Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
  • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
  • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
• • 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
  • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
  • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
  • F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
  • F16H2037/103—Power split variators with each end of the CVT connected or connectable to a Ravigneaux set
• • 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
  • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
  • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
  • F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
  • F16H2037/104—Power split variators with one end of the CVT connected or connectable to two or more differentials
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
  • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
  • F16H3/46—Gearings having only two central gears, connected by orbital gears
  • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
  • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
  • F16H3/56—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears both central gears being sun gears
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
  • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
  • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
  • F16H3/727—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path

Definitions

• the present invention relates to a gear transmission device, arranged between a driving motor and a driving receiving device, for example a driving machine, industrial or agricultural, or even the wheels of a motor vehicle.
• the object of the present invention is to develop a speed transmission apparatus making it possible to modify the transmission ratio without discontinuity, between two determined selectable limits, and without power limitation.
• the transmission device can be controlled manually or fully automatically, or by combining the two modes.
• a gear transmission device arranged between a drive motor and a drivable receiving device, comprising a first rotary casing arranged so as to be able to rotate around a first axis of rotation, a double planetary gear train which comprises a first train and a second train and which is arranged at least partially in said first rotary casing, between a drive input connected to the drive motor and an output shaft, arranged so as to be able to rotate around a second axis of rotation and connected to the drive receiving device, the aforementioned double train establishing between the drive input and the output shaft a transmission ratio between an input rotation speed and a output rotation speed, a first rotation transmission arranged at an intermediate output of the first planetary gear train, one two ith rotation transmission arranged at an intermediate input of the second planetary gear train, a first intermediate shaft arranged in one of said first and second rotation transmission, so as to be able to rotate around a third axis of rotation, a first electric motor brake acting
• the limits are a maximum output speed when the engine brake completely blocks the intermediate shaft and the drive motor is at its maximum power and a zero output speed when the input speed is zero.
• the speed variation range therefore only depends on the transmission ratio preset by the double planetary gear train chosen and on the application under given conditions, on the one hand, of the appropriate input speed and, on the other hand part, of the engine brake on the intermediate shaft to obtain the appropriate output speed, which can be positive or negative with respect to the drive motor.
• the apparatus further comprises a second intermediate shaft arranged in the other of said first and second rotation transmissions, so as to be able to rotate around a fourth axis of rotation, and a second electric motor brake, which acts on the second intermediate shaft, being capable of modifying a speed of rotation thereof, following commands received from the control means to which it is electrically connected.
• the first intermediate shaft and the second intermediate shaft have, in the absence of the engine brakes, different rotation speeds
• the engine brake acting on the fastest intermediate shaft is an alternator having coils, which excitation is varied to obtain a variable brake effect, and producing an electric current
• the engine brake acting on the slowest intermediate shaft is an electric motor, which is supplied by the electric current produced by said alternator and which provides a variable acceleration effect.
• the continuous variation of the engine brake effect is obtained by varying the excitation of the alternator coils, this variation being produced by means of the control means, either manually or by a computer which will take into account different data, such as the speed of the output shaft, the speed of rotation at the input, the requested transmission power, in a similar way to what happens in an automatic gearbox.
• the control means will now act continuously and not by jumps from certain limits.
• the first planetary gear train comprises an input shaft arranged at least partially in the first rotary casing so as to be able to rotate around the first axis of rotation and this input shaft is connected to the drive motor and serves as a motor input.
• the device comprises a second rotary casing, which is arranged so as to be able to rotate around a fifth axis of rotation and in which is housed the second planetary gear train of said double train, which allows a rotation transmission to the output shaft, the first gear train being housed in the first rotary casing.
• the double planetary gear train is divided into two separate trains, each of which is housed in a clean rotating housing.
• the first rotary casing is arranged so as to be driven in rotation by the drive motor, thus serving as the motor input of the device, and the double gear train is housed in the first rotary housing.
• the double gear train is enclosed in a single enclosure and the device is relatively compact.
• FIG. 1 shows a schematic embodiment, partially in section, of an apparatus according to the invention.
• FIG. 2 schematically represents another embodiment of the apparatus according to the invention.
• the transmission device shown is arranged between a current drive motor, not shown, and coupled to an input shaft 1, and a current drivable receiving device, not shown, and coupled to a drive shaft exit 2.
• the apparatus comprises a double planetary gear train which has a first planetary gear train housed in a first rotary casing 3 and a second planetary gear train housed in a second rotary casing 4.
• Each rotary casing, with its train of gears, is a known system that can be found on the market for example under the name of the REDEX epicyclic system (firm TEXROPE, cios Industrielle de Transmissions).
• the first gear train comprises a first planetary carrier plate 5, mounted on the input shaft 1 so as to rotate with it, about its axis of rotation 6, and a second planetary carrier plate 7, mounted on an intermediate output shaft 8 so as to be able to rotate with it, around this same axis of rotation 6.
• the input shaft 1 partially protrudes from the casing 3, which is coaxial with it, and this so as to be able to rotate freely relative to the casing.
• this input shaft 1 is hollow and serves as a guide centered on the intermediate output shaft 8, which is also coaxial with the input shaft, and also partially protruding from the casing 3, so to be able to rotate freely in relation to it.
• pivot axes 9 are supported parallel to the axis of rotation 6, so as to be able to rotate freely on themselves, but so as to be driven in revolution around the axis of rotation 6, when the casing 3 rotates.
• Each pivot axis 9 carries two satellites 10 and 11 so that they rotate together with this pivot axis.
• Each satellite 10 and 11 is engaged with one of the planetary carrier plates 5 and 7.
• the rotary casing 3 finally has a engagement system, for example an external toothing 12 shown diagrammatically, which can engage with a transmission of external rotation.
• the diameters of the casing 3, of the planetary carrier plates 5 and 7, and of the satellites 10 and 11 are chosen so as to establish between the input shaft 1 and the intermediate output shaft 8 a preselected transmission ratio (which may be modified according to the invention as described below).
• the second gear train comprises a third planetary carrier plate 13, mounted on an intermediate input shaft 14, so as to rotate around its axis of rotation. In the illustrated embodiment, this axis of rotation is coaxial with the axis of rotation 6.
• the second gear train further comprises a fourth planetary carrier plate 15 mounted on the output shaft 2 so as to be able to turn with it, this output shaft being again in the example of the Figure 1 coaxial with the axis of rotation 6 and partially projecting from the casing 4.
• the output shaft 2 is arranged so that it can rotate freely relative to the casing 4 and, in this example, it is provided hollow to serve as a guide centered on the intermediate input shaft 14, which also protrudes partially therefrom out of the casing 4, so that it can rotate freely relative to it.
• pivot axes 16 are supported parallel to the axis of rotation 6, so as to be able to rotate freely on themselves, but so as to be driven in revolution around the axis of rotation 6, when the casing 4 rotates.
• Each pivot axis 16 carries two satellites 17 and 18 so that they rotate together with this pivot axis 16.
• Each of the satellites 17 and 18 is engaged with one of the planetary carrier plates 13 and 15.
• the rotary casing 4 has an engagement system, for example an external toothing 19 shown diagrammatically, which can engage with an external rotation transmission.
• the diameters of the casing 4, of the planetary carrier plates 13 and 15 and of the satellites 17 and 18 are chosen so as to establish between the intermediate input shaft 14 and the output shaft 2 a preselected transmission ratio (which may be modified according to the invention as described below).
• the double planetary gear train illustrated must be chosen so as to establish a given transmission ratio between the input rotation speed and the output rotation speed.
• a first intermediate shaft 20 is arranged parallel to the axis of rotation 6, so as to be able to rotate on itself. He wears two toothed gears 21 and 22 which are each capable, by a gear, of engaging with the toothing 12 of the casing 3 and respectively the toothing 19 of the casing 4. This arrangement thus produces a first rotation transmission at an intermediate output of the casing 3, transmission which is also engaged with the casing 4.
• the intermediate output shaft 8 and the intermediate input shaft 14 together form, or provide between them coaxially, an intermediate shaft 23 which thus performs a second rotation transmission between the first planetary gear train and the second, at an intermediate entrance to it.
• a first engine brake 24 is arranged so as to be able to act on the first intermediate shaft 20.
• This engine brake can for example be a current alternator, provided with coils, which is electrically connected to a control center 25, for example a computer which integrates input data, such as the power of the drive motor, the rotation speed of the input shaft, the speed of the output shaft, etc. and which can act automatically on the motor brake 24 so that the latter releases the intermediate shaft 20, either the brake, or even possibly blocks it, by varying the excitation of the coils.
• the energy released is transformed by the alternator into electric current.
• a second motor brake 26 can also be arranged so as to be able to act on the second intermediate shaft 23, for example by means of toothed gears shown schematically.
• This second motor brake can for example be an electric motor which is electrically connected to the control center 25, as well as to the first motor brake 24, in order to be able to be supplied with current at least partially by the latter.
• the control center 25 can act automatically on the engine brake 26 so that the latter releases the intermediate shaft 23, either the brake, or the blocks, by varying the current supply to the electric motor. This recovers the energy released by the first engine brake.
• This arrangement thus makes it possible to separate on two different axes (the two intermediate shafts) a single input speed, and this by means of the first gear train, which thus forms a first differential, to create an interaction between these two axes, by means of at least one of the engine brakes, before remixing the two gears in the second gear train, which thus forms a second differential.
• This interaction makes it possible to continuously vary the ratio between the input speed and the output speed. This effect is obtained in particular because the speeds at the outputs of a differential change relative to each other as a function of the resisting torque.
• ⁇ represents the speed of rotation of the element indicated in subscript
• d represents the diameter of the element indicated in subscript.
• a speed of exit ⁇ 2 which can vary between 16 times the speed of entry ⁇ , and -8 / 7 times the speed of entry ⁇
• the first case corresponds to a forward drive and the second case to a reverse.
• the intermediate shaft 20 is blocked by the engine brake 24 and the intermediate shaft 23 is free.
• the intermediate shaft 23 is blocked by the engine brake 26 and the intermediate shaft 20 is released and rotates in the opposite direction. The variation between these two limits is continuous by the set of engine brakes which act on the intermediate shafts.
• the axes of rotation of the casing 3, of the casing 4, of the input shaft 1, of the output shaft 2, of the intermediate output shaft 8 and the intermediate input shaft 14 are coaxial, it is possible to provide that some of them are not. It is possible for example that the rotation transmission between the intermediate output shaft 8 and the intermediate input shaft 14 form one or more return angles. The same is true for the transmission of rotation between the housing 3 and the housing 4.
• the rotary casing 27 is unique and the double planetary gear train is completely housed inside it. It is with the rotary housing
• the rotary casing therefore serves here as a drive input.
• the double gear train consists of two trains merged into each other.
• the first gear train comprises a planetary carrier plate 29 mounted on an output intermediate shaft 30, so as to rotate with it, a central plate 31 mounted on the output shaft 32 so as to rotate with it and satellites 33 and 34 arranged between the planetary carrier plate 29 and respectively the central plate 31, on several pivot axes 41 parallel to the axis of rotation 6 of the casing.
• the satellites are driven in revolution around this axis when the casing 27 rotates.
• Each pivot axis 41 carries two satellites 33 and 34 which are each engaged with the planetary carrier plate 29 or the central plate 31.
• the second gear train comprises a planetary carrier plate 35, mounted on an intermediate input shaft 36, so as to rotate about its axis of rotation, and the central plate 31 described above. It also includes satellites, satellite 37 and satellite 34 described above. The satellites 37 are each arranged, like the satellites 33 and 34, on a pivot axis 41.
• the first rotation transmission comprises the intermediate output shaft 30 as the first intermediate shaft on which the engine brake 38 acts by a set of gears.
• the second rotation transmission comprises the intermediate input shaft 36 as the second intermediate shaft on which the engine brake 39 acts.
• the two engine brakes are electrically connected to the control center 40 and to each other.
• the axes of rotation of the casing 27, the output shaft 32, the intermediate output shaft 30 and the intermediate input shaft 36, are coaxial.
• This embodiment has the advantage of less bulk.
• the advantages of the transmission devices according to the invention are inter alia the following: - they make it possible to run any motor permanently at its best efficiency for the requested power, which leads to minimum consumption,
• the efficiency of the transmission device itself is very high and comparable to that of existing mechanical gearboxes, the transmission of power from the drive motor to the drive receiver device being done by means of gears as in the case of the boxes. mechanical speeds.

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• 2001
  • 2001-07-04 BE BE2001/0451A patent/BE1014275A3/fr active
• 2002
  • 2002-07-03 US US10/482,287 patent/US7037230B2/en not_active Expired - Fee Related
  • 2002-07-03 JP JP2003510843A patent/JP2004532962A/ja active Pending
  • 2002-07-03 WO PCT/BE2002/000112 patent/WO2003004905A1/fr not_active Application Discontinuation
  • 2002-07-03 EP EP02748476A patent/EP1402202A1/de not_active Withdrawn
• 2006
  • 2006-03-23 US US11/277,255 patent/US7166051B2/en not_active Expired - Fee Related

Non-Patent Citations (1)

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