EP3227582A1 - Speed transmission device for moving a motor vehicle, notably a motorized at least two-wheeled vehicle, and power train using such a device particularly for a hybrid vehicle - Google Patents

Speed transmission device for moving a motor vehicle, notably a motorized at least two-wheeled vehicle, and power train using such a device particularly for a hybrid vehicle

Info

Publication number
EP3227582A1
EP3227582A1 EP15805136.7A EP15805136A EP3227582A1 EP 3227582 A1 EP3227582 A1 EP 3227582A1 EP 15805136 A EP15805136 A EP 15805136A EP 3227582 A1 EP3227582 A1 EP 3227582A1
Authority
EP
European Patent Office
Prior art keywords
shaft
wheel
transmission device
vehicle
clutch
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP15805136.7A
Other languages
German (de)
French (fr)
Inventor
Stephane Venturi
Samy LAABIDI
Misa MILOSAVLJEVIC
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IFP Energies Nouvelles IFPEN
Original Assignee
IFP Energies Nouvelles IFPEN
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 IFP Energies Nouvelles IFPEN filed Critical IFP Energies Nouvelles IFPEN
Publication of EP3227582A1 publication Critical patent/EP3227582A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—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
    • F16H3/091—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 including a single 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
    • 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
    • F16H3/10—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 with one or more one-way clutches as an essential feature
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds

Definitions

  • Speed transmission device for moving a motor vehicle, in particular a motorized vehicle with at least two wheels, and powertrain using such a device, in particular for a hybrid vehicle.
  • the present invention relates to a speed transmission device for moving a motor vehicle, in particular a motorized vehicle with at least two wheels, as well as a powertrain using this speed transmission device, particularly for a hybrid vehicle.
  • this speed transmission device comprises a motor shaft placed substantially parallel to a receiving shaft which is generally used to drive the driving wheel or wheels of the vehicle.
  • the motor shaft is rotated by the heat engine and carries, in a fixed manner, two gears which are each engaged with receiving gears borne by the receiving shaft while being mounted idle on this tree.
  • This receiving shaft also carries walk-around drives which make it possible to rotate the receiving gears with this shaft.
  • the vehicle in displacement at different speeds by acting on the various players that carry the receiving shaft to secure one of the toothed wheels of the motor shaft with a receiving gear of the receiving shaft.
  • this type of transmission can be used with a hybrid type vehicle that combines, as means of moving the vehicle, the internal combustion engine to a driving machine / generator rotary, like an electric machine connected to an electrical source, such as one or more electric accumulators.
  • This combination optimizes the performance of this vehicle, in particular by reducing the fuel consumption of the entire device, while preserving the environment by limited releases of pollutants into the atmosphere.
  • the engine is used to move this vehicle for uses where high driving power and a long operating autonomy are required.
  • This transmission device although satisfactory, nevertheless has disadvantages. Indeed, it is necessary, to obtain the desired speed of movement, to couple or uncouple some elements of the device, such as the gears receiving. This has the effect of lengthening the time of passage from one speed to another resulting in driving discomfort.
  • the transmission device must include a multiplicity of actuators to control the players. These actuators increase the cost of producing the device and can be the source of faults and / or malfunctions.
  • these actuators must be controlled by a computing unit, as the calculator that usually includes the engine, which requires increasing the capacity of this computer.
  • the present invention proposes to overcome the drawbacks mentioned above by means of a speed transmission device of simple and inexpensive embodiment.
  • the invention relates to a transmission device for motor vehicles, especially motor vehicles with at least two wheels, comprising a motor shaft carrying at least two driving gears, a receiving shaft carrying at least two driven gears and a intermediate motion transmission shaft carrying intermediate gear wheels cooperating with the gear wheels of the motor shaft and the output shaft, characterized in that at least one of the intermediate gear wheels is mounted idle on the intermediate shaft and in that the device comprises a coupling for the connection between the intermediate shaft and the intermediate idler gear.
  • the coupling may include a centrifugal clutch.
  • the coupling may include a disk clutch.
  • the coupling may include a synchronizer.
  • the coupling may include a clutch.
  • the invention also relates to a powertrain, in particular for a motor vehicle, comprising an internal combustion engine, a speed transmission device and a powertrain, characterized in that it comprises a speed transmission device as defined above. above.
  • the powertrain may include a prime mover / generator to achieve at least the displacement of the vehicle.
  • the rotor of the machine can be connected to the clutch plate.
  • the powertrain may comprise a band closed on itself for the connection in rotation between the rotor of the machine and the element that it drives.
  • the power unit according to one of the claims may comprise a band closed on itself for the connection in rotation between the driving gears, the intermediate gears and the driven gears
  • FIG. 1 which is a diagram showing a powertrain comprising the speed transmission device according to the invention.
  • the speed transmission device 10 comprises a drive shaft 12 connected to the crankshaft 14 of an internal combustion engine 16, thus forming a powertrain.
  • This motor shaft carries two toothed wheels 18 and 20, here of different diameters, a coupling 22 for the wheel 18 and a controlled-control coupling 24 for the wheel 20.
  • the coupling 22 for the wheel 18, illustrated by way of example in the figure, is a unidirectional coupling, such as a freewheel, but this coupling can also be a controlled-control coupling.
  • the toothed wheel 18 (called small gear wheel) is placed on the motor shaft 12 by interposing the free wheel 22. To the right of this small gear is placed the other gear wheel 20 (or large gear wheel) on a sheath 26 surrounding the shaft 12 being free to rotate on the shaft but fixed in translation.
  • the controlled-control coupling 24 is here a friction disk clutch which comprises a reaction plate 28 fixed on the shaft 12, a pressure plate 30, free in translation but fixed in rotation with the reaction plate, being controlled moving towards the reaction plate by any known means, such as levers 32, and a friction disc 34 free in translation on the sleeve 26 but fixed in rotation thereon being placed between the pressure plate and the plate of reaction.
  • this controlled control coupling 24 can also take the form of a synchronizer or dog clutch.
  • This transmission device also comprises an intermediate shaft for transmitting rotational movement 36, placed substantially parallel to the drive shaft 12 and which carries two toothed wheels 38, 40 of different diameter, one of whose wheels is fixed on it. shaft, here the small toothed wheel 40. These gears are connected to the toothed wheels of the motor shaft.
  • the gearwheel 38 (large intermediate gear) is connected to the small drive gear and the gearwheel 40 (small intermediate gear) is connected to the large gearwheel.
  • This device also comprises, substantially parallel to the drive shaft 12 and the intermediate shaft 36, a receiving shaft 42 which carries, as for the drive shaft 12, two gears receiving 44 and 46, here also of diameter different.
  • the receiver gears are placed on the receiving shaft in a manner symmetrical to that of the motor shaft.
  • the toothed wheel 44 (small driven gear wheel) is placed on a sleeve 48 surrounding the receiving shaft 42 being free to rotate on this shaft but fixed in translation.
  • This toothed wheel 44 has the possibility of being rotatably connected to this receiving shaft by a controlled-control coupling 50, such as a friction disc clutch or a synchronizer or dog clutch.
  • the controlled-control coupling 50 is here a friction clutch with a reaction plate 52 fixed on the receiving shaft, a pressure plate 54, free in translation but fixed in rotation with the reaction plate, being controlled in displacement towards the reaction plate by any known means, such as levers 56, and a friction disc 58 free in translation on the sleeve 48 but fixed in rotation.
  • the toothed wheel 46 (large driven gear) is placed on the shaft 42 through a unidirectional coupling 60, such as a freewheel.
  • the unidirectional coupling 60 may also be a controlled-controlled coupling, such as a disk clutch or synchronizer or clutch.
  • the small driven wheel 44 is in connection with the large intermediate wheel 38 while the large driven wheel 46 is in connection with the small intermediate wheel 40.
  • the toothed wheel 38 of the rotary motion transmission intermediate shaft 36 is mounted idly on this shaft by being carried by a sleeve 62 which surrounds in a fixed manner in translation but free in rotation the shaft 36.
  • the shaft 36 is connected to the sleeve 62 by a coupling 64, which is, in the example of FIG. 1, a centrifugal clutch 66.
  • This centrifugal coupling comprises a plate 68 fixedly supported by the intermediate shaft 36, a web 70 fixedly connected to the sleeve 62 and bearing friction weights 72 subjected to the centrifugal force and returned to the rest position by spring means 74. Therefore, under the rotation of the large intermediate gear wheel 38, the veil 70 is rotated. Under the impulse of this rotation of the web, the flyweights 72 move radially and come into contact with the plate 68 thus establishing a rotational connection between the intermediate shaft 36 and the toothed wheel 38.
  • the device described above thus makes it possible to achieve four speed ratios by using two disk clutches 24 and 50, two freewheels 22 and 60 and a centrifugal clutch 66.
  • the small driving gear 18 is rotated by the actuation of the free wheel 22 connecting the motor shaft and the wheel.
  • This rotation of the wheel 18 is then transmitted to the large intermediate gear wheel 38.
  • the rotation of this wheel causes the activation of the centrifugal clutch 66, which has the effect of establishing a connection between this wheel and the intermediate shaft 36.
  • the rotation of this shaft rotates the small intermediate gear wheel 40.
  • This small wheel in turn drives the large driven wheel 46 which retransmits this rotation to the receiving shaft 42 through the action of the freewheel 60.
  • the clutch 24 of the motor shaft is in the engaged position and the clutch 50 of the receiving shaft is in the disengaged position.
  • the large driving wheel 20 is then rotated by the motor shaft 12 by the action of the clutch 24.
  • This rotation is transmitted to the intermediate shaft 36 by the small intermediate wheel 40 which communicates to the ferris wheel conducted 46.
  • the rotation of this large wheel is transmitted to the receiving shaft 42 by the actuation of the freewheel 60.
  • the rotation of the shaft 12 causes rotation of the small driving wheel 18 through the freewheel 22.
  • This rotation is transmitted to the large intermediate wheel 38 which, through the rotation of the sheath 62, makes active the centrifugal clutch 66 ensuring the connection between the shaft 36 and the large intermediate wheel.
  • the clutch 66 is active, the small driving wheel 18 has a higher speed than that of the shaft 12.
  • the free wheel 22 is then rendered inactive and the driving wheel 18 rotates crazy around the shaft 12.
  • the small driven wheel 44 idly turns on the shaft 42 and the receiver shaft 42 is rotated only by the wheel 46.
  • the clutch 50 of the drive shaft 42 is in the engaged position and the clutch 24 of the motor shaft 12 is in the disengaged position.
  • the small driving wheel 18 is then rotated by the motor shaft 12 through the free wheel 22.
  • the rotation of this small driving wheel is communicated to the intermediate shaft 36 by the large intermediate wheel 38 and the setting action of the centrifugal clutch 66.
  • This rotation of the wheel 38 causes the rotation of the driven wheel 44 which transmits it to the receiving shaft 42 under the action of the clutch 50.
  • the rotation of the shaft 36 causes the rotation of the small intermediate wheel 40 which then drives the large driven wheel 46.
  • the latter is uncoupled from the large wheel driven by the inaction of the freewheel 60.
  • the rotation of the small intermediate wheel 40 rotates the large driving wheel 20 which rotates wild around the shaft 12 .
  • the rotation of the motor shaft 12 is transmitted, by the action of the free wheel 22, to the small driving wheel 18 which transmits it to the large intermediate gear wheel 38.
  • the rotation of this large intermediate gear wheel 38 allows to couple this wheel to the shaft 36 by the action of the clutch 66.
  • the rotation of the wheel 38 is then transmitted to the drive wheel 44 and the receiving shaft 42 through the clutch 50.
  • the motor shaft 12 is uncoupled from the small driving wheel 18 by the freewheel 22 and the receiving shaft 42 is uncoupled from the large driven wheel 46 by the freewheel 60 in consideration of the differential rotation speed between the driven wheel and the receiving shaft.
  • the transmission device as described above makes it possible to achieve four gear ratios with the advantage of having a centrifugal clutch on the intermediate shaft which works at higher speeds and at lower torques while providing a gain in compactness, inertia, mass and price. This also reduces the wear of the parts of the transmission and have a better performance of all.
  • the wheels 18, 38, and 44 as well as the wheels 20, 40 and 46 are interconnected by a band closed on itself, such as a chain or a belt, preferably notched internally and / or externally. .
  • this chain (or this belt) can limit friction with the wheels.
  • toothed wheels meshing directly with each other.
  • the variant of Figure 2 differs from the embodiment of Figure 1 in that the centrifugal clutch of Figure 1 is replaced by a controlled control coupling 80, such as a synchronizer or clutch or a clutch.
  • a controlled control coupling 80 such as a synchronizer or clutch or a clutch.
  • this coupling is a disc clutch 82 between the sleeve 62 and the intermediate shaft 36.
  • this clutch 82 comprises a reaction plate 84 fixed on the intermediate shaft 36, a pressure plate 86, free in translation but fixed in rotation with the reaction plate, being controlled in displacement towards the reaction plate by levers 88, and a friction disc 90 free in translation and fixed in rotation on the sleeve 62 being placed between the reaction plate and the pressure plate.
  • the disk clutch 82 will be active or inactive depending on this ratio. Specifically, for the report with a configuration where the two clutches 24 and 50 are in the disengaged position, the clutch 82 is engaged position.
  • the clutch 24 of the motor shaft 12 is in the engaged position
  • the clutch 50 of the receiving shaft 42 is in the disengaged position
  • the clutch 82 can be in the disengaged or engaged position.
  • it is preferable to leave it in the disengaged position since in this case the speed of rotation of the gears 18, 38 and 44 is imposed by the rotation of the driving wheel 18 through the freewheel 22. If the clutch 82 is kept engaged, the speed of rotation of the gears 18, 38 and 44 is higher because it is imposed by the intermediate wheel 38.
  • the clutch 50 of the output shaft 42 is in the engaged position, the clutch 24 of the motor shaft 12 is in the disengaged position and the clutch 82 can be in the disengaged or engaged position.
  • FIGS. 1 and 2 also show the application of the speed transmission device 10 to a power unit of a motor vehicle, such as a motorized vehicle, in particular a vehicle with at least two wheels and with use on a motor vehicle. hybrid type vehicle with the combination of a driving machine / generator 92 to the internal combustion engine 16.
  • a motor vehicle such as a motorized vehicle, in particular a vehicle with at least two wheels and with use on a motor vehicle.
  • hybrid type vehicle with the combination of a driving machine / generator 92 to the internal combustion engine 16.
  • This machine is, solely by way of example in the following description, a hydraulic or pneumatic machine or an electric machine powered by batteries (not shown) which is used, either as an electric motor for moving the vehicle or as a generator to charge the batteries or power the vehicle's electrical accessories.
  • the electric machine comprises a rotor 94 carrying a toothed wheel 96.
  • This machine can be connected in different places to the transmission device.
  • the rotor 92 is rotatably connected to the reaction plate 52 of the clutch 50 (FIGS. 1 and 2); for the configuration B, this rotor is connected to the intermediate shaft 36 through the plate 68 of the centrifugal clutch 66 (FIG. 2); for the configuration B '(FIG. 2), the rotor is connected to the reaction plate 84 of the clutch 82 carried by the intermediate shaft 36.
  • this machine will be chosen by the skilled person in a judicious manner, including taking into account the size and desired gear ratios for the purely electric drive of the vehicle.
  • the machine drives the vehicle with a gear ratio and for configuration B and B 'with two gear ratios.
  • the connection of the machine with the trays 52, 68, 82 can be performed by a chain or a toothed belt.
  • connection can also be achieved by cooperation of the toothed wheel 96 of the rotor with a complementary toothing (not shown) carried by the periphery of the plates.
  • This electric motor can also be used in conjunction with the internal combustion engine 16 to either bring additional power to the output shaft, or be used as a generator to recharge the batteries.
  • the rotor of the machine is rotated by the different gears and in this case the machine becomes a generator.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Arrangement Of Transmissions (AREA)
  • Electric Propulsion And Braking For Vehicles (AREA)
  • Hybrid Electric Vehicles (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The present invention relates to a speed transmission device for motor vehicles, notably for motorized at least two-wheeled vehicles, comprising a drive shaft (12) bearing at least two driving gear wheels (18, 20), a receiving shaft (42) bearing at least two driven gear wheels (44, 46) and an intermediate movement transmission shaft (36) bearing intermediate gear wheels (38, 40) collaborating with the gear wheels of the drive shaft (12) and of the receiving shaft (42). According to the invention, at least one (38) of the intermediate gear wheels is mounted to turn freely on the intermediate shaft (36) and the device comprises a coupling (64) for making the connection between the intermediate shaft (36) and the freely mounted intermediate gear wheel (38).

Description

Dispositif de transmission de vitesse pour le déplacement d'un véhicule automobile, notamment d'un véhicule motorisé à au moins deux roues, et groupe motopropulseur utilisant un tel dispositif en particulier pour un véhicule hybride.  Speed transmission device for moving a motor vehicle, in particular a motorized vehicle with at least two wheels, and powertrain using such a device, in particular for a hybrid vehicle.
La présente invention se rapporte à un dispositif de transmission de vitesse pour le déplacement d'un véhicule automobile, notamment d'un véhicule motorisé à au moins deux roues, ainsi qu'à un groupe motopropulseur utilisant ce dispositif de transmission de vitesse en particulier pour un véhicule hybride. The present invention relates to a speed transmission device for moving a motor vehicle, in particular a motorized vehicle with at least two wheels, as well as a powertrain using this speed transmission device, particularly for a hybrid vehicle.
Dans l'exemple décrit dans le document FR 2 81 1 395, ce dispositif de transmission de vitesse comprend un arbre-moteur placé sensiblement parallèlement à un arbre récepteur qui est généralement utilisé pour entraîner la ou les roues motrices du véhicule. In the example described in document FR 2 81 1 395, this speed transmission device comprises a motor shaft placed substantially parallel to a receiving shaft which is generally used to drive the driving wheel or wheels of the vehicle.
Dans ce type de transmission, l'arbre-moteur est entraîné en rotation par le moteur thermique et porte, de manière fixe, deux roues dentées qui sont chacune en prise avec des roues dentées réceptrices portées par l'arbre récepteur en étant montées folles sur cet arbre. Cet arbre récepteur porte également des baladeurs à débattement alternatif qui permettent de rendre solidaires en rotation les roues dentées réceptrices avec cet arbre. In this type of transmission, the motor shaft is rotated by the heat engine and carries, in a fixed manner, two gears which are each engaged with receiving gears borne by the receiving shaft while being mounted idle on this tree. This receiving shaft also carries walk-around drives which make it possible to rotate the receiving gears with this shaft.
Ainsi en fonctionnement, le véhicule est entraîné en déplacement à différentes vitesses en agissant sur les différents baladeurs que portent l'arbre récepteur pour solidariser une des roues dentées de l'arbre-moteur avec une des roues dentées réceptrices de cet arbre récepteur. Thus, in operation, the vehicle is driven in displacement at different speeds by acting on the various players that carry the receiving shaft to secure one of the toothed wheels of the motor shaft with a receiving gear of the receiving shaft.
Comme cela est bien connu, ce type de transmission peut être utilisé avec un véhicule de type hybride qui combine, comme moyen de déplacement du véhicule, le moteur à combustion interne à une machine motrice/génératrice rotative, comme une machine électrique reliée à une source électrique, telle qu'un ou plusieurs accumulateurs électriques. As is well known, this type of transmission can be used with a hybrid type vehicle that combines, as means of moving the vehicle, the internal combustion engine to a driving machine / generator rotary, like an electric machine connected to an electrical source, such as one or more electric accumulators.
Cette combinaison permet d'optimiser les performances de ce véhicule, notamment en diminuant la consommation en carburant de l'ensemble du dispositif, tout en préservant l'environnement par des rejets limités de polluants dans l'atmosphère. This combination optimizes the performance of this vehicle, in particular by reducing the fuel consumption of the entire device, while preserving the environment by limited releases of pollutants into the atmosphere.
Ainsi, lorsque l'on souhaite déplacer le véhicule avec un couple important sur une grande plage de vitesses tout en limitant la génération de gaz polluants et de bruit, comme dans un site urbain, l'utilisation de la machine électrique est privilégiée pour entraîner en déplacement ce véhicule.  Thus, when it is desired to move the vehicle with a large torque over a wide range of speeds while limiting the generation of pollutant gases and noise, as in an urban site, the use of the electric machine is preferred to lead in moving this vehicle.
Par contre, le moteur thermique est utilisé pour déplacer ce véhicule lors d'utilisations où une puissance d'entraînement élevée et une grande autonomie de fonctionnement sont demandées. On the other hand, the engine is used to move this vehicle for uses where high driving power and a long operating autonomy are required.
Ce dispositif de transmission bien que donnant satisfaction présente néanmoins des inconvénients. En effet, il est nécessaire, pour obtenir la vitesse de déplacement souhaitée, d'accoupler ou de désaccoupler certains éléments du dispositif, comme les roues dentées réceptrices. Ceci a pour effet d'allonger le temps de passage d'une vitesse à une autre en entraînant un inconfort de conduite. De plus, le dispositif de transmission doit comporter une multiplicité d'actionneurs pour commander les baladeurs. Ces actionneurs augmentent le coût de réalisation du dispositif et peuvent être la source de pannes et/ou de dysfonctionnements. En outre, ces actionneurs doivent être contrôlés par une unité de calcul, comme le calculateur que comporte habituellement le moteur, ce qui nécessite d'augmenter la capacité de ce calculateur. La présente invention se propose de remédier aux inconvénients mentionnés ci-dessus grâce à un dispositif de transmission de vitesse de réalisation simple et peu coûteuse. This transmission device, although satisfactory, nevertheless has disadvantages. Indeed, it is necessary, to obtain the desired speed of movement, to couple or uncouple some elements of the device, such as the gears receiving. This has the effect of lengthening the time of passage from one speed to another resulting in driving discomfort. In addition, the transmission device must include a multiplicity of actuators to control the players. These actuators increase the cost of producing the device and can be the source of faults and / or malfunctions. In addition, these actuators must be controlled by a computing unit, as the calculator that usually includes the engine, which requires increasing the capacity of this computer. The present invention proposes to overcome the drawbacks mentioned above by means of a speed transmission device of simple and inexpensive embodiment.
A cet effet, l'invention concerne un dispositif de transmission pour véhicules automobiles, notamment véhicules motorisés à au moins deux roues, comprenant un arbre-moteur portant au moins deux roues dentées menantes, un arbre récepteur portant au moins deux roues dentées menées et un arbre intermédiaire de transmission de mouvement portant des roues dentées intermédiaires coopérant avec les roues dentées de l'arbre-moteur et de l'arbre récepteur, caractérisé en ce que au moins l'une des roues dentées intermédiaires est montée folle sur l'arbre intermédiaire et en ce que le dispositif comprend un accouplement pour la liaison entre l'arbre intermédiaire et la roue dentée intermédiaire montée folle. To this end, the invention relates to a transmission device for motor vehicles, especially motor vehicles with at least two wheels, comprising a motor shaft carrying at least two driving gears, a receiving shaft carrying at least two driven gears and a intermediate motion transmission shaft carrying intermediate gear wheels cooperating with the gear wheels of the motor shaft and the output shaft, characterized in that at least one of the intermediate gear wheels is mounted idle on the intermediate shaft and in that the device comprises a coupling for the connection between the intermediate shaft and the intermediate idler gear.
L'accouplement peut comprendre un embrayage centrifuge. L'accouplement peut comprendre un embrayage à disque. The coupling may include a centrifugal clutch. The coupling may include a disk clutch.
L'accouplement peut comprendre un synchroniseur. The coupling may include a synchronizer.
L'accouplement peut comprendre un crabot. L'invention concerne également un groupe motopropulseur, notamment pour véhicule automobile, comprenant un moteur à combustion interne, un dispositif de transmission de vitesse et une voie motrice, caractérisé en ce qu'il comprend un dispositif de transmission de vitesse telle que défini ci-dessus. Le groupe motopropulseur peut comprendre une machine motrice/génératrice pour réaliser au moins le déplacement du véhicule. Le rotor de la machine peut être est relié au plateau de l'embrayage. The coupling may include a clutch. The invention also relates to a powertrain, in particular for a motor vehicle, comprising an internal combustion engine, a speed transmission device and a powertrain, characterized in that it comprises a speed transmission device as defined above. above. The powertrain may include a prime mover / generator to achieve at least the displacement of the vehicle. The rotor of the machine can be connected to the clutch plate.
Le groupe motopropulseur peut comprendre une bande fermée sur elle- même pour la liaison en rotation entre le rotor de la machine et l'élément qu'il entraîne. The powertrain may comprise a band closed on itself for the connection in rotation between the rotor of the machine and the element that it drives.
Le groupe motopropulseur selon l'une des revendications peut comprendre une bande fermée sur elle-même pour la liaison en rotation entre les roues dentées menantes, les roues dentées intermédiaires et les roues dentées menées The power unit according to one of the claims may comprise a band closed on itself for the connection in rotation between the driving gears, the intermediate gears and the driven gears
Les autres caractéristiques et avantages de l'invention vont apparaître maintenant à la lecture de la description qui va suivre, donnée à titre uniquement illustratif et non limitatif, et à laquelle sont annexées : The other features and advantages of the invention will now appear on reading the following description, given solely by way of illustration and not limitation, and to which are appended:
- la figure 1 qui est un schéma montrant un groupe motopropulseur comprenant le dispositif de transmission de vitesse selon l'invention, et  FIG. 1 which is a diagram showing a powertrain comprising the speed transmission device according to the invention, and
- la figure 2 qui montre une variante du groupe motopropulseur de la figure - Figure 2 shows a variant of the powertrain of the figure
1 . Comme illustré sur la figure 1 , le dispositif de transmission de vitesse 10 comprend un arbre-moteur 12 relié au vilebrequin 14 d'un moteur à combustion interne 16 en formant ainsi un groupe motopropulseur. Cet arbre-moteur porte deux roues dentées 18 et 20, ici de diamètres différents, un accouplement 22 pour la roue 18 et un accouplement à commande contrôlée 24 pour la roue 20. 1. As illustrated in FIG. 1, the speed transmission device 10 comprises a drive shaft 12 connected to the crankshaft 14 of an internal combustion engine 16, thus forming a powertrain. This motor shaft carries two toothed wheels 18 and 20, here of different diameters, a coupling 22 for the wheel 18 and a controlled-control coupling 24 for the wheel 20.
L'accouplement 22 pour la roue 18, illustré à titre d'exemple sur la figure, est un accouplement unidirectionnel, comme une roue libre, mais cet accouplement peut être également un accouplement à commande contrôlée. La roue dentée 18 (dénommée petite roue dentée) est placée sur l'arbre- moteur 12 en y interposant la roue libre 22. A droite de cette petite roue dentée est placée l'autre roue dentée 20 (ou grande roue dentée) sur un fourreau 26 entourant l'arbre 12 en étant libre en rotation sur cet arbre mais fixe en translation. L'accouplement à commande contrôlée 24 est ici un embrayage à disque de friction qui comprend un plateau de réaction 28 fixe sur l'arbre 12, un plateau de pression 30, libre en translation mais fixe en rotation avec le plateau de réaction, en étant commandé en déplacement vers le plateau de réaction par tous moyens connus, comme des leviers 32, et un disque de friction 34 libre en translation sur le fourreau 26 mais fixe en rotation sur celui-ci en étant placé entre le plateau de pression et le plateau de réaction. The coupling 22 for the wheel 18, illustrated by way of example in the figure, is a unidirectional coupling, such as a freewheel, but this coupling can also be a controlled-control coupling. The toothed wheel 18 (called small gear wheel) is placed on the motor shaft 12 by interposing the free wheel 22. To the right of this small gear is placed the other gear wheel 20 (or large gear wheel) on a sheath 26 surrounding the shaft 12 being free to rotate on the shaft but fixed in translation. The controlled-control coupling 24 is here a friction disk clutch which comprises a reaction plate 28 fixed on the shaft 12, a pressure plate 30, free in translation but fixed in rotation with the reaction plate, being controlled moving towards the reaction plate by any known means, such as levers 32, and a friction disc 34 free in translation on the sleeve 26 but fixed in rotation thereon being placed between the pressure plate and the plate of reaction.
A titre d'autre exemple, cet accouplement à commande contrôlée 24 peut aussi prendre la forme d'un synchroniseur ou d'un crabot.  As another example, this controlled control coupling 24 can also take the form of a synchronizer or dog clutch.
Pour des raisons de simplification dans la suite de la description, les roues dentées 18 et 20 sont dénommées roues dentées menantes. Ce dispositif de transmission comprend également un arbre intermédiaire de transmission de mouvement de rotation 36, placé sensiblement parallèlement à l'arbre-moteur 12 et qui porte deux roues dentées 38, 40 ici de diamètre différent dont l'une des roues est fixe sur cet arbre, ici la petite roue dentée 40. Ces roues dentées sont reliées aux roues dentées de l'arbre- moteur. La roue dentée 38 (grande roue dentée intermédiaire) est reliée à la petite roue dentée menante et la roue dentée 40 (petite roue dentée intermédiaire) est reliée à la grande roue dentée menante. For reasons of simplification in the rest of the description, the gears 18 and 20 are called driving gears. This transmission device also comprises an intermediate shaft for transmitting rotational movement 36, placed substantially parallel to the drive shaft 12 and which carries two toothed wheels 38, 40 of different diameter, one of whose wheels is fixed on it. shaft, here the small toothed wheel 40. These gears are connected to the toothed wheels of the motor shaft. The gearwheel 38 (large intermediate gear) is connected to the small drive gear and the gearwheel 40 (small intermediate gear) is connected to the large gearwheel.
Ce dispositif comprend aussi, sensiblement parallèlement à l'arbre-moteur 12 et à l'arbre intermédiaire 36, un arbre récepteur 42 qui porte, comme pour l'arbre-moteur 12, deux roues dentées réceptrices 44 et 46, ici également de diamètre différent. This device also comprises, substantially parallel to the drive shaft 12 and the intermediate shaft 36, a receiving shaft 42 which carries, as for the drive shaft 12, two gears receiving 44 and 46, here also of diameter different.
Les roues dentées réceptrices sont placées sur l'arbre récepteur d'une façon symétrique à celle de l'arbre-moteur. Ainsi, la roue dentée 44 (petite roue dentée menée) est placée sur un fourreau 48 entourant l'arbre récepteur 42 en étant libre en rotation sur cet arbre mais fixe en translation. Cette roue dentée 44 a la possibilité d'être reliée en rotation à cet arbre récepteur par un accouplement à commande contrôlée 50, comme un embrayage à disque de friction ou un synchroniseur ou un crabot. The receiver gears are placed on the receiving shaft in a manner symmetrical to that of the motor shaft. Thus, the toothed wheel 44 (small driven gear wheel) is placed on a sleeve 48 surrounding the receiving shaft 42 being free to rotate on this shaft but fixed in translation. This toothed wheel 44 has the possibility of being rotatably connected to this receiving shaft by a controlled-control coupling 50, such as a friction disc clutch or a synchronizer or dog clutch.
Comme pour l'accouplement 24 placé sur l'arbre-moteur, l'accouplement à commande contrôlée 50 est ici un embrayage à friction avec un plateau de réaction 52 fixe sur l'arbre récepteur, un plateau de pression 54, libre en translation mais fixe en rotation avec le plateau de réaction, en étant commandé en déplacement vers le plateau de réaction par tous moyens connus, comme des leviers 56, et un disque de friction 58 libre en translation sur le fourreau 48 mais fixe en rotation. Comme mieux illustré sur la figure 1 , la roue dentée 46 (grande roue dentée menée) est placée sur l'arbre 42 au travers d'un accouplement unidirectionnel 60, comme une roue libre.  As for the coupling 24 placed on the motor shaft, the controlled-control coupling 50 is here a friction clutch with a reaction plate 52 fixed on the receiving shaft, a pressure plate 54, free in translation but fixed in rotation with the reaction plate, being controlled in displacement towards the reaction plate by any known means, such as levers 56, and a friction disc 58 free in translation on the sleeve 48 but fixed in rotation. As best illustrated in FIG. 1, the toothed wheel 46 (large driven gear) is placed on the shaft 42 through a unidirectional coupling 60, such as a freewheel.
Comme pour T'accouplement 22 de la roue 18, l'accouplement unidirectionnel 60 peut être également un accouplement à commande contrôlée, comme un embrayage à disque ou un synchroniseur ou un crabot.  As for the coupling 22 of the wheel 18, the unidirectional coupling 60 may also be a controlled-controlled coupling, such as a disk clutch or synchronizer or clutch.
Ainsi, la petite roue menée 44 est en liaison avec la grande roue intermédiaire 38 alors que la grande roue menée 46 est en liaison avec la petite roue intermédiaire 40. Thus, the small driven wheel 44 is in connection with the large intermediate wheel 38 while the large driven wheel 46 is in connection with the small intermediate wheel 40.
Comme mieux visible sur cette figure, la roue dentée 38 de l'arbre intermédiaire de transmission de mouvement de rotation 36 est montée folle sur cet arbre en étant portée par un fourreau 62 qui entoure de manière fixe en translation mais libre en rotation l'arbre 36. As best seen in this figure, the toothed wheel 38 of the rotary motion transmission intermediate shaft 36 is mounted idly on this shaft by being carried by a sleeve 62 which surrounds in a fixed manner in translation but free in rotation the shaft 36.
L'arbre 36 est relié au fourreau 62 par un accouplement 64, qui est, dans l'exemple de la figure 1 , un embrayage centrifuge 66. Cet accouplement centrifuge comprend un plateau 68 porté fixement par l'arbre intermédiaire 36, un voile 70 relié fixement au fourreau 62 et portant des masselottes de friction 72 soumises à la force centrifuge et rappelées en position de repos par des moyens à ressort 74. De ce fait, sous la rotation de la grande roue dentée intermédiaire 38, le voile 70 est mis en rotation. Sous l'impulsion de cette rotation du voile, les masselottes 72 se déplacent radialement et viennent au contact du plateau 68 en établissant ainsi une liaison à rotation entre l'arbre intermédiaire 36 et la roue dentée 38. The shaft 36 is connected to the sleeve 62 by a coupling 64, which is, in the example of FIG. 1, a centrifugal clutch 66. This centrifugal coupling comprises a plate 68 fixedly supported by the intermediate shaft 36, a web 70 fixedly connected to the sleeve 62 and bearing friction weights 72 subjected to the centrifugal force and returned to the rest position by spring means 74. Therefore, under the rotation of the large intermediate gear wheel 38, the veil 70 is rotated. Under the impulse of this rotation of the web, the flyweights 72 move radially and come into contact with the plate 68 thus establishing a rotational connection between the intermediate shaft 36 and the toothed wheel 38.
Bien entendu, il est à la portée de l'homme du métier de prévoir des moyens connus, comme des actionneurs hydrauliques ou pneumatiques ou électriques ou mécaniques, pour actionner les leviers 32, 56 des embrayages en fonction du rapport de vitesse souhaité. Of course, it is within the abilities of those skilled in the art to provide known means, such as hydraulic or pneumatic or electric or mechanical actuators for actuating the levers 32, 56 of the clutches according to the desired speed ratio.
Le dispositif décrit ci-dessus permet ainsi de réaliser quatre rapports de vitesse en utilisant deux embrayages à disque 24 et 50, deux roues libres 22 et 60 et un embrayage centrifuge 66. Dans un de ces rapports de vitesse, lors de la rotation de l'arbre-moteur et dans la position débrayée des deux embrayages 24 et 50, la petite roue dentée menante 18 est entraînée en rotation par la mise en action de la roue libre 22 reliant l'arbre-moteur et cette roue. Cette rotation de la roue 18 est ensuite transmise à la grande roue dentée intermédiaire 38. La rotation de cette roue entraîne la mise en action de l'embrayage centrifuge 66, ce qui a pour effet d'établir une liaison entre cette roue et l'arbre intermédiaire 36. La rotation de cet arbre entraîne en rotation la petite roue dentée intermédiaire 40. Cette petite roue entraîne à son tour la grande roue menée 46 qui retransmet cette rotation à l'arbre récepteur 42 grâce à l'action de la roue libre 60. The device described above thus makes it possible to achieve four speed ratios by using two disk clutches 24 and 50, two freewheels 22 and 60 and a centrifugal clutch 66. In one of these speed ratios, during the rotation of the clutch. and in the disengaged position of the two clutches 24 and 50, the small driving gear 18 is rotated by the actuation of the free wheel 22 connecting the motor shaft and the wheel. This rotation of the wheel 18 is then transmitted to the large intermediate gear wheel 38. The rotation of this wheel causes the activation of the centrifugal clutch 66, which has the effect of establishing a connection between this wheel and the intermediate shaft 36. The rotation of this shaft rotates the small intermediate gear wheel 40. This small wheel in turn drives the large driven wheel 46 which retransmits this rotation to the receiving shaft 42 through the action of the freewheel 60.
Bien entendu comme les deux embrayages 24 et 50 sont inactifs, ni la grande roue menante 20, ni la petite roue menée 44 ne sont entraînées en rotation par l'arbre-moteur ou l'arbre récepteur et tournent ainsi de manière folle sur les arbres 12 et 42. Of course, as the two clutches 24 and 50 are inactive, neither the driving wheel 20 nor the small driven wheel 44 are driven in. rotation by the motor shaft or the shaft and thus turn wildly on the shafts 12 and 42.
Dans un autre rapport de vitesse, l'embrayage 24 de l'arbre-moteur est en position embrayée et l'embrayage 50 de l'arbre récepteur est en position débrayée. La grande roue menante 20 est alors entraînée en rotation par l'arbre-moteur 12 par l'action de l'embrayage 24. Cette rotation est retransmise à l'arbre intermédiaire 36 par la petite roue intermédiaire 40 qui la communique à la grande roue menée 46. La rotation de cette grande roue est transmise à l'arbre récepteur 42 par la mise en action de la roue libre 60. In another gear ratio, the clutch 24 of the motor shaft is in the engaged position and the clutch 50 of the receiving shaft is in the disengaged position. The large driving wheel 20 is then rotated by the motor shaft 12 by the action of the clutch 24. This rotation is transmitted to the intermediate shaft 36 by the small intermediate wheel 40 which communicates to the ferris wheel conducted 46. The rotation of this large wheel is transmitted to the receiving shaft 42 by the actuation of the freewheel 60.
Bien entendu, la rotation de l'arbre 12 entraîne la rotation de la petite roue menante 18 au travers de la roue libre 22. Cette rotation est retransmise à la grande roue intermédiaire 38 qui, par l'intermédiaire de la rotation du fourreau 62, rend actif l'embrayage centrifuge 66 en assurant la liaison entre l'arbre 36 et la grande roue intermédiaire. Lorsque l'embrayage 66 est actif, la petite roue menante 18 a un régime supérieur à celui de l'arbre 12. La roue libre 22 est alors rendue inactive et la roue menante 18 tourne folle autour de l'arbre 12. Cependant, compte tenu de la position inactive de l'embrayage 50, la petite roue menée 44 tourne de manière folle sur l'arbre 42 et l'arbre récepteur 42 est entraîné en rotation que par la roue 46.  Of course, the rotation of the shaft 12 causes rotation of the small driving wheel 18 through the freewheel 22. This rotation is transmitted to the large intermediate wheel 38 which, through the rotation of the sheath 62, makes active the centrifugal clutch 66 ensuring the connection between the shaft 36 and the large intermediate wheel. When the clutch 66 is active, the small driving wheel 18 has a higher speed than that of the shaft 12. The free wheel 22 is then rendered inactive and the driving wheel 18 rotates crazy around the shaft 12. However, given the inactive position of the clutch 50, the small driven wheel 44 idly turns on the shaft 42 and the receiver shaft 42 is rotated only by the wheel 46.
Pour un autre rapport de vitesse, l'embrayage 50 de l'arbre récepteur 42 est en position embrayée et l'embrayage 24 de l'arbre-moteur 12 est en position débrayée. La petite roue menante 18 est alors entraînée en rotation par l'arbre- moteur 12 au travers de la roue libre 22. La rotation de cette petite roue menante est communiquée à l'arbre intermédiaire 36 par la grande roue intermédiaire 38 et la mise en action de l'embrayage centrifuge 66. Cette rotation de la roue 38 entraîne la rotation de la roue menée 44 qui la transmet à l'arbre récepteur 42 sous l'action de l'embrayage 50. For another speed ratio, the clutch 50 of the drive shaft 42 is in the engaged position and the clutch 24 of the motor shaft 12 is in the disengaged position. The small driving wheel 18 is then rotated by the motor shaft 12 through the free wheel 22. The rotation of this small driving wheel is communicated to the intermediate shaft 36 by the large intermediate wheel 38 and the setting action of the centrifugal clutch 66. This rotation of the wheel 38 causes the rotation of the driven wheel 44 which transmits it to the receiving shaft 42 under the action of the clutch 50.
Bien entendu, la rotation de l'arbre 36 entraîne la rotation de la petite roue intermédiaire 40 qui entraîne alors la grande roue menée 46. Cependant, compte tenu du différentiel de vitesses de rotation entre la roue menée 46 et l'arbre récepteur 42, ce dernier est désaccouplé de la grande roue menée par l'inaction de la roue libre 60. La rotation de la petite roue intermédiaire 40 entraine en rotation la grande roue menante 20 qui tourne folle autour de l'arbre 12. Of course, the rotation of the shaft 36 causes the rotation of the small intermediate wheel 40 which then drives the large driven wheel 46. However, given the difference in rotational speeds between the driven wheel 46 and the receiving shaft 42, the latter is uncoupled from the large wheel driven by the inaction of the freewheel 60. The rotation of the small intermediate wheel 40 rotates the large driving wheel 20 which rotates wild around the shaft 12 .
Enfin pour le dernier rapport, les deux embrayages 24 et 50 sont en position embrayée. La rotation de l'arbre-moteur 12 est transmise, par l'action de l'embrayage 24, à la grande roue menante 20 qui la transmet à la petite roue dentée intermédiaire 40 de l'arbre intermédiaire 36. Cette rotation est ensuite transmise à la grande roue menée 46.  Finally for the last report, the two clutches 24 and 50 are in the engaged position. The rotation of the motor shaft 12 is transmitted, by the action of the clutch 24, to the large driving wheel 20 which transmits it to the small intermediate gear 40 of the intermediate shaft 36. This rotation is then transmitted to the Ferris wheel 46.
Simultanément, la rotation de l'arbre-moteur 12 est transmise, par l'action de la roue libre 22, à la petite roue menante 18 qui la transmet à la grande roue dentée intermédiaire 38. La rotation de cette grande roue dentée intermédiaire 38 permet d'accoupler cette roue à l'arbre 36 par l'action de l'embrayage 66. La rotation de la roue 38 est ensuite transmise à la roue menante 44 puis à l'arbre récepteur 42 au travers de l'embrayage 50.  Simultaneously, the rotation of the motor shaft 12 is transmitted, by the action of the free wheel 22, to the small driving wheel 18 which transmits it to the large intermediate gear wheel 38. The rotation of this large intermediate gear wheel 38 allows to couple this wheel to the shaft 36 by the action of the clutch 66. The rotation of the wheel 38 is then transmitted to the drive wheel 44 and the receiving shaft 42 through the clutch 50.
Dans cette configuration, compte tenu du différentiel de vitesses de rotation entre l'arbre-moteur 12 et la petite roue menante 18, et entre l'arbre récepteur 42 et la grande roue menante 46, l'arbre-moteur 12 est désaccouplé de la petite roue menante 18 par la roue libre 22 et l'arbre récepteur 42 est désaccouplé de la grande roue menée 46 par la roue libre 60 en considération du différentiel de vitesses de rotation entre la roue menée et l'arbre récepteur. In this configuration, taking into account the differential speed of rotation between the motor shaft 12 and the small driving wheel 18, and between the receiving shaft 42 and the large driving wheel 46, the motor shaft 12 is uncoupled from the small driving wheel 18 by the freewheel 22 and the receiving shaft 42 is uncoupled from the large driven wheel 46 by the freewheel 60 in consideration of the differential rotation speed between the driven wheel and the receiving shaft.
Ainsi, le dispositif de transmission tel que décrit ci-dessus permet de réaliser quatre rapports de vitesse avec l'avantage de disposer d'un embrayage centrifuge sur l'arbre intermédiaire qui travaille à des régimes plus élevés et à des couples moins importants tout en procurant un gain en compacité, en inertie, en masse et en prix. Ceci permet également de réduire l'usure des pièces de la transmission et d'avoir un meilleur rendement de l'ensemble. Sur la figure 1 , les roues 18, 38, et 44 ainsi que les roues 20, 40 et 46 sont reliées entre elles par une bande fermée sur elle-même, comme une chaîne ou une courroie, de préférence crantée intérieurement et/ou extérieurement. Thus, the transmission device as described above makes it possible to achieve four gear ratios with the advantage of having a centrifugal clutch on the intermediate shaft which works at higher speeds and at lower torques while providing a gain in compactness, inertia, mass and price. This also reduces the wear of the parts of the transmission and have a better performance of all. In FIG. 1, the wheels 18, 38, and 44 as well as the wheels 20, 40 and 46 are interconnected by a band closed on itself, such as a chain or a belt, preferably notched internally and / or externally. .
Comme mieux visible sur cette figure, il est prévu une chaîne 76 pour relier la petite roue menante 18, la grande roue dentée intermédiaire 38, et la petite roue menée 44 ainsi qu'une chaîne 78 pour relier la grande roue dentée menante 20, la petite roue dentée intermédiaire 40 et la grande roue dentée menée 46. Cela a pour effet de pouvoir modifier l'emplacement des arbres et de les placer à distance les uns des autres selon l'encombrement disponible tout en assurant la transmission du mouvement de rotation entre ces arbres.  As best seen in this figure, there is provided a chain 76 for connecting the small driving wheel 18, the large intermediate gear wheel 38, and the small driven wheel 44 and a chain 78 for connecting the large driving gear wheel 20, the small intermediate gear wheel 40 and large gearwheel 46. This has the effect of changing the location of the trees and place them at a distance from each other depending on the available space while ensuring the transmission of the rotational movement between these trees.
De plus, cette chaîne (ou cette courroie) permet de limiter les frottements avec les roues. In addition, this chain (or this belt) can limit friction with the wheels.
L'utilisation de chaîne ou de courroie peut permettre également d'éviter des solutions de lubrification en carter humide.  The use of a chain or belt may also prevent wet sump lubrication solutions.
Bien entendu et cela sans sortir du cadre de l'invention, il peut être prévue que les roues dentées engrènent directement les unes avec les autres. Of course and without departing from the scope of the invention, it may be provided that the toothed wheels meshing directly with each other.
La variante de la figure 2 se distingue de l'exemple de réalisation de la figure 1 par le fait que l'embrayage centrifuge de la figure 1 est remplacé par un accouplement à commande contrôlée 80, comme un synchroniseur ou un crabot ou un embrayage. The variant of Figure 2 differs from the embodiment of Figure 1 in that the centrifugal clutch of Figure 1 is replaced by a controlled control coupling 80, such as a synchronizer or clutch or a clutch.
Dans l'exemple de la figure 2, cet accouplement est un embrayage à disque 82 entre le fourreau 62 et l'arbre intermédiaire 36.  In the example of FIG. 2, this coupling is a disc clutch 82 between the sleeve 62 and the intermediate shaft 36.
Comme pour les embrayages 24 et 50, cet embrayage 82 comprend un plateau de réaction 84 fixe sur l'arbre intermédiaire 36, un plateau de pression 86, libre en translation mais fixe en rotation avec le plateau de réaction, en étant commandé en déplacement vers le plateau de réaction par des leviers 88, et un disque de friction 90 libre en translation et fixe en rotation sur le fourreau 62 en étant placé entre le plateau de réaction et le plateau de pression. As for the clutches 24 and 50, this clutch 82 comprises a reaction plate 84 fixed on the intermediate shaft 36, a pressure plate 86, free in translation but fixed in rotation with the reaction plate, being controlled in displacement towards the reaction plate by levers 88, and a friction disc 90 free in translation and fixed in rotation on the sleeve 62 being placed between the reaction plate and the pressure plate.
Le fonctionnement de cette variante est semblable à celui de la figure 1 en offrant la possibilité d'obtenir quatre rapports de vitesse. The operation of this variant is similar to that of Figure 1 by providing the possibility of obtaining four gear ratios.
Pour le rapport choisi, l'embrayage à disque 82 sera actif ou inactif en fonction de ce rapport. Plus précisément, pour le rapport avec une configuration où les deux embrayages 24 et 50 sont dans la position débrayée, l'embrayage 82 est position embrayée. For the selected gear, the disk clutch 82 will be active or inactive depending on this ratio. Specifically, for the report with a configuration where the two clutches 24 and 50 are in the disengaged position, the clutch 82 is engaged position.
Dans un autre rapport de vitesse, l'embrayage 24 de l'arbre-moteur 12 est en position embrayée, l'embrayage 50 de l'arbre récepteur 42 est en position débrayée et l'embrayage 82 peut être en position débrayée ou embrayée. Il est cependant préférable de le laisser en position débrayée, puisque dans ce cas la vitesse de rotation des roues dentées 18, 38 et 44 est imposée par la rotation de la roue menante 18 au travers de la roue libre 22. Si l'embrayage 82 est maintenu embrayé, la vitesse de rotation des roues dentées 18, 38 et 44 est plus élevée car elle est imposée par la roue intermédiaire 38. In another gear ratio, the clutch 24 of the motor shaft 12 is in the engaged position, the clutch 50 of the receiving shaft 42 is in the disengaged position and the clutch 82 can be in the disengaged or engaged position. However, it is preferable to leave it in the disengaged position, since in this case the speed of rotation of the gears 18, 38 and 44 is imposed by the rotation of the driving wheel 18 through the freewheel 22. If the clutch 82 is kept engaged, the speed of rotation of the gears 18, 38 and 44 is higher because it is imposed by the intermediate wheel 38.
Pour un autre rapport de vitesse, l'embrayage 50 de l'arbre récepteur 42 est en position embrayée, l'embrayage 24 de l'arbre-moteur 12 est en position débrayée et l'embrayage 82 peut être en position débrayée ou embrayée. De même, il est préférable de le laisser en position débrayée, puisque dans ce cas les roues dentées 20, 40 et 46 ne sont pas entraînées en rotation. Si l'embrayage 82 est maintenu embrayé, les roues dentées 20, 40 et 46 sont entraînées en rotation. For another gear ratio, the clutch 50 of the output shaft 42 is in the engaged position, the clutch 24 of the motor shaft 12 is in the disengaged position and the clutch 82 can be in the disengaged or engaged position. Similarly, it is preferable to leave it in the disengaged position, since in this case the gears 20, 40 and 46 are not rotated. If the clutch 82 is kept engaged, the gears 20, 40 and 46 are rotated.
Enfin pour le dernier rapport, tous les embrayages 24, 50 et 82 sont en position embrayée. Les exemples illustrés sur les figures 1 et 2 montrent également l'application du dispositif de transmission de vitesse 10 à un groupe motopropulseur de véhicule automobile, tel qu'un véhicule motorisé, notamment un véhicule à au moins deux roues et avec une utilisation sur un véhicule de type hybride avec l'association d'une machine motrice/génératrice 92 au moteur à combustion interne 16. Finally for the last report, all the clutches 24, 50 and 82 are in the engaged position. The examples illustrated in FIGS. 1 and 2 also show the application of the speed transmission device 10 to a power unit of a motor vehicle, such as a motorized vehicle, in particular a vehicle with at least two wheels and with use on a motor vehicle. hybrid type vehicle with the combination of a driving machine / generator 92 to the internal combustion engine 16.
Cette machine est, uniquement à titre d'exemple dans la suite de la description, une machine hydraulique ou pneumatique ou une machine électrique alimentée par des batteries (non représentées) qui est utilisée, soit en tant que moteur électrique pour le déplacement du véhicule soit en tant que génératrice pour charger les batteries ou alimenter les accessoires électriques du véhicule. This machine is, solely by way of example in the following description, a hydraulic or pneumatic machine or an electric machine powered by batteries (not shown) which is used, either as an electric motor for moving the vehicle or as a generator to charge the batteries or power the vehicle's electrical accessories.
Comme mieux visible sur les figures, la machine électrique comporte un rotor 94 portant une roue dentée 96. As best seen in the figures, the electric machine comprises a rotor 94 carrying a toothed wheel 96.
Cette machine peut être reliée en différents endroits au dispositif de transmission. This machine can be connected in different places to the transmission device.
Ainsi, dans la configuration A mentionnée sur les figures 1 et 2, le rotor 92 est lié en rotation avec le plateau de réaction 52 de l'embrayage 50 (figures 1 et 2) ; pour la configuration B, ce rotor est relié à l'arbre intermédiaire 36 au travers du plateau 68 de l'embrayage centrifuge 66 (figure 2) ; pour la configuration B' (figure 2), le rotor est relié au plateau de réaction 84 de l'embrayage 82 porté par l'arbre intermédiaire 36. Thus, in the configuration A mentioned in FIGS. 1 and 2, the rotor 92 is rotatably connected to the reaction plate 52 of the clutch 50 (FIGS. 1 and 2); for the configuration B, this rotor is connected to the intermediate shaft 36 through the plate 68 of the centrifugal clutch 66 (FIG. 2); for the configuration B '(FIG. 2), the rotor is connected to the reaction plate 84 of the clutch 82 carried by the intermediate shaft 36.
La localisation de cette machine sera choisie par l'homme du métier de manière judicieuse, notamment en tenant compte de l'encombrement et des rapports de vitesse souhaités pour l'entraînement purement électrique du véhicule. Dans la configuration A, la machine entraîne le véhicule avec un rapport de vitesse et pour la configuration B et B' avec deux rapports de vitesse. A titre d'exemple, la liaison de la machine avec les plateaux 52, 68, 82 peut être réalisée par une chaîne ou une courroie crantée. The location of this machine will be chosen by the skilled person in a judicious manner, including taking into account the size and desired gear ratios for the purely electric drive of the vehicle. In configuration A, the machine drives the vehicle with a gear ratio and for configuration B and B 'with two gear ratios. For example, the connection of the machine with the trays 52, 68, 82 can be performed by a chain or a toothed belt.
Cette liaison peut également être réalisée par coopération de la roue dentée 96 du rotor avec une denture complémentaire (non représentée) portée par la périphérie des plateaux.  This connection can also be achieved by cooperation of the toothed wheel 96 of the rotor with a complementary toothing (not shown) carried by the periphery of the plates.
Par cela, il est possible de réaliser l'entraînement du véhicule en marche avant ou en marche arrière grâce à la rotation du rotor 92 qui est transmise au plateau et via les différentes roues dentées à la voie motrice relié à l'arbre récepteur 42. By this, it is possible to carry out the drive of the vehicle in forward or reverse by rotating the rotor 92 which is transmitted to the plate and via the different gears to the driveway connected to the shaft 42.
En fonctionnement purement électrique pour le déplacement du véhicule, seul le moteur électrique est utilisé.  In purely electric operation for the movement of the vehicle, only the electric motor is used.
Ce moteur électrique peut être également utilisé en association avec le moteur à combustion interne 16 soit pour amener un complément de puissance sur l'arbre récepteur, soit être utilisé en tant que génératrice pour recharger les batteries. This electric motor can also be used in conjunction with the internal combustion engine 16 to either bring additional power to the output shaft, or be used as a generator to recharge the batteries.
De plus, lors des décélérations du véhicule, le rotor de la machine est entraîné en rotation par les différentes roues dentées et dans ce cas la machine devient une génératrice. In addition, during decelerations of the vehicle, the rotor of the machine is rotated by the different gears and in this case the machine becomes a generator.

Claims

REVENDICATIONS
1 ) Dispositif de transmission de vitesse pour véhicules automobiles, notamment véhicule motorisé à au moins deux roues, comprenant un arbre- moteur (12) portant au moins deux roues dentées menantes (18, 20), un arbre récepteur (42) portant au moins deux roues dentées menées (44, 46) et un arbre intermédiaire de transmission de mouvement (36) portant des roues dentées intermédiaires (38, 40) coopérant avec les roues dentées de l'arbre- moteur (12) et de l'arbre récepteur (42), caractérisé en ce que au moins l'une (38) des roues dentées intermédiaires est montée folle sur l'arbre intermédiaire (36) et en ce que le dispositif comprend un accouplement (64) pour la liaison entre l'arbre intermédiaire (36) et la roue dentée intermédiaire montée folle (38). 1) Speed transmission device for motor vehicles, in particular a motorized vehicle with at least two wheels, comprising a motor shaft (12) carrying at least two driving gears (18, 20), a receiving shaft (42) carrying at least two two driven gears (44, 46) and an intermediate motion transmission shaft (36) carrying intermediate gears (38, 40) cooperating with the gears of the motor shaft (12) and the receiving shaft (42), characterized in that at least one (38) of the intermediate gear wheels is mounted idle on the intermediate shaft (36) and in that the device comprises a coupling (64) for connection between the shaft intermediate (36) and idler intermediate gear (38).
2) Dispositif de transmission de vitesse selon la revendication 1 , caractérisé en ce que l'accouplement comprend un embrayage centrifuge (66). 2) A speed transmission device according to claim 1, characterized in that the coupling comprises a centrifugal clutch (66).
3) Dispositif de transmission de vitesse selon la revendication 1 , caractérisé en ce que l'accouplement comprend un embrayage à disque (82). 4) Dispositif de transmission de vitesse selon la revendication 1 , caractérisé en ce que l'accouplement comprend un synchroniseur. 3) A speed transmission device according to claim 1, characterized in that the coupling comprises a disk clutch (82). 4) Speed transmission device according to claim 1, characterized in that the coupling comprises a synchronizer.
5) Dispositif de transmission de vitesse selon la revendication 1 , caractérisé en ce que l'accouplement comprend un crabot. 5) A speed transmission device according to claim 1, characterized in that the coupling comprises a dog clutch.
6) Groupe motopropulseur, notamment pour véhicule automobile, comprenant un moteur à combustion interne (1 6), un dispositif de transmission de vitesse (10) et une voie motrice, caractérisé en ce qu'il comprend un dispositif de transmission de vitesse (10) selon l'une des revendications précédentes. 7) Groupe motopropulseur selon la revendication 6, caractérisé en ce qu'il comprend une machine motrice/génératrice (92) pour réaliser au moins le déplacement du véhicule. 8) Groupe motopropulseur selon la revendication 7, caractérisé en ce que le rotor (94) de la machine (92) est relié au plateau (52, 68, 84) de l'embrayage (50, 66, 82). (6) Power train, in particular for a motor vehicle, comprising an internal combustion engine (1 6), a speed transmission device (10) and a driving track, characterized in that it comprises a speed transmission device (10). ) according to one of the preceding claims. 7) Powertrain according to claim 6, characterized in that it comprises a driving machine / generator (92) to achieve at least the displacement of the vehicle. 8) Powertrain according to claim 7, characterized in that the rotor (94) of the machine (92) is connected to the plate (52, 68, 84) of the clutch (50, 66, 82).
9) Groupe motopropulseur selon l'une des revendications 6 à 8, caractérisé en ce qu'il comprend une bande fermée sur elle-même pour la liaison en rotation entre le rotor (94) de la machine (92) et l'élément qu'il entraîne. 9) power train according to one of claims 6 to 8, characterized in that it comprises a band closed on itself for the connection in rotation between the rotor (94) of the machine (92) and the element qu 'it causes.
10) Groupe motopropulseur selon l'une des revendications 6 à 9, caractérisé en ce qu'il comprend une bande fermée sur elle-même (76, 76) pour la liaison en rotation entre les roues dentées menantes, les roues dentés intermédiaires et les roues dentées menées. 10) power train according to one of claims 6 to 9, characterized in that it comprises a closed band on itself (76, 76) for the rotational connection between the driving gears, the intermediate gears and the driven gears.
EP15805136.7A 2014-12-03 2015-12-01 Speed transmission device for moving a motor vehicle, notably a motorized at least two-wheeled vehicle, and power train using such a device particularly for a hybrid vehicle Withdrawn EP3227582A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1461843A FR3029584B1 (en) 2014-12-03 2014-12-03 SPEED TRANSMISSION DEVICE FOR THE DISPLACEMENT OF A MOTOR VEHICLE, IN PARTICULAR A MOTORIZED VEHICLE WITH AT LEAST TWO WHEELS, AND MOTOR POWER PACKAGE USING SUCH A DEVICE, IN PARTICULAR FOR A HYBRID VEHICLE.
PCT/EP2015/078190 WO2016087434A1 (en) 2014-12-03 2015-12-01 Speed transmission device for moving a motor vehicle, notably a motorized at least two-wheeled vehicle, and power train using such a device particularly for a hybrid vehicle

Publications (1)

Publication Number Publication Date
EP3227582A1 true EP3227582A1 (en) 2017-10-11

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EP15805136.7A Withdrawn EP3227582A1 (en) 2014-12-03 2015-12-01 Speed transmission device for moving a motor vehicle, notably a motorized at least two-wheeled vehicle, and power train using such a device particularly for a hybrid vehicle

Country Status (5)

Country Link
EP (1) EP3227582A1 (en)
JP (1) JP2017538900A (en)
CN (1) CN107002828A (en)
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WO (1) WO2016087434A1 (en)

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CN109986957B (en) * 2017-12-29 2021-09-03 比亚迪股份有限公司 Power driving system and vehicle
CN109990053B (en) * 2017-12-29 2022-04-15 比亚迪股份有限公司 Transmission, power driving system and vehicle
CN112193049B (en) * 2020-10-23 2022-05-24 东风汽车集团有限公司 Multi-gear hybrid power gearbox

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FR2164001A5 (en) * 1971-12-09 1973-07-27 Peugeot & Renault
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JP2592406Y2 (en) * 1992-08-27 1999-03-24 株式会社 神崎高級工機製作所 Work vehicle transmission
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WO2016087434A1 (en) 2016-06-09
FR3029584B1 (en) 2018-03-16
CN107002828A (en) 2017-08-01
JP2017538900A (en) 2017-12-28
FR3029584A1 (en) 2016-06-10

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