential.
Chaque rapport de démultiplication comporte un couple de pignons formant un engrenage, transmettant le mouvement d'un arbre primaire à un arbre secondaire suivant un rapport de démultiplication, pour réaliser un rapport de vitesse de la transmission, appelé par la suite vitesse.  Each gear ratio comprises a pair of gear wheels forming a gear, transmitting the movement of a primary shaft to a secondary shaft in a gear ratio, to achieve a transmission speed ratio, hereafter called speed.
Un pignon de chaque engrenage est fixé sur son arbre, l'autre pignon monté libre en rotation, peut être rendu solidaire de son arbre par le coulissement axial d'un manchon de synchronisation réalisant une synchronisation de la vitesse du pignon libre, puis un crabotage de ce pignon sur son arbre engageant le rapport de démultiplication.  A pinion of each gear is fixed on its shaft, the other pinion mounted free in rotation, can be secured to its shaft by the axial sliding of a synchronizing sleeve making a synchronization of the speed of the free pinion, then a dog clutch of this pinion on his shaft engaging the gear ratio.
Les vitesses prises dans un ordre croissant, dépendent alternativement de l'un et de l'autre des arbres primaires. En passant le couple progressivement d'un embrayage à l'autre, on assure une continuité de la transmission du couple moteur vers les roues motrices pendant les changements de vitesse.  The speeds, taken in increasing order, depend alternately on one and the other of the primary trees. By passing the torque gradually from one clutch to another, it ensures a continuity of transmission of the engine torque to the drive wheels during gear changes.
Les commandes des embrayages et des vitesses comprennent des actionneurs pilotés par un calculateur, recevant des informations sur le fonctionnement du véhicule et sur les demandes du conducteur.  The clutch and gear controls include computer-controlled actuators receiving information about the operation of the vehicle and the demands of the driver.
Un perfectionnement à ce type de boîte de vitesses, décrit dans le document EP-A1 -2128487, présente une transmission comprenant une liaison de transfert entre les deux arbres primaires, qui réduit la vitesse du deuxième arbre primaire par rapport au premier arbre primaire, et au moins cinq rapports de démultiplication pour réaliser au moins six vitesses. La première vitesse est réalisée par la liaison de transfert disposée en série avec le rapport de démultiplication donnant la plus grande démultiplication, appelé par la suite deuxième rapport de démultiplication, An improvement to this type of gearbox, described in document EP-A1-2128487, presents a transmission comprising a transfer link between the two primary shafts, which reduces the speed of the second primary shaft relative to the first primary shaft, and at least five gear ratios to achieve at least six gears. The first gear is performed by the transfer link arranged in series with the gear ratio giving the largest gear ratio, hereinafter called the second gear ratio,
Une deuxième liaison de transfert de marche arrière, comportant un pignon libre intermédiaire entre l'arbre de transfert et le deuxième arbre primaire, réalise une réduction de vitesse avec une inversion du sens de rotation de ce deuxième arbre primaire, par rapport au premier arbre primaire entraîné par le moteur. Le deuxième arbre primaire entraîne ensuite un arbre secondaire par le deuxième rapport de démultiplication, pour réaliser une marche arrière comportant une démultiplication totale qui est proche de celle de la première vitesse, avec généralement une démultiplication un peu plus faible.  A second reverse transfer link, comprising a free intermediate gear between the transfer shaft and the second primary shaft, performs a speed reduction with a reversal of the direction of rotation of the second primary shaft, relative to the first primary shaft. driven by the engine. The second primary shaft then drives a secondary shaft by the second gear ratio, to perform a reverse gear with a total gear that is close to that of the first gear, with generally a gear ratio a little lower.
Le pignon libre intermédiaire disposant d'un axe spécifique comporte un encombrement qui peut être gênant pour le dessin de la boîte de vitesses, èt qui entraîne des coûts.  The intermediate free gear having a specific axis has a size that can be inconvenient for the design of the gearbox, and entails costs.
Un problème qui se pose avec ce type de transmission comprenant une liaison de transfert, est de réaliser des boîtes de vitesses compactes, comprenant un nombre réduit de pignons. De plus ces transmissions doivent comporter une gamme de vitesses disposant d'un bon étagement, et une marche arrière disposant d'un rapport adapté.  A problem that arises with this type of transmission comprising a transfer link, is to achieve compact gearboxes, comprising a reduced number of gears. In addition these transmissions must include a range of speeds with a good staging, and a reverse gear with a suitable ratio.
La présente invention a notamment pour but d'éviter ces inconvénients de l'art antérieur.  The present invention is intended to avoid these disadvantages of the prior art.
Elle propose à cet effet une boîte de vitesses comportant un premier et un deuxième arbre primaire disposés suivant un axe commun et reliés chacun par un embrayage à un moteur, et au moins un arbre secondaire entraînant les roues motrices du véhicule, chaque arbre primaire pouvant être relié aux arbres secondaires par des rapports de démultiplication comprenant chacun un pignon menant porté par un arbre primaire, qui engrène avec un pignon mené porté par un arbre secondaire, un deuxième rapport de démultiplication réalisant à partir du deuxième arbre primaire la deuxième vitesse en entraînant le premier arbre secondaire, cette boîte de vitesses comportant de plus une liaison de transfert pouvant relier les deux arbres primaires entre eux en passant par un arbre de transfert disposé parallèlement à ces arbres primaires, en réduisant la vitesse du deuxième arbre primaire par rapport à celle du premier arbre primaire, caractérisée en ce qu'un pignon d'un rapport de marche arrière disposé sur le deuxième arbre secondaire ou sur l'arbre de transfert, engrène directement avec le pignon mené du deuxième rapport de démultiplication pour réaliser la marche arrière. It proposes for this purpose a gearbox comprising a first and a second primary shaft disposed along a common axis and each connected by a clutch to a motor, and at least one secondary shaft driving the driving wheels of the vehicle, each primary shaft can be connected to the secondary shafts by gear ratios each comprising a driving pinion carried by a primary shaft, which meshes with a driven pinion carried by a secondary shaft, a second gear ratio realizing from the second primary shaft the second gear by driving the first secondary shaft, this gearbox further comprising a transfer link that can connect the two primary shafts together through a transfer shaft disposed parallel to these primary shafts, reducing the speed of the second primary shaft relative to that of the first primary shaft, characterized in that a pinion of a reverse ratio disposed on the second secondary shaft or on the transfer shaft meshes directly with the driven gear of the second gear ratio to perform reverse gearing .
Un avantage de la boîte de vitesses suivant l'invention, est qu'après la liaison de transfert réalisant un première réduction, en reliant directement un pignon disposé sur le deuxième arbre secondaire ou sur l'arbre de transfert, avec le pignon mené du deuxième rapport de démultiplication, on peut entraîner le premier arbre secondaire avec une démultiplication suffisante, et en inversant son sens de rotation de manière simple, sans utiliser de pignon libre intermédiaire.  An advantage of the gearbox according to the invention is that after the transfer link making a first reduction, by directly connecting a pinion disposed on the second secondary shaft or on the transfer shaft, with the driven pinion of the second gear ratio, one can drive the first secondary shaft with sufficient gear, and reversing its direction of rotation in a simple way, without using an intermediate idle gear.
La boîte de vitesses selon l'invention peut en outre comporter une ou plusieurs des caractéristiques suivantes, qui peuvent être combinées entre elles.  The gearbox according to the invention may further comprise one or more of the following features, which may be combined with each other.
Selon un mode de réalisation, la boîte de vitesses comporte deux arbres secondaires, l'arbre de transfert comprenant un creux longitudinal, étant traversé et supporté par le premier arbre secondaire.  According to one embodiment, the gearbox comprises two secondary shafts, the transfer shaft comprising a longitudinal hollow, being traversed and supported by the first secondary shaft.
Avantageusement, un manchon de synchronisation double commande d'un côté le rapport de marche arrière, et de l'autre un des rapports de démultiplication.  Advantageously, a dual synchronization sleeve controls on one side the reverse ratio, and on the other one of the gear ratios.
En particulier, un manchon de synchronisation double peut commander d'un côté le deuxième rapport de démultiplication, et de l'autre un sixième rapport de démultiplication.  In particular, a dual sync sleeve can control on one side the second gear ratio, and on the other a sixth gear ratio.
Avantageusement, la distance transversale entre le premier arbre secondaire et les arbres primaires, et inférieure à celle entre le deuxième arbre secondaire et ces arbres primaires, cette boîte comportant au moins un pignon fixe porté par un arbre primaire qui est commun pour deux rapports de démultiplication.  Advantageously, the transverse distance between the first secondary shaft and the primary shafts, and less than that between the second secondary shaft and these primary shafts, this box comprising at least one fixed gear borne by a primary shaft which is common for two gear ratios. .
En particulier, la boîte de vitesses peut comporter un pignon menant du troisième rapport de démultiplication, lié au premier arbre primaire, qui engrène avec un pignon d'entraînement de l'arbre de transfert.  In particular, the gearbox may include a drive gear of the third gear ratio, linked to the first input shaft, which meshes with a drive pinion of the transfer shaft.
Avantageusement, l'arbre de transfert entraîne le deuxième arbre primaire, par les pignons menant et mené d'un sixième rapport de démultiplication. Selon un autre mode de réalisation, la boîte de vitesses comporte un seul arbre secondaire, supportant un manchon de synchronisation double qui commande d'un côté la liaison de transfert, et de l'autre le rapport de marche arrière. Advantageously, the transfer shaft drives the second primary shaft, by driving gears and led a sixth gear ratio. According to another embodiment, the gearbox comprises a single secondary shaft, supporting a dual synchronization sleeve which controls the transfer link on one side and the reverse gear on the other.
L'invention a aussi pour objet un procédé de fonctionnement d'une boîte de vitesses comprenant l'une quelconque des caractéristiques précédentes, comportant une cinquième vitesse réalisée en engageant simultanément un troisième rapport de démultiplication lié au premier arbre primaire, et la liaison de transfert, et en fermant le deuxième embrayage entraînant le deuxième arbre primaire.  The invention also relates to a method of operating a gearbox comprising any one of the preceding characteristics, comprising a fifth gear made by simultaneously engaging a third gear ratio linked to the first primary shaft, and the transfer link. , and closing the second clutch driving the second primary shaft.
En particulier, la boîte de vitesses peut comporter un dernier rapport de démultiplication lié au premier arbre primaire, qui réalise la sixième vitesse.  In particular, the gearbox may include a last gear ratio linked to the first primary shaft, which carries the sixth gear.
L'invention sera mieux comprise et d'autres caractéristiques et avantages apparaîtront plus clairement à la lecture de la description détaillée ci-après donnée à titre d'exemple, et faite en référence aux dessins annexés dans lesquels :  The invention will be better understood and other features and advantages will appear more clearly on reading the detailed description given below by way of example, and with reference to the appended drawings in which:
- la figure 1 est un schéma d'une boîte de vitesses suivant l'invention comprenant cinq rapports de démultiplication, pouvant réaliser six ou sept vitesses ;  - Figure 1 is a diagram of a gearbox according to the invention comprising five gear ratios, which can achieve six or seven speeds;
- les figures 2 et 3 sont des schémas de boîtes de vitesses similaires, comportant des variantes ;  FIGS. 2 and 3 are diagrams of similar gearboxes, comprising variants;
- la figure 4 est un schéma d'une boîte de vitesses comprenant quatre rapports de démultiplication, pouvant réaliser six vitesses ;  - Figure 4 is a diagram of a gearbox with four gear ratios, can achieve six speeds;
- les figures 5 et 6 sont des schémas de boîtes de vitesses similaires, comportant des variantes ;  FIGS. 5 and 6 are diagrams of similar gearboxes, comprising variants;
- la figure 7 est un schéma d'une boîte de vitesses comprenant trois rapports de démultiplication, pouvant réaliser cinq vitesses ; et  - Figure 7 is a diagram of a gearbox with three gear ratios, can achieve five speeds; and
- les figures 8 et 9 sont des schémas de boîtes de vitesses similaires, comportant des variantes.  - Figures 8 and 9 are similar gearbox diagrams, with variants.
La figure 1 représente une boîte de vitesses 1 recevant le mouvement d'un moteur M, entraînant deux embrayages C1 , C2 disposés suivant un même axe. Le premier embrayage C1 disposé axialement du côté du moteur appelé côté avant, est lié à un premier arbre primaire plein 2, et le deuxième embrayage C2 disposé axialement du côté opposé au moteur appelé côté arrière, est lié à un deuxième arbre primaire 4 comportant un creux longitudinal qui est traversé par le premier arbre primaire. FIG. 1 represents a gearbox 1 receiving the movement of a motor M, driving two clutches C1, C2 arranged along the same axis. The first clutch C1 arranged axially on the side of the engine called the front side, is connected to a first solid primary shaft 2, and the second clutch C2 disposed axially on the opposite side to the engine called side rear, is connected to a second primary shaft 4 having a longitudinal recess which is traversed by the first primary shaft.
Deux arbres secondaires 6, 10 disposés parallèlement aux arbres primaires 2, 4, comportent chacun du côté avant un pignon de sortie 8, 12 qui engrène avec un couronné d'un différentiel non représenté.  Two secondary shafts 6, 10 arranged parallel to the primary shafts 2, 4, each comprise on the front side an output gear 8, 12 which meshes with a crown of a differential not shown.
Des rapports de démultiplication notés II à VI, formés chacun par un couple de pignons comprenant un pignon fixe lié à un arbre primaire 2, 4, et un pignon libre porté par un arbre secondaire 6, 10, qui est engagé avec l'arbre le portant par un manchon de synchronisation, peuvent relier directement ces arbres primaires à un des arbres secondaires pour réaliser les vitesses notés de la même manière II à VI.  Reduction ratios denoted II to VI, each formed by a pair of pinions comprising a fixed pinion linked to a primary shaft 2, 4, and a free pinion carried by a secondary shaft 6, 10, which is engaged with the shaft on carrying a synchronizing sleeve, can directly connect these primary shafts to one of the secondary shafts to achieve the speeds noted in the same manner II to VI.
Sur le deuxième arbre primaire 4 on trouve successivement en partant du côté avant, un pignon fixe 14 du deuxième rapport de démultiplication II, et un pignon fixe 18 du quatrième IV et sixième VI rapport de démultiplication. Sur le premier arbre primaire 2 on trouve successivement en partant du côté avant, des pignons fixes 24, 28 du cinquième V et du troisième III rapport de démultiplication.  On the second primary shaft 4 is successively starting from the front side, a fixed gear 14 of the second gear ratio II, and a fixed gear 18 of the fourth IV and sixth VI gear ratio. On the first primary shaft 2 is successively starting from the front side, fixed gears 24, 28 of the fifth V and the third III gear ratio.
Sur le premier arbre secondaire 6 on trouve successivement en partant du côté avant, des pignons libres 16, 20 du deuxième II et du sixième VI rapport de démultiplication, un manchon double de synchronisation 22 intercalé entre ces pignons libres, permettant de craboter l'un ou l'autre de ces pignons pour engager la deuxième II ou la sixième VI vitesse.  On the first secondary shaft 6 there are successively starting from the front side, free gears 16, 20 of the second II and the sixth VI gear ratio, a double synchronizing sleeve 22 interposed between these free gears, allowing to craboter one either of these gears to engage the second II or the sixth VI speed.
On trouve ensuite un pignon libre 40 de la liaison de transfert T, qui engrène avec le pignon fixe 28 du troisième rapport de démultiplication III. Un manchon simple de synchronisation 42 placé en avant du pignon libre 40 de la liaison de transfert T, comporte un moyeu lié à un arbre de transfert creux 44 traversé et porté par le premier arbre secondaire 6, et qui est lié au pignon libre 20 du sixième rapport de démultiplication VI.  Then there is a free pinion 40 of the transfer link T, which meshes with the fixed gear 28 of the third gear ratio III. A single synchronizing sleeve 42 placed in front of the free pinion 40 of the transfer link T, comprises a hub connected to a hollow transfer shaft 44 crossed and carried by the first secondary shaft 6, and which is connected to the free pinion 20 of the sixth gear ratio VI.
La commande du manchon simple de synchronisation 42 engage la liaison de transfert T en liant le pignon libre 40 à l'arbre de transfert 44, ce qui relie le deuxième arbre primaire 4 au premier arbre primaire 2 en passant par cet arbre de transfert, avec une réduction de la vitesse correspondant au rapport de la liaison de transfert T. Sur le deuxième arbre secondaire 10 on trouve en partant du côté avant, un pignon libre 36 de rapport de marche arrière R qui engrène directement avec le pignon libre 16 du deuxième rapport de démultiplication II porté par le premier arbre secondaire 6, et un pignon libre 34 du quatrième rapport de démultiplication IV. Un manchon double de synchronisation 38 intercalé entre ces pignons libres 34, 36, permettant de craboter l'un ou l'autre de ces pignons pour engager le rapport de marche arrière R ou la quatrième vitesse IV. The control of the single synchronizing sleeve 42 engages the transfer link T by linking the free pinion 40 to the transfer shaft 44, which connects the second primary shaft 4 to the first primary shaft 2 via this transfer shaft, with a reduction in the speed corresponding to the ratio of the transfer link T. On the second secondary shaft 10 is found starting from the front side, a free gear 36 of reverse ratio R which meshes directly with the free pinion 16 of the second gear ratio II carried by the first secondary shaft 6, and a free pinion 34 of the fourth gear ratio IV. A double synchronizing sleeve 38 interposed between these free pinions 34, 36, for engaging one or the other of these pinions to engage the reverse ratio R or the fourth speed IV.
On trouve ensuite successivement des pignons libres 26, 30 du cinquième V et du troisième III rapport de démultiplication, un manchon double de synchronisation 32 intercalé entre ces pignons libres, permettant de craboter l'un ou l'autre de ces pignons pour engager la cinquième V ou la troisième III vitesse.  Then there are successively free gears 26, 30 of the fifth V and the third III gear ratio, a double synchronizing sleeve 32 interposed between these free gears, allowing to jibe one or the other of these gears to engage the fifth V or the third III speed.
On notera que pour réaliser le quatrième IV et le sixième VI rapport de démultiplication avec un pignon fixe commun 18, et obtenir les bons écarts entre ces rapports, il faut prévoir en partant des arbres primaires 2, 4, une distance du premier arbre secondaire 6 qui est inférieure à celle du deuxième arbre secondaire 10.  Note that to achieve the fourth IV and the sixth VI gear ratio with a common fixed gear 18, and get the good differences between these reports, it is necessary to start from the primary shafts 2, 4, a distance from the first secondary shaft 6 which is smaller than that of the second secondary shaft 10.
Le fonctionnement de la boîte de vitesses 1 est le suivant.  The operation of the gearbox 1 is as follows.
Pour la première vitesse I, la liaison de transfert T et le deuxième rapport de démultiplication II sont engagés simultanément, puis le premier embrayage C1 est fermé. La liaison de transfert T et le deuxième rapport de démultiplication II effectuent successivement deux réductions de vitesse, pour réaliser la première vitesse I. On notera que l'écart entre la première I et la deuxième II vitesse, est donné par le rapport de la liaison de transfert T.  For the first speed I, the transfer link T and the second gear ratio II are engaged simultaneously, then the first clutch C1 is closed. The transfer link T and the second gear ratio II successively perform two speed reductions, to achieve the first speed I. It will be noted that the difference between the first I and the second II speed, is given by the ratio of the link T transfer.
Un calcul réalisé à partir des caractéristiques habituellement utilisées pour les gammes de rapports, montre que le rapport de réduction de la liaison de transfert T qui relie le pignon fixe 28 du troisième rapport de démultiplication III entraînant le deuxième arbre secondaire 10, au pignon fixe 18 du sixième rapport de démultiplication VI entraînant le premier arbre secondaire 6, l'arbre de transfert 44 porté par ce premier arbre secondaire étant transversalement plus proche des arbres primaires 2, 4 que le deuxième arbre secondaire, donne un écart entre la première et la deuxième vitesse qui convient bien. Pour le passage de la première I à la deuxième II vitesse, on bascule le couple moteur du premier embrayage C1 au deuxième embrayage C2, pour utiliser uniquement le deuxième rapport de démultiplication II. On réalise ensuite successivement les passages du deuxième II à la sixième VI vitesse, en engageant le rapport de démultiplication suivant, puis en basculant le couple moteur d'un embrayage à l'autre. Le moteur M maintient un couple sur les roues motrices pendant ces différents passages de vitesses. A calculation made from the characteristics usually used for the gear ranges, shows that the reduction ratio of the transfer link T which connects the fixed gear 28 of the third gear ratio III driving the second secondary shaft 10 to the fixed gear 18 of the sixth gear ratio VI driving the first secondary shaft 6, the transfer shaft 44 carried by the first secondary shaft being transversally closer to the primary shafts 2, 4 than the second secondary shaft, gives a gap between the first and second speed that suits well. For the passage of the first I to the second II gear, the engine torque of the first clutch C1 to the second clutch C2, to use only the second gear ratio II. Then successively passes the passages of the second II to the sixth VI speed, engaging the next gear ratio, then switching the engine torque from one clutch to another. The engine M maintains a torque on the drive wheels during these different shifts.
Une septième vitesse VII peut être réalisée, en engageant simultanément le cinquième rapport de démultiplication V et la liaison de transfert T, puis en fermant le deuxième embrayage C2. La liaison de transfert T réalise alors une augmentation de la vitesse du premier arbre primaire 2 par rapport au deuxième 4, qui donne une septième vitesse VII plus élevée que la sixième vitesse VI. On notera que le passage de la sixième VI à la septième VII vitesse, se fait avec une interruption du couple moteur.  A seventh speed VII can be achieved by simultaneously engaging the fifth gear ratio V and the transfer link T, then closing the second clutch C2. The transfer link T then realizes an increase in the speed of the first primary shaft 2 relative to the second 4, which gives a seventh speed VII higher than the sixth speed VI. It will be noted that the transition from the sixth VI to the seventh VII speed is done with an interruption of the engine torque.
Pour un démarrage du véhicule en marche arrière, la liaison de transfert For a vehicle start in reverse, the transfer link
T et le rapport de marche arrière R sont engagés simultanément, puis le premier embrayage C1 est fermé. La liaison de transfert T effectue une réduction de la vitesse du deuxième arbre primaire 4, puis le pignon fixe 14 du deuxième rapport de démultiplication II entraîne le pignon libre 16 de ce rapport servant de pignon intermédiaire, qui entraîne à son tour directement le pignon libre 36 du rapport de marche arrière R. T and the reverse ratio R are engaged simultaneously, then the first clutch C1 is closed. The transfer link T makes a reduction in the speed of the second primary shaft 4, then the fixed gear 14 of the second gear ratio II drives the free gear 16 of this ratio acting as an intermediate gear, which in turn drives the free gear directly. 36 reverse gear R.
Cette disposition permet d'éviter l'installation d'un pignon intermédiaire supplémentaire, comprenant un arbre disposé sur un axe spécifique qui serait latéralement décalé par rapport aux autres axes des arbres primaires et secondaires.  This arrangement avoids the installation of an additional intermediate gear, comprising a shaft disposed on a specific axis which would be laterally offset from the other axes of the primary and secondary shafts.
On notera que la démultiplication totale de la marche arrière R comporte deux démultiplications successives, données par la liaison de transfert T, et par le rapport entre le pignon fixe 14 du deuxième rapport de démultiplication II, et le pignon libre mené 36 du rapport de marche arrière R. Cette dernière démultiplication ne devant pas être très élevée, peut être facilement réalisée avec un pignon libre mené 36 pas trop grand, ce qui permet de définir une distance transversale entre les deux arbres secondaires 6, 10 similaire à celles généralement utilisées. En pratique le pignon libre 36 du rapport de marche arrière R doit avoir un diamètre un peu plus petit que le pignon libre 16 du deuxième rapport de démultiplication II, pour obtenir une démultiplication de marche arrière R un peu plus faible que celle de la première vitesse I. It will be noted that the total reduction of the reverse gear R comprises two successive reductions, given by the transfer link T, and by the ratio between the fixed gear 14 of the second gear ratio II, and the driven free gear 36 of the gear ratio. Rear R. This last gear ratio must not be very high, can be easily achieved with a free pinion 36 not too large, which allows to define a transverse distance between the two secondary shafts 6, 10 similar to those generally used. In practice the free gear 36 of the reverse ratio R must have a diameter a little smaller than the free gear 16 of the second gear ratio II, to obtain a gear ratio R a little lower than that of the first gear I.
En variante non représentée, cette boîte de vitesses pourrait comporter un septième rapport de démultiplication, le pignon fixe 24 du cinquième rapport de démultiplication V engrenant avec un pignon libre du septième rapport de démultiplication porté par le premier arbre secondaire 6. Les quatrième IV et sixième VI rapports de démultiplication peuvent alors comporter deux pignons fixes distincts, portés par le deuxième arbre primaire 4.  In a variant not shown, this gearbox could include a seventh reduction ratio, the fixed gear 24 of the fifth gear ratio V meshing with a free gear of the seventh gear ratio carried by the first secondary shaft 6. The fourth and sixth IV VI gear ratios can then comprise two separate fixed gears, carried by the second primary shaft 4.
Une septième vitesse réalisée par ce septième rapport de démultiplication, utilisant un seul engrenage pour entraîner l'arbre secondaire, comporterait un bon rendement. De plus le passage de la sixième à la septième vitesse se ferait en maintenant un couple moteur.  A seventh gear made by this seventh gear ratio, using a single gear to drive the secondary shaft, would have a good performance. Moreover the passage of the sixth to the seventh speed would be done while maintaining a torque engine.
La figure 2 présente une boîte de vitesses 61 comportant les différences suivantes par rapport à la boîte de vitesses 1 présentée figure 1.  FIG. 2 shows a gearbox 61 having the following differences with respect to the gearbox 1 shown in FIG.
Un pignon fixe 60 de la liaison de transfert T, porté par le premier arbre primaire 2 et disposé en avant du pignon fixe 28 du troisième rapport de démultiplication III, engrène avec le pignon libre 40 de la liaison de transfert T.  A fixed gear 60 of the transfer link T, carried by the first primary shaft 2 and disposed in front of the fixed gear 28 of the third gear ratio III, meshes with the free gear 40 of the transfer link T.
Cette disposition particulière nécessitant un pignon supplémentaire, permet d'ajuster de manière indépendante le rapport entre le premier arbre primaire 2 et l'arbre de transfert 44, ce qui permet de fixer librement le rapport total de la liaison de transfert T, et donc l'écart entre la première I et la deuxième II vitesse.  This particular arrangement requiring an additional pinion makes it possible to adjust independently the ratio between the first primary shaft 2 and the transfer shaft 44, which makes it possible to freely set the total ratio of the transfer link T, and therefore the difference between the first I and the second II speed.
Par ailleurs, le moyeu du manchon simple de synchronisation 42 est lié au pignon libre 40 de la liaison de transfert T.  Furthermore, the hub of the single synchronization sleeve 42 is connected to the free pinion 40 of the transfer link T.
La figure 3 présente une boîte de vitesses 71 comportant les différences suivantes par rapport à la boîte de vitesses 1 présentée figure 1.  FIG. 3 presents a gearbox 71 having the following differences with respect to the gearbox 1 presented in FIG.
Un pignon intermédiaire 70 monté libre sur un arbre 72, engrène d'une part avec le pignon fixe 14 du deuxième rapport de démultiplication II, et d'autre part avec le pignon libre 36 du rapport de marche arrière R.  An intermediate gear 70 mounted free on a shaft 72, meshes with the fixed gear 14 of the second gear ratio II and with the idle gear 36 of the reverse gear ratio R.
Pour un démarrage du véhicule en marche arrière, la liaison de transfert T et le rapport de marche arrière R sont engagés simultanément, puis le premier embrayage C1 est fermé. Le premier arbre primaire 2 entraîne l'arbre de transfert 44 puis le deuxième arbre primaire 4, qui entraîne le deuxième arbre secondaire 10 par l'intermédiaire du pignon libre intermédiaire 70. For starting the vehicle in reverse, the transfer link T and the reverse gear R are engaged simultaneously, then the first clutch C1 is closed. The first primary shaft 2 drives the transfer shaft 44 and then the second primary shaft 4, which drives the second secondary shaft 10 via the intermediate idle gear 70.
Cette disposition particulière nécessite un pignon supplémentaire pour réaliser la marche arrière R, mais ne fixe pas de distance entre les deux arbres secondaires 6, 10 qui ne comportent plus de pignon engrenant directement entre eux.  This particular arrangement requires an additional pinion to perform the reverse gear R, but does not set a distance between the two secondary shafts 6, 10 which no longer have pinion meshing directly between them.
On notera que pour les différentes boîtes de vitesses 1 , 61 71 présentées ci-dessus, pour le démarrage du véhicule en marche arrière, une fermeture du deuxième embrayage C2 à la place du premier embrayage C1 suite à une défaillance par exemple, n'inverse pas le sens de marche de ce véhicule ce qui limite les risques d'accidents.  Note that for the various gearboxes 1, 61 71 presented above, for starting the vehicle in reverse, closing the second clutch C2 in place of the first clutch C1 following a failure for example, does not reverse not the direction of travel of this vehicle which limits the risk of accidents.
La figure 4 présente une boîte de vitesses 81 comportant un unique arbre secondaire 6, et un arbre de transfert 44 disposé parallèlement à cet arbre secondaire, qui est porté directement par le carter de la boîte de vitesses.  Figure 4 shows a gearbox 81 having a single secondary shaft 6, and a transfer shaft 44 disposed parallel to the secondary shaft, which is carried directly by the housing of the gearbox.
Sur le deuxième arbre primaire 4 on trouve successivement en partant du côté avant, un pignon fixe 14 du deuxième rapport de démultiplication II, et un pignon fixe 80 du quatrième IV rapport de démultiplication.  On the second primary shaft 4 is successively starting from the front side, a fixed gear 14 of the second gear ratio II, and a fixed gear 80 of the fourth IV gear ratio.
Sur le premier arbre primaire 2 on trouve successivement en partant du côté avant, un pignon fixe 82 du sixième rapport de démultiplication VI, un pignon fixe 60 de la liaison de transfert T, et un pignon fixe 28 du troisième rapport de démultiplication III.  On the first primary shaft 2 is successively starting from the front side, a fixed gear 82 of the sixth gear ratio VI, a fixed gear 60 of the transfer link T, and a fixed gear 28 of the third gear ratio III.
Sur l'arbre secondaire 6 on trouve successivement en partant du côté avant, des pignons libres 16, 34 du deuxième II et du quatrième IV rapport de démultiplication, avec un manchon double de synchronisation 84 intercalé entre eux, et des pignons libres 20, 30 du sixième VI et du troisième III rapport de démultiplication, avec un manchon double de synchronisation 86 intercalé entre eux.  On the secondary shaft 6 is successively starting from the front side, free gears 16, 34 of the second II and the fourth IV gear ratio, with a double synchronization sleeve 84 interposed between them, and free pinions 20, 30 the sixth VI and the third III gear ratio, with a dual synchronizing sleeve 86 interposed between them.
Sur l'arbre de transfert 44 on trouve successivement en partant du côté avant, un pignon libre 90 du rapport de marche arrière R qui engrène directement avec le pignon libre 16 du deuxième rapport de démultiplication II, porté par l'arbre secondaire 6, et un pignon libre 92 de la liaison de transfert T qui engrène avec le pignon fixe 80 du quatrième rapport de démultiplication IV. On trouve ensuite sur l'arbre de transfert 44 un pignon fixe 40 qui engrène avec le pignon fixe 60 de la liaison de transfert T, disposé sur le premier arbre primaire 2. On the transfer shaft 44 is successively starting from the front side, a free gear 90 of the reverse ratio R which meshes directly with the free pinion 16 of the second gear ratio II, carried by the secondary shaft 6, and a free gear 92 of the transfer link T which meshes with the fixed gear 80 of the fourth gear ratio IV. Then there is on the transfer shaft 44 a fixed gear 40 which meshes with the fixed gear 60 of the transfer link T, arranged on the first primary shaft 2.
Un manchon double de synchronisation 94 intercalé entre les pignons libres 90, 92 de l'arbre de transfert 44, permet de lier l'un ou l'autre de ces pignons libres avec l'arbre de transfert, pour engager le rapport de marche arrière R ou la liaison de transfert T.  A synchronizing double sleeve 94 interposed between the free pinions 90, 92 of the transfer shaft 44 makes it possible to link one or the other of these idle gears with the transfer shaft, to engage the reverse ratio. R or the transfer link T.
Le fonctionnement de la boîte de vitesses 81 est le suivant.  The operation of the gearbox 81 is as follows.
La première vitesse I utilise simultanément la liaison de transfert T et le deuxième rapport de démultiplication II. Pour les deuxième II, troisième III et quatrième IV vitesses, on utilise directement le . rapport de démultiplication correspondant. The first gear I simultaneously uses the transfer link T and the second gear ratio II. For the second II, third III and fourth IV speeds, one directly uses the . corresponding gear ratio.
Pour la cinquième vitesse V, on engage simultanément le troisième rapport de démultiplication III et la liaison de transfert T. En fermant le deuxième embrayage C2 du deuxième arbre primaire 4, on augmente la vitesse du premier arbre primaire 2 par la liaison de transfert T.  For the fifth speed V, the third gear ratio III is simultaneously engaged with the transfer link T. By closing the second clutch C2 of the second primary shaft 4, the speed of the first primary shaft 2 is increased by the transfer link T.
On obtient un écart entre la troisième III et la cinquième V vitesse égale au rapport donné par la liaison de transfert T, qui convient bien, la valeur de la quatrième vitesse IV pouvant être librement ajustée entre ces troisième et cinquième vitesses. La valeur dé la sixième vitesse VI peut être aussi librement ajustée.  A difference is obtained between the third III and the fifth V speed equal to the ratio given by the transfer link T, which is well suited, the value of the fourth speed IV can be freely adjusted between these third and fifth speeds. The value of the sixth speed VI can be adjusted as freely.
On obtient ainsi une gamme de six vitesses comprenant un bon étagement des rapports, avec une interruption du couple moteur entre les quatrième IV et cinquième V vitesses, et entre les cinquième V et sixième VI vitesses. Par contre on peut réaliser des passages directs maintenant un couple moteur, entre les troisième III et cinquième V vitesses, et entre les quatrième IV et sixième VI vitesses, ce qui est intéressant en particulier pour effectuer des descentes directes de deux vitesses tout en maintenant un couple moteur, et obtenir rapidement une forte accélération du véhicule.  This gives a range of six speeds including a good gear ratio, with an interruption of the engine torque between the fourth IV and fifth V speeds, and between the fifth V and sixth VI speeds. On the other hand, it is possible to carry out direct passages maintaining a driving torque between the third and fifth speeds, and between the fourth and fourth speeds, which is particularly advantageous for direct descents of two speeds while maintaining engine torque, and quickly get a strong acceleration of the vehicle.
Par ailleurs la sixième VI et dernière vitesse, qui réalise généralement la majorité des kilomètres, met en œuvre un seul engrènement pour entraîner l'arbre secondaire 6, ce qui limite les pertes et procure à cette vitesse un bon rendement. Pour la marche arrière, le rapport de marche arrière R et le deuxième rapport de démultiplication II sont engagés simultanément, puis lé premier embrayage C1 est fermé. On réalise ainsi à partir du premier arbre primaire 2 un entraînement de l'arbre de transfert 44, puis un entraînement direct de l'arbre secondaire 6 par le pignon libre 90 de rapport de marche arrière R engrenant avec le pignon libre 16 du deuxième rapport de démultiplication II. Furthermore the sixth VI and last speed, which generally achieves the majority of kilometers, implements a single meshing to drive the secondary shaft 6, which limits losses and provides a good performance at this speed. For the reverse, the reverse ratio R and the second gear ratio II are engaged simultaneously, then the first clutch C1 is closed. This is done from the first primary shaft 2 a drive of the transfer shaft 44, then a direct drive of the secondary shaft 6 by the free gear 90 of reverse ratio R meshing with the free gear 16 of the second report of reduction II.
Cette boîte de vitesses 81 comporte seulement 3 manchons 84, 86, 94 réalisant chacun une double synchronisation, commandés par trois fourchettes, ce qui permet de réduire le nombre d'actionneurs pour effectuer ces commandes, ainsi que l'encombrement et la masse de cette boîte de vitesses.  This gearbox 81 comprises only three sleeves 84, 86, 94 each performing a double synchronization, controlled by three forks, which reduces the number of actuators to perform these commands, as well as the size and mass of this gearbox.
La figure 5 présente une boîte de vitesses 101 comportant les différences suivantes, par rapport à la boîte de vitesses 81 présentée figure 4.  FIG. 5 shows a gearbox 101 having the following differences with respect to the gearbox 81 shown in FIG. 4.
Le pignon fixe 40 de l'arbre de transfert 44, engrène avec le pignon fixe 28 du troisième rapport de démultiplication III, porté par le premier arbre primaire 2. On économise ainsi un pignon. Par contre le rapport de la liaison de transfert T, ne peut pas être fixé indépendamment du troisième III et du quatrième IV rapport de démultiplication.  The fixed gear 40 of the transfer shaft 44, meshes with the fixed gear 28 of the third gear ratio III, carried by the first primary shaft 2. This saves a pinion. On the other hand, the ratio of the transfer link T can not be set independently of the third III and the fourth IV gear ratio.
La figure 6 présente une boîte de vitesses 111 comportant les différences suivantes, par rapport à la boîte de vitesses 81 présentée figure 4.  FIG. 6 shows a gearbox 111 having the following differences with respect to the gearbox 81 shown in FIG. 4.
Un pignon intermédiaire 70 monté libre sur un arbre 72, engrène d'une part avec le pignon libre 90 du rapport de marche arrière R, et d'autre part avec le pignon fixe 14 du deuxième rapport de démultiplication II.  An intermediate gear 70 mounted free on a shaft 72, meshes with the free gear 90 of the reverse ratio R, and secondly with the fixed gear 14 of the second gear ratio II.
Pour un démarrage du véhicule en marche arrière, la liaison de transfert T et le rapport de marche arrière R sont engagés simultanément, puis le premier embrayage C1 est fermé. Le premier arbre primaire 2 entraîne l'arbre de transfert 44, qui entraîne l'arbre secondaire 6 par l'intermédiaire du pignon libre intermédiaire 70, puis du deuxième arbre secondaire 4.  For a starting of the vehicle in reverse, the transfer link T and the reverse ratio R are engaged simultaneously, then the first clutch C1 is closed. The first primary shaft 2 drives the transfer shaft 44, which drives the secondary shaft 6 via the intermediate idle gear 70, then the second secondary shaft 4.
La figure 7 présente une boîte de vitesses 121 comportant la différence suivante par rapport à la boîte de vitesses 81 présentée figure 4, le sixième rapport de démultiplication VI est supprimé, les pignons 82, 20 de ce rapport ainsi que le synchroniseur du pignon libre étant retirés.  FIG. 7 shows a gearbox 121 comprising the following difference with respect to the gearbox 81 shown in FIG. 4, the sixth gear ratio VI is eliminated, the gearwheels 82, 20 of this ratio and the synchronizer of the free gear being removed.
On obtient ainsi une boîte de vitesses 121 comprenant trois rapports de démultiplication, pouvant réaliser cinq vitésses, la cinquième vitesse V étant obtenue par le transfert T utilisé en série avec le troisième rapport de démultiplication III, l'embrayage C2 étant fermé. This gives a gearbox 121 comprising three gear ratios, which can achieve five times, the fifth gear V being obtained by the transfer T used in series with the third gear ratio III, the clutch C2 being closed.
La figure 8 présente une boîte de vitesses 131 comportant la différence suivante par rapport à la boîte de vitesses 121 présentée figure 7, un pignon intermédiaire 70 monté libre sur un arbre 72, engrène d'une part avec le pignon libre 90 du rapport de marche arrière R, et d'autre part avec le pignon fixe 14 du deuxième rapport de démultiplication II.  FIG. 8 shows a gearbox 131 having the following difference with respect to the gearbox 121 shown in FIG. 7, an intermediate gear 70 mounted freely on a shaft 72 meshes with the free gear 90 of the gear ratio. rear R, and secondly with the fixed gear 14 of the second gear ratio II.
La figure 9 présente une boîte de vitesses 141 comportant la différence suivante par rapport à la boîte de vitesses 131 présentée figure 8. Les pignons 28, 30 du troisième rapport de démultiplication III, sont disposés du côté avant par rapport au manchon de synchronisation 86, et aux pignons fixes 40, 60 de la liaison de transfert T.  FIG. 9 shows a gearbox 141 having the following difference with respect to the gearbox 131 shown in FIG. 8. The gears 28, 30 of the third gear ratio III are arranged on the front side with respect to the synchronization sleeve 86, and fixed gears 40, 60 of the transfer link T.
On notera que pour les différentes boîtes de vitesses 81 , 101 , 111 , 121 , 131 et 141 présentées par les figures 4 à 9, pour le démarrage du véhicule en marche arrière, une fermeture du deuxième embrayage C2 à la place du premier embrayage C1 inverse le sens de marche de ce véhicule.  Note that for the various gearboxes 81, 101, 111, 121, 131 and 141 shown in Figures 4 to 9, for starting the vehicle in reverse, closing the second clutch C2 in place of the first clutch C1 reverses the direction of travel of this vehicle.

Claims

REVENDICATIONS
1 - Boîte de vitesses comportant un premier (2) et un deuxième (4) arbre primaire disposés suivant un axe commun et relies chacun par un embrayage (C1 , C2) à un moteur, et au moins un arbre secondaire (6, 10) entraînant les roues motrices du véhicule, chaque arbre primaire (2, 4) pouvant être relié aux arbres secondaires (6, 10) par des rapports de démultiplication comprenant chacun un pignon menant porté par un arbre primaire, qui engrène avec un pignon mené porté par un arbre secondaire, un deuxième rapport de démultiplication (II) réalisant à partir du deuxième arbre primaire (4) la deuxième vitesse (II) en entraînant le premier arbre secondaire (6), cette boîte de vitesses comportant de plus une liaison de transfert (T) pouvant relier les deux arbres primaires (2, 4) entre eux en passant par un arbre de transfert (44) disposé parallèlement à ces arbres primaires, en réduisant la vitesse du deuxième arbre primaire (4) par rapport à celle du premier arbre primaire (2), caractérisée en ce qu'un pignon (16, 90) d'un rapport de marche arrière (R) disposé sur le deuxième arbre secondaire (10) ou sur l'arbre de transfert (44), engrène directement avec le pignon mené (16) du deuxième rapport de démultiplication (II) pour réaliser la marche arrière. 1 - Gearbox comprising a first (2) and a second (4) primary shaft arranged along a common axis and each connected by a clutch (C1, C2) to a motor, and at least one secondary shaft (6, 10) driving the driving wheels of the vehicle, each primary shaft (2, 4) being connectable to the secondary shafts (6, 10) by reduction ratios each comprising a driving pinion carried by a primary shaft, which meshes with a driven pinion carried by a secondary shaft, a second gear ratio (II) producing from the second primary shaft (4) the second gear (II) driving the first secondary shaft (6), this gearbox further comprising a transfer link ( T) being able to connect the two primary shafts (2, 4) to each other via a transfer shaft (44) arranged parallel to these primary shafts, reducing the speed of the second primary shaft (4) relative to that of the first shaftprimary (2), characterized in that a pinion (16, 90) of a reverse ratio (R) disposed on the second secondary shaft (10) or on the transfer shaft (44) meshes directly with the driven gear (16) of the second gear ratio (II) for reversing.
2 - Boîte de vitesses suivant la revendication 1 , caractérisée en ce qu'elle comporte deux arbres secondaires (6, 10), l'arbre de transfert (44) comprenant un creux longitudinal, étant traversé et supporté par le premier arbre secondaire (6).  2 - gearbox according to claim 1, characterized in that it comprises two secondary shafts (6, 10), the transfer shaft (44) comprising a longitudinal recess, being traversed and supported by the first secondary shaft (6 ).
3 - Boîte de vitesses suivant la revendication 2, caractérisée en ce qu'un manchon de synchronisation double (38) commande d'un côté le rapport de marche arrière (R), et de l'autre un des rapports de démultiplication (IV).  3 - Gearbox according to claim 2, characterized in that a double synchronization sleeve (38) controls the reverse gear ratio (R) on one side, and the other one of the gear ratios (IV) on the other .
4 - Boîte de vitesses suivant la revendication 2 ou 3, caractérisée en ce qu'un manchon de synchronisation double (22) commande d'un côté le deuxième rapport de démultiplication (II), et de l'autre un sixième rapport de démultiplication (VI).  4 - Gearbox according to claim 2 or 3, characterized in that a double synchronization sleeve (22) controls on one side the second gear ratio (II), and on the other a sixth gear ratio ( VI).
5 - Boîte de vitesses suivant l'une quelconque des revendications 2 à 4, caractérisée en ce que la distance transversale entre le premier arbre secondaire (6) et les arbres primaires (2, 4), et inférieure à celle entre le deuxième arbre secondaire (10) et ces arbres primaires, cette boîte comportant au moins un pignon fixe (18) porté par un arbre primaire (4) qui est commun pour deux rapports de démultiplication. 5 - Gearbox according to any one of claims 2 to 4, characterized in that the transverse distance between the first secondary shaft (6) and the primary shafts (2, 4), and less than that between the second secondary shaft (10) and these primary trees, this box comprising at least one fixed gear (18) carried by a primary shaft (4) which is common for two gear ratios.
6 - Boîte de vitesses suivant l'une quelconque des revendications précédentes, caractérisée en ce qu'elle comporte un pignon menant (28) du troisième rapport de démultiplication (III), lié au premier arbre primaire (2), qui engrène avec un pignon d'entraînement (40) de l'arbre de transfert (44).  6 - Gearbox according to any one of the preceding claims, characterized in that it comprises a drive gear (28) of the third gear ratio (III), connected to the first primary shaft (2), which meshes with a pinion drive (40) of the transfer shaft (44).
7 - Boîte de vitesses suivant l'une des revendications 2 à 5, et la revendication 6, caractérisée en ce l'arbre de transfert (44) entraîne le deuxième arbre primaire (4), par les pignons menant (18) et mené (20) d'un sixième rapport de démultiplication (VI).  Gearbox according to one of Claims 2 to 5, and Claim 6, characterized in that the transfer shaft (44) drives the second primary shaft (4) by the drive pinions (18) and drives ( 20) of a sixth gear ratio (VI).
8 - Boîte de vitesses suivant la revendication 1 , caractérisée en ce qu'elle comporte un seul arbre secondaire (6), supportant un manchon de synchronisation double (94) qui commande d'un côté la liaison de transfert (T), et de l'autre le rapport de marche arrière (R).  8 - Gearbox according to claim 1, characterized in that it comprises a single secondary shaft (6), supporting a dual synchronization sleeve (94) which controls on one side the transfer link (T), and the other is the reverse gear (R).
9 - Procédé de fonctionnement d'une boîte de vitesses suivant l'une quelconque des revendications précédentes, caractérisé en ce qu'une cinquième vitesse (V) est réalisée en engageant simultanément un troisième rapport de démultiplication (III) lié au premier arbre primaire (2), et la liaison de transfert (T), et en fermant le deuxième embrayage (C2) entraînant le deuxième arbre primaire (4).  9 - A method of operation of a gearbox according to any one of the preceding claims, characterized in that a fifth speed (V) is achieved by simultaneously engaging a third gear ratio (III) linked to the first primary shaft ( 2), and the transfer link (T), and closing the second clutch (C2) driving the second primary shaft (4).
10 - Boîte de vitesses utilisant un procédé de fonctionnement suivant la revendication 9, caractérisée en ce qu'elle comporte un dernier rapport de démultiplication lié au premier arbre primaire (2), qui réalise la sixième vitesse (VI).  10 - gearbox using a method of operation according to claim 9, characterized in that it comprises a last gear ratio linked to the first primary shaft (2), which carries the sixth gear (VI).
PCT/FR2011/000313 2010-05-26 2011-05-25 Dual clutch transmission comprising a transfer link and a reverse gear WO2011148065A1 (en)

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US34830710P 2010-05-26 2010-05-26
US34832110P 2010-05-26 2010-05-26
US34831410P 2010-05-26 2010-05-26
US61/348,314 2010-05-26
US61/348,307 2010-05-26
US61/348,321 2010-05-26

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CN103775569A (en) * 2014-01-23 2014-05-07 长城汽车股份有限公司 Double-clutch transmission and power assembly
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DE10015336A1 (en) * 2000-03-28 2001-10-04 Volkswagen Ag Dual clutch gearbox has elements arranged so that for certain engaged gear drive train consists of first drive shaft, parallel shaft, second input shaft and output shaft
JP2003120764A (en) * 2001-10-15 2003-04-23 Toyota Motor Corp Twin clutch transmission
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Publication number Priority date Publication date Assignee Title
CN103671749A (en) * 2012-09-26 2014-03-26 重庆长安汽车股份有限公司 Dual-clutch automatic transmission device
CN103671748A (en) * 2012-09-26 2014-03-26 重庆长安汽车股份有限公司 Transmission device of dual-clutch transmission
CN103671746A (en) * 2012-09-26 2014-03-26 重庆长安汽车股份有限公司 Dual-clutch transmission
CN103711877A (en) * 2012-10-09 2014-04-09 重庆长安汽车股份有限公司 Double-clutch automatic gearbox transmission device
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FR3010165A1 (en) * 2013-08-29 2015-03-06 Peugeot Citroen Automobiles Sa DOUBLE CLUTCH GEARBOX FOR A MOTOR VEHICLE
FR3010164A1 (en) * 2013-08-29 2015-03-06 Peugeot Citroen Automobiles Sa DOUBLE CLUTCH GEARBOX FOR A MOTOR VEHICLE
CN103775569A (en) * 2014-01-23 2014-05-07 长城汽车股份有限公司 Double-clutch transmission and power assembly
WO2021170456A1 (en) * 2020-02-27 2021-09-02 Renault S.A.S Dual clutch gearbox with short ratios obtained by combination
FR3107742A1 (en) * 2020-02-27 2021-09-03 Renault Sas DUAL CLUTCH GEARBOX WITH SHORT SPEED OBTAINED BY COMBINATION

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