Classifications

• • H—ELECTRICITY
  • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
  • H02P—CONTROL OR REGULATION OF ELECTRIC MOTORS, ELECTRIC GENERATORS OR DYNAMO-ELECTRIC CONVERTERS; CONTROLLING TRANSFORMERS, REACTORS OR CHOKE COILS
  • H02P9/00—Arrangements for controlling electric generators for the purpose of obtaining a desired output
  • H02P9/04—Control effected upon non-electric prime mover and dependent upon electric output value of the generator
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
  • F03D—WIND MOTORS
  • F03D15/00—Transmission of mechanical power
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
  • F03D—WIND MOTORS
  • F03D15/00—Transmission of mechanical power
  • F03D15/10—Transmission of mechanical power using gearing not limited to rotary motion, e.g. with oscillating or reciprocating members
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
  • F03D—WIND MOTORS
  • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
  • F03D9/20—Wind motors characterised by the driven apparatus
  • F03D9/25—Wind motors characterised by the driven apparatus the apparatus being an electrical generator
• • 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
  • F16H3/724—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 using external powered electric machines
• • 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
  • F16H37/0833—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 with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • 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
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
  • F05B2260/00—Function
  • F05B2260/40—Transmission of power
  • F05B2260/403—Transmission of power through the shape of the drive components
  • F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
  • F05B2260/40311—Transmission of power through the shape of the drive components as in toothed gearing of the epicyclic, planetary or differential type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • 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
  • F16H37/0833—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 with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
  • F16H37/084—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 with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
  • F16H2037/0866—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • 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
  • F16H2037/102—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 the input or output shaft of the transmission is 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
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H2061/0075—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by a particular control method
  • F16H2061/0078—Linear control, e.g. PID, state feedback or Kalman
• • 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
  • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
  • F16H59/36—Inputs being a function of speed
  • F16H59/38—Inputs being a function of speed of gearing elements
  • F16H59/40—Output shaft speed
• • H—ELECTRICITY
  • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
  • H02P—CONTROL OR REGULATION OF ELECTRIC MOTORS, ELECTRIC GENERATORS OR DYNAMO-ELECTRIC CONVERTERS; CONTROLLING TRANSFORMERS, REACTORS OR CHOKE COILS
  • H02P2101/00—Special adaptation of control arrangements for generators
  • H02P2101/15—Special adaptation of control arrangements for generators for wind-driven turbines
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
  • Y02B10/00—Integration of renewable energy sources in buildings
  • Y02B10/30—Wind power
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
  • Y02E10/00—Energy generation through renewable energy sources
  • Y02E10/70—Wind energy
  • Y02E10/72—Wind turbines with rotation axis in wind direction
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T74/00—Machine element or mechanism
  • Y10T74/20—Control lever and linkage systems
  • Y10T74/20012—Multiple controlled elements
  • Y10T74/20018—Transmission control

Definitions

• Transmission device for a machine for generating electricity from a variable speed power source, an electric power generating unit and a wind turbine thus equipped, and a transmission ratio transmission method
• the present invention relates to the field of wind turbines or any other field in which an electric generator must be connected to a variable speed drive source.
• the invention relates more particularly to a transmission device for a machine for generating electricity from a variable speed rotary power source, in particular a wind turbine propeller.
• the invention also relates to a power generation unit suitable for being driven by a wind turbine propeller.
• the invention also relates to a wind turbine equipped with the transmission device or the power generation unit.
• the invention also relates to a method for adjusting a transmission ratio.
• Wind turbines are also known provided with a generatrix with variable number of poles. By modifications of the pole connection, such a generator can operate with different numbers of poles, and therefore accept different speeds of rotation.
• the frequency of the electric current produced varies according to the speed of rotation of the generator, which makes it impossible to connect to the network or requires a complex transformation to obtain a frequency compatible with that of the network.
• a technology with two generators requires a switch from one generator to the other in the supply of the power grid, and therefore the need to regularly adjust the frequency and the phase of the product current to that of the network. This problem increases the price of the installation and does not significantly increase the efficiency of the wind turbine.
• a transmission device for a wind turbine generator uses a main speed transmission channel between the propeller and the rotor of the generator, and a regulating voice. parallel in which is provided a hydraulic torque converter. But stabilizing the drive speed of the generator is not enough. The frequency of the produced current fluctuates between 50 and 60 Hertz. The converter dissipates energy in the form of heat.
• WO 81/01444 provides between the propeller and the axis of the generator, a parallel control channel through a hydraulic drive, mechanical or electrical. The drive is controlled according to two signals representative of the speed of the propeller on the one hand, and the speed of the axis of the generator on the other hand.
• This motor-driven dimmer requires a high control energy, which consumes at least 10 to 15% of the energy produced by the generator.
• the current produced can be used in a local network, for example a group of houses.
• a local network for example a group of houses.
• the object of the present invention is to overcome at least some of the foregoing disadvantages, in particular with a view to reducing the cost and / or complexity, and / or to improving the energy efficiency and / or frequency stability of the production of electricity.
• the transmission device for a machine for producing electricity from a variable speed rotary power source comprising a frame, an input shaft connected to the driving source. an output shaft connected to a rotor of the machine, and at least two transmission paths, at least one of which passes through a differential mechanism with at least three rotary members, is characterized in that one of the transmission paths comprises two rotary elements which are in dynamic coupling and kinematic decoupling relationship, and which have relative to each other, due to the connection of each of them with the rest of the transmission device, a relative speed causing a relative rotation in a control apparatus which establishes between the rotary members a torque varying in the direction of maintaining the rotor of the machine at a predetermined speed, in particular substantially constant nte.
• the torque variation is defined by a characteristic relationship of the apparatus between its torque and a rotational speed in the apparatus.
• the variation of the torque is defined by a control, in particular a control loop of the torque
• the variation of the torque exerted by the regulating device between the two rotary elements makes it possible, in a very simple way, to influence the transmission ratio established by the differential mechanism, and thus on the transmission ratio between the gear shaft. input and the output shaft of the transmission device.
• the transmission device makes it possible, if desired, to maintain a determined speed, typically substantially constant at the input of the electricity generating machine supplying the network, even when the speed of rotation of the driving source is extremely low, for example close to 1 turn per minute.
• the transmission device thus gives, for example, the possibility of permanently maintaining the power supply of the network by the electricity generating machine, which avoids having to frequently adapt the frequency of the electric current produced by the machine to the frequency of the network, and therefore dispenses to provide bulky and expensive equipment for this purpose.
• the maximum power of the control device can remain extremely limited, for example of the order of 3 to 5%, or even less, the power of the main machine.
• the regulating device may be a motor which injects into the transmission device an additional amount of mechanical energy which is found as a supplement on the output shaft for driving the machine for producing electricity. If this control motor is electric, it can be powered by electricity taken from that produced by the power generation machine.
• the regulating apparatus is an electric generator.
• a generator allows to feed electrically various functional organs of a wind turbine or other form of power generation unit.
• functional units are, for example, a wind turbine orientation motor, or a propeller blade orientation motor, lighting or light-signaling devices, etc.
• Excess electricity can supply storage batteries and / or an electric motor driving the output shaft of the transmission device to increase the mechanical power supplied to the power generating machine.
• the generator or other control device can be controlled by a single electrical signal, which allows a high degree of control accuracy.
• the electrical signal can be generated according to a permanent or cyclic comparison between the rotational speed of the rotor of the production machine and a set point in advance for this speed. It is also possible to take into account the rotation speed of the input shaft to generate a basic value of the signal, the regulation of the rotor speed of the production machine being done by varying the value of the signal around this basic value.
• the regulating apparatus may be an electric generator of the variable pole number type.
• a generator is able to operate with, between its rotor and its stator, an "electric" speed different from the kinematic speed. This is advantageous for optimizing the efficiency and power of the electric generator when the arrangement of the transmission device and the expected operating conditions cause large variations in the kinematic speed of the rotor relative to the stator in the control generator.
• the regulating device it is possible to install the regulating device directly between the two elements.
• a relative speed which is equal to the difference in speed of rotation of the two elements.
• the rotor of an electric generator turns with one of the elements, while the constituent usually called “stator” is here a rotating element with the other element.
• revolving connections are necessary for the energy connection, typically electrical, of the control device, as well as for its control and other possible control and regulation links.
• such an apparatus operates satisfactorily only if the relative speed between the rotor and stator is at least of the order of 1000 revolutions per minute. This results for the regulating device a certain power value.
• the invention provides an advantageous alternative to the solution of directly mounting the device between the two rotating elements.
• the two elements are connected to the two inputs of a comparator differential gear having a rotary output indicative of the difference, possibly weighted, of the absolute values of the rotational speeds of the two elements, and the shaft of the device is connected to the rotary output.
• the apparatus is then mounted between the rotary outlet and the frame, and, according to another advantageous feature, the device comprises means for multiplying the speed of rotation of the shaft of the apparatus relative to that of the outlet.
• rotary differential gear comparator rotary differential gear comparator
• the regulating apparatus can have a fixed stator, and the absolute value of the speed of its rotor or other moving part is considerably reduced.
• the rotating connections are no longer necessary, and we can have between the two rotating elements a difference in speed as low as we want since we can multiply as much as we want the speed of entry of the device relative at the output speed of the comparator differential.
• the device comprises means for rotating the two rotating elements in opposite directions from each other.
• the differential differential gear can then be of a type having satellites meshing with two opposite planetary gears. Satellites are carried by a cage which rotates at a speed equal to the algebraic average (thus half of the difference of the absolute values when the speeds are reversed from one another) speeds of two planetary each constituting one elements.
• a comparator differential gear capable of outputting a speed indicative of the possibly weighted difference between two rotation speeds in the same direction is also conceivable, as will be seen in the description of the examples.
• weighted difference calculated between two values (two speeds) multiplied by different coefficients.
• a non-zero weighted difference is obtained when the rotational speeds have equal absolute values. This may be useful in certain embodiments described below, in particular for generating in the regulating apparatus a speed proportional to the absolute value of the speed of rotation of the two elements.
• the invention teaches a kinematic interruption between two elements which are mechanically in series along a transmission path, to connect these two elements to the two inputs of a comparator differential gear arranged so that the rotary output of this comparator differential gear rotates at a speed representative of the difference, possibly weighted, between the absolute values of the speeds of the two elements, of connecting the rotary output to a dynamic control device for energy sampling, such as an electric generator, a pump, etc., or of energy injection, such as a motor, this apparatus realizing either by its own characteristic or by a control which is associated with it a regulation or regulation of the rotational speed the transmission path, the torque transmitted by the transmission path, the slip between the rotational speeds of the two el things, etc.
• a dynamic control device for energy sampling such as an electric generator, a pump, etc.
• energy injection such as a motor
• the transmission path comprising the two elements comprises means for multiplying the speed of rotation of each element.
• the two elements rotate faster and a difference in speed given between the two elements corresponds to a lower power of the control device and a smaller proportion of the power passing through the transmission path.
• one of the elements is in a fixed ratio meshing relationship with one of the input and output shafts
• the other member is in a fixed ratio meshing relationship with a rotary member of the differential mechanism, which rotary member is itself in variable ratio meshing relationship with each of the input and output shafts.
• the at least one differential mechanism comprises two differential mechanisms each comprising three rotary members, and the at least two transmission paths comprise three transmission paths each connecting a rotational member of one of the mechanisms to a second one. respective rotary member of the other mechanism.
• the two elements are then part of one of the three paths.
• This embodiment makes it possible to ensure that the two elements rotate continuously at speeds whose absolute values can be very close to each other or even equal, so that the energy involved in the
• the control apparatus can be very small, in theory as small as desired, even if the transmission ratio between the input shaft and the output of the transmission device varies within a very wide range.
• one of the three paths is an input path comprising a transmission member secured to the input shaft, and another of the three paths is an output path comprising a transmission member integral with the shaft.
• the transmission device can be considered as having two differential mechanisms connected in parallel between the input shaft and the output shaft, and further coupled with each other by the third transmission path.
• the device comprises a difference between the two differential mechanisms, and / or a difference in at least one of the transmission paths, and / or a difference in the coupling of the two rotary elements with the regulating device so that the regime of The operation of the transmission device is dependent on the dynamic action of the control device.
• the transmission ratio is a direct function of the speed of the input shaft
• the rotation speed applied to the device by the two elements varies according to the speed of the input shaft.
• the speed of rotation of the apparatus defines the transmission ratio.
• the rotational speed applied to the apparatus increases as the speed of the input shaft increases.
• the apparatus such as an electric generator
• the increase in the torque of the electric generator accompanies the increase in torque in the transmission path. having both elements.
• the set may be able to regulate itself automatically. A finer regulation is feasible, for example by varying the excitation applied to a control device consisting of an electric generator.
• One of the differential mechanisms can be mounted to have two of its rotary members in connection respectively with the input shaft and with the output shaft, and a third rotary member producing an average, possibly weighted, of the speed of the input shaft and the speed of the output shaft.
• the weighting is chosen so that, depending in particular on the speed of the input shaft, the average thus obtained, applied at least indirectly to the third rotary member of the other differential mechanism, cause this other differential mechanism to produce the ratio of desired transmission between the input shaft and the output shaft.
• one of the transmission paths comprises a kinematic interruption bridged by a dynamic coupling provided by the control device.
• the two differential mechanisms are identical.
• at least one of the three transmission paths defines between the two rotary members that it connects a transmission ratio different from that defined by another one of the three paths between the two rotary members connected by this other path.
• the mechanisms are identical and two of the three transmission paths define identical transmission ratios and constitute in particular rigid connections each ensuring a common rotation of a rotary member of one of the differential mechanisms and a rotary member respective differential mechanism.
• the third path interconnecting the two third rotary members of the two differential mechanisms, may have a different mechanical transmission ratio to generate a speed difference between the two rotary elements.
• the two differential mechanisms are of identical architecture and have a gear ratio difference.
• the three transmission paths then preferably define identical transmission ratios.
• the two mechanisms are coaxial and at least one of the transmission paths, preferably two of the three transmission paths are links ensuring a common rotation of two rotating members each belonging to one of the mechanisms.
• the differential mechanism is preferably realized. in the form of an epicyclic gear train, comprising a planetary wheel connected to the output shaft, a ring gear constituting a rotary reaction member, and a planet carrier (s) connected to the input shaft and supporting the least one crew of two cascaded satellites, one of which meshes with the sun wheel and the other with the ring gear.
• Such a type of differential mechanism has the remarkable feature of providing a ratio of overdrive varying from 1 to infinity when the speed of the crown varies, respectively, a speed equal to the speed of the sun wheel at a speed equal to a fraction of the speed of the wheel planetary. Said fraction is equal to the ratio of toothing between the sun wheel and the crown. It is very advantageous to choose such a differential mechanism in which the number of teeth of the crown is twice that of the planet wheel.
• the invention relates to a power generation unit comprising a transmission device according to the first object, and a synchronous type power generation machine.
• the invention makes it possible to achieve perfect stabilization of the rotational speed of the electricity generating machine which consequently delivers a current stable in frequency and in phase.
• the power generation unit comprises a rotor speed sensor of the electric power generating machine, and a regulation loop of this rotational speed, which controls the apparatus in accordance with the invention. difference between the rotational speed of the rotor and a setpoint.
• the invention relates to a wind turbine comprising a transmission device according to the first object, and / or a power generation unit according to the second object.
• the method for adjusting a transmission ratio between a driving source and a load is characterized in that between the driving source and the load are placed two differential mechanisms each having at least three rotary members. each rotary member of one of the mechanisms being connected to a respective rotational member of the other mechanism by a respective transmission path, one of the paths comprising two rotary members connected by the action of a dynamic coupling apparatus , and the coupling apparatus is adjusted.
• FIG. 1 is a schematic axial view of a first embodiment of a wind turbine according to the invention
• FIG. 2 is a basic front view of the epicyclic gear train used in the wind turbine of FIG. 1;
• FIG. 3 is a half-front view of the epicyclic gear train, illustrating certain of its geometric and operating dimensional characteristics
• the hatches drawn on the rotating elements indicate their direction of rotation. In the case of satellites, this is the direction of rotation around their own axis.
• the wind turbine which is only partially represented, comprises a propeller 1 which drives the rotor 2 of an electricity generating machine 3 via an overdrive. input 4 followed by a transmission device 6 according to the invention.
• the stator 7 of the machine 3 is fixed to a frame 8 which is only symbolized.
• the electricity generating machine 3 can be a synchronous generator rotating at a perfectly stabilized speed, for example 1500 revolutions per minute, stably producing a current of 50 Hertz compatible with the network.
• the propeller 1 rotates at a very variable speed typically between 1 and 30 revolutions per minute depending on the strength of the wind.
• the overdrive 4 increases this speed by multiplying it by a constant factor, for example a factor of 50.
• the transmission device 6 establishes a transmission ratio which varies continuously to multiply from 30 times to once the rotational speed of its output shaft 12 integral with the rotor 2 of the machine 3 with respect to the speed of rotation of its machine. input shaft 11.
• the transmission device 6 comprises a differential mechanism 13, in this example a planetary or epicyclic gear train, composed of three rotary members, namely a sun gear 14 connected to the output shaft 12, a ring gear 16 constituting a rotary member of reaction, and a planet carrier 17 connected to the input shaft 11.
• the planet carrier 17 supports at least one crew of two satellites 18, 19 cascaded, meshing with each other.
• the satellite 18 meshes with the external toothing of the sun gear 14 and the satellite 19 meshes with the internal toothing of the ring gear 16.
• This type of epicyclic gear train with pairs of cascaded satellites has the following particularities: for a transmission ratio equal to 1: 1 between the input shaft 11 and the output shaft 12, the sun gear 14, the ring 16 and the planet carrier 17 rotate at the same speed.
• R1 is the tooth radius of the sun wheel
• R2 is the tooth radius of the ring 16 (see FIG. 3).
• the transmission device regulates the rotational speed Vc of the ring gear 16 so that, by virtue of the above relationship, the output shaft 12 rotates at the desired value V s and / or the ratio V s / V e take the desired value.
• the transmission device 6 defines between the input shaft 11 and the output shaft 12 two transmission paths TC and TD.
• the kinematic path TC comprises the differential mechanism 13 and an intermediate shaft 21 rigidly connecting the sun gear 14 with the output shaft 12.
• the dynamic path TD comprises the differential mechanism 13, and a kinematic interruption bridged by a particular dynamic link between the crown 16 and the output shaft 12.
• the TD transmission path comprises two rotary elements 22, 23 which are in power transmission relationship while being decoupled kinematically and having a relative speed causing relative rotation with respect to each other.
• the first rotary element 22 rotates at a speed which is in a fixed ratio with the rotational speed of the ring gear 16.
• the first rotary element 22 is integral with a pinion 24 which meshes with an outer toothing 22 of the ring gear 16.
• the second rotary element 23 rotates at a speed which is in a fixed ratio with the speed of the output shaft 12.
• the second rotary element 23 is secured to a pinion 27 which meshes with a toothed wheel 28 integral with the output shaft 12.
• the intermediate shaft 21 extends between the sun gear 14 and the gear wheel 28.
• the transmission paths TC and TD are connected to one another. to the other at one end by the differential mechanism 13 and at the other end by the toothed wheel 28 because it is integral in rotation with the intermediate shaft 21 and meshes in a fixed ratio with the pinion 27.
• the two rotary elements 22 and 23 are mounted in rotation along a geometric axis common 29 which is fixed and located parallel and at a distance from the general axis 31 of the output shaft 12 and input 11, which is also the axis of the differential mechanism 13 and the intermediate shaft 21.
• a regulating apparatus 32 is mounted to establish between the rotary elements 22 and 23 a torque which varies in the direction of holding the rotor 2 of the machine 3 at a determined speed, in particular substantially constant.
• control device 32 is an electric generator, for example an alternator, whose rotor 33 is integral with the element 22 rotating at a predetermined speed relative to the ring 16.
• the stator 34 of the generator 32 instead of being fixed as a conventional stator, is here a rotating stator fixed in rotation with the second rotary element 23 rotating at a predetermined speed with respect to the output shaft 12.
• the tooth ratios between the pinion 24 and the external toothing 26 of the ring 16 on the one hand, and between the pinion 27 and the toothed wheel 28 on the other hand, are such that i) the rotary elements 22 and 23 rotate in the same direction and ii) the rotational speed of the rotary element 22 coupled to the ring gear 16 is always greater than that of the rotary element 23 coupled to the output shaft 12.
• the smallest possible speed for the ring gear 16 is equal to half that of the output shaft 12. It can therefore be ensured that the first rotary element 22 always turns faster than the second rotary member 23 overdrive twice more the speed of rotation of the element 22 relative to the ring gear 16 than the speed of rotation of the element 23 relative to the output shaft 12.
• these overdrive ratios are chosen relatively high, so that the rotating members 22 and 23 rotate at relatively high speeds compared to the speed of rotation. rotation of the input shaft 11 and the output shaft 12.
• the second element 23 it is possible for the second element 23 to rotate at 14,000 rpm and the first element 22 between 15,000 and 30,000 revolutions per minute. minute.
• the rotor 33 rotates faster than the rotating stator 34.
• the electromagnetic forces existing between the rotor 33 and the stator 34 are in the direction tending to brake the rotor 33 and therefore the ring 16, and in the the direction of accelerating the stator 34 and thus the output shaft 12.
• the energy transfer is therefore carried out from the differential mechanism 13 to the output 12 through the TD dynamic transmission path. It also takes place from the input shaft 11 to the output shaft 12 through the kinematic transmission path TC because the sun gear 14 undergoes from the satellite 18 a torque in the SR direction (FIG. the rotation of the wheel 14.
• the two transmission paths are motors for the output shaft 12.
• the torque transmitted by the dynamic transmission path TD is proportional to the input torque present on the input shaft 11.
• the speed Vs of the output shaft 12 is constant, the speed of rotation of the rotor 33 relative to to the stator 34 is only a function of the rotation speed Ve of the input shaft 11.
• the torque on the input shaft 11 increases. , for example proportionally, with the rotation speed Ve of the input shaft 11. Therefore, the regulation according to the invention requires that the electromagnetic torque existing between the rotor 33 and the stator 34 increases when the rotation speed of the The rotor 33 increases with respect to the stator 34.
• a device By choosing a regulating device 32 having a characteristic curve suitably chosen with respect to its torque as a function of the speed of rotation of its rotor relative to its stator, a device is made available.
• transmission system capable of automatically stabilizing the rotational speed of the rotor 2 of the power generation machine 3 without the need for a control driving circuit.
• a control device is provided for a finer control and a better accuracy of the rotational speed of the rotor 2 of the electricity generating machine 3.
• It comprises a sensor 36 of the rotational speed of the output shaft 12, a memory or the like 37 for a rotational speed reference of the stator 2, a comparator 38 to determine a possible difference between the real speed of the shaft 12 and the setpoint, and a circuit 39 for converting the output of the comparator 38 into an excitation current applied to the stator 34 via one or more rotating contacts 41 provided on the rotary member 23.
• a sensor 42 of the rotation speed Ve of the input shaft 11 has also been provided. The sensor 42 sends a signal to the circuit 39 to select ranges of current values. excitation according to the speed Ve.
• an automatic gear change device can be interposed in the TD transmission path, for example between the pinion 24 and the stator 33, an automatic gear change device continuously variable or finite number of reports.
• the automation of this device tends permanently or cyclically to adjust the speed of rotation of the rotor 33 so that it presents an optimum difference with respect to that of the stator 34.
• This improves the efficiency of the regulator generator 32, and can significantly reduce the power absorbed by the generator 32, in particular by reducing the speed difference between the rotor 33 and the stator 34 for the high values of the speed Ve of the input shaft 11.
• the circuit of pilot described above automatically corrects the excitation of the generator 32 according to the transmission ratio established by the gearshift device.
• circuit 39 an input for a signal informing circuit 39 of the established report. by the gearshift device.
• the circuit 39 is thus able to anticipate the excitation variations to be made instead of reacting to fluctuations in the speed of rotation of the rotor 2 of the machine 3.
• the presence of the gearshift device makes it possible to between the toothed wheel 28 and the pinion 27, between the gear wheel 28 and the gear wheel 27, the gear wheel 24, on the other hand, has different ratios from those previously described, and which have in any case been given only example.
• the generator 32 in the form of a generatrix with changing poles.
• This known type of generator generates a variable electrical rotation of the stator poles relative to the mechanical structure of the stator. It is thus possible to modify and particularly optimize the difference in electrical speed between the rotor and the stator.
• the circuit 39 may be designed to apply a suitable control to the stator 34 by the rotary contacts 41 or any other rotating contact provided in addition, taking into account for example the signal provided by the detector 42 representative of the input speed ve.
• the electricity produced by the generator 32 is collected by virtue of rotary rotor contacts 43 provided, for example, around the periphery of the rotary element 22. This electrical energy then reaches for example a rectifier 44 for charging batteries 46 and / or feeding the boundaries of one or more uses 47.
• the second rotary member 23 is now in a fixed transmission ratio with the third rotary member or cage 48 of a second differential 49.
• the first two rotating members of the second differential 49 are two bevel gears 51, 52 having identical teeth and disposed opposite one another. These two planetaries are in a fixed transmission ratio, one (51) with the input shaft 11, the other (52) with the output shaft 12.
• These three rotary members 48, 51, 52 have a common axis of rotation 53 fixed relative to the frame, and parallel and spaced relative to that 29 of the rotary elements 22 and 23 and 31 of the input shaft 11 and output shaft 12.
• Conical satellites 54 are mounted freely rotatable inside the cage 48 along axes perpendicular to the axis 53. Each conical satellite 54 meshes with the two planetaries 51 and 52. In such a differential, the cage 48 rotates around the common axis 53 at a speed which is equal to the average algebraic rotational speeds of the two planetary. In this case, the assembly is such that the two planetary rotate in the same direction. Thus, the cage 48 rotates at a speed which represents an arithmetic mean of the speed of the input and output shafts 12.
• the two rotary members 16, 48 connected by the third path tend, one (16), to reduce the transmission ratio of its differential mechanism when its speed increases, and the other (48), to increase the transmission ratio of its differential mechanism as its speed increases.
• the idea underlying this embodiment is as follows: when the speed Ve of the input shaft 11 varies from 50 to 1500 rpm, the speed of the ring 16 must vary from approximately 750 at 1500 rpm, which is similar to the variation in the average speed of the input and output shafts. The idea is to generate a speed representative of this average and to apply it directly or indirectly to the ring 16.
• the second rotary element 23 that is to say the stator of the generator 32, is applied to a speed judiciously generated from the input and output speeds. output so that this speed varies similarly to the desired speed for the crown, but always being lower than it.
• a typical control apparatus such as an electric generator needs at least a certain level of rotor speed relative to the stator to function well, for example at least 1000 rpm. For such a difference in speed to be only a small fraction of the speed of the rotating elements 22 and 23, it is advantageous to provide means for multiplying the speed of the rotary elements 22 and 23 relative to those of the shaft. input 11 and the output shaft 12.
• the pinion 24 integral with the rotary member 22 has for example a diameter equal to 1 / 20th of that of the outer toothing of the ring 16.
• the element 22 thus rotates 20 times faster than the crown 16.
• Multiplying gears 56 and 57 are also provided between the input shaft 11 and the sun gear 51 on the one hand, between the output shaft 12 and the sun gear 52 on the other hand.
• the rotational speed of the cage 48 has an amplified value with respect to the arithmetic average of the speeds Ve and Vs. This amplified average is transmitted in a ratio
• the average speed provided by the cage 48 corresponds to a weighted average.
• the relationship between the speed of rotation of the cage 48 on the one hand and the ratio Ve / Vs on the other hand can be finely adjusted.
• the crown 16 runs from 750 to 1500 Rotations per minute.
• the element 22 rotates 20 times faster, that is to say 15,000 to 30,000 revolutions per minute. If it is desired that the speed difference between the elements 22 and 23 varies from 1000 to 2000 revolutions per minute, the element 23, therefore the cage 48, must rotate from 14,000 to 28,000 revolutions per minute. This is (approximately) achieved if the overdrive ratio of the gear 56 is 19: 1 and the overdrive ratio of the gear 57 is 18: 1. With such a choice, the energy absorbed by the generator 32 is of the order of 6 to 7% of that flowing in the transmission path T3.
• two differential mechanisms 13, 48 are connected in parallel between the shaft of 11 and the output shaft 12.
• Each of these differential mechanisms has an input member 17, 51 connected to the input shaft 11, an output member 14, 52 connected to the output shaft 12, and a reaction member 16, 48.
• the two reaction members 16, 48 are connected together by a transmission path T3 but are not in a fixed ratio with either the input shaft 11 or the output shaft 12
• the two differential mechanisms can not establish the same transmission ratio between the input shaft 11 and the output shaft 12 unless the speed of their reaction members 16, 48 are in a different relationship to that which would correspond to a connection of the elements 22 and 23.
• the two differential mechanisms are indeed obliged to establish the same transmission ratio between the input shaft 11 and the output shaft 12, it there exists between the elements 22 and 23 a difference in speed which is a function of the ratio Vs / Ve. It is therefore possible to adjust the transmission ratio Vs / Ve by adjusting the difference in speed between the elements 22 and 23. This difference in speed is regulated by controlling the activation of the dynamic coupling 32.
• a first path T1 or input path, connects in determined tooth ratios the input shaft 11 with an input member 17 of the first mechanism 13 and an input member 51 of the second mechanism 49.
• a second path T2, or output path connects in determined gear ratios the output shaft 12 with an output member 14 of the first mechanism 13 and an output member 52 of the second mechanism 49.
• a third path T3, or path of reaction links in a specific relationship a reaction member 16 of the first mechanism 13 with a reaction member 48 of the second mechanism 49. There is somewhere in one of the three paths a kinematic interruption bridged by a dynamic coupling.
• the dynamic coupling by the control device 32 is inserted either in the third transmission path T3 between the ring 16 and the cage 48, but in the second path or output path T2. More particularly, the kinematic interruption bridged by the dynamic coupling 32 is placed between the output member 52 of the second differential mechanism 49 on the one hand and the multiplier gear 57 connecting with the output shaft 12.
• the third path T3 transmission is greatly simplified since it consists of a direct meshing between the periphery of the ring 16 and the cage 48. There are only two geometric axes, the general axis 31 and the axis 53 which is now common to the differential 49 and the generator 32. There is one less intermediate gear in each of the multiplier gears 56 and 57.
• FIG. 6 The embodiment of FIG. 6 will only be described for its differences with respect to that of FIG.
• the differential mechanism 13 is of a simple satellite type 58, and no longer a pair of cascaded satellites. Each satellite 58 meshes with the sun gear 14 and with the internal toothing of the ring gear 16.
• Such a differential mechanism provides a high overdrive ratio of the sun gear 14 relative to the planet carrier 17 when the ring gear 16 rotates in the opposite direction of the planet carrier 17 and the planet wheel 14.
• the overdrive ratio reaches 3: 1 when the crown is stopped, and 90: 1 when the crown rotates 43.5 times faster than the shaft 11.
• the overdrive 4 produces a ratio of overdrive which is only about 17: 1, so that the speed of rotation of the shaft Input 11 now ranges from 17 to 500 rpm.
• the overdrive ratio of the gear 56 is about three times higher than that of the gear 57.
• the speed of the cage 48 is substantially representative of half the speed of the output shaft 12.
• the input speed is maximum (500 revolutions per minute)
• its value three times more overdrive than that of the output shaft is introduced in reverse in the differential mechanism 49 with the result that the average provided by the cage 48 is zero.
• the speed of the cage 48 thus varies in the desired way with respect to the speed of the input shaft 11. It is transmitted in the appropriate direction to the ring 16 so that it rotates in the opposite direction of the shafts. entrance and exit 11 and 12.
• the torque to be applied to the ring 16 must be in the same direction as its rotation.
• the generator 32 must be driving for the ring 16 and not mechanically resistant.
• the assembly of the generator was reversed with respect to the previous examples, so that its rotating stator 34 is on the side of the ring 16, and its rotor 33 is on the side of the speed reference, that is to say say in a fixed ratio with one of the input and output shafts, in this example the output shaft 12.
• the overdrive ratios in the gears 56 and 57 as well as between the ring gear 16 and the cage 48 are carefully selected to optimize the law of the relative speed between the stator and the rotor in the gearbox. regulating apparatus 32.
• FIG. 7 constitutes another modification with respect to the embodiment of FIG. 5 and will therefore be, like the mode of FIG. 6, only described for its differences with respect to that of FIG.
• the kinematic interruption, with dynamic coupling by the control device 32 is again placed in the second transmission path or output path T2, but this time between the sun gear 14 of the first mechanism 13 and the toothed wheel 28.
• the intermediate shaft 21 is now interrupted.
• the rotor 33 on the one hand and the stator 34 on the other hand are coupled to the sun gear 14 and respectively to the toothed wheel 28 by multiplying gears 61, 63 and 62, 28.
• the tooth ratios are, for example, chosen for that the rotating elements 22 and 23 which is coupled to the sun gear 14 rotates faster than the other.
• FIG. 8 will only be described for its differences with respect to that of FIG. 7.
• the two differential mechanisms are coaxial along the general axis 31.
• the input transmission path T1 is a rigid coupling of the input shaft 11 with the planet carrier 17 and with the sun gear. input 51 of the mechanism 49.
• the third transmission path T3 is a bell 64 rigidly connecting the ring 13 and the cage 48.
• the sun gear 14, the intermediate shaft 21 and the toothed wheel 63 form a freely rotatable tubular assembly around the input shaft 11.
• the toothed wheel 63 is located on the side of the helix 1 relative to the sun gear 14.
• the two differential mechanisms 13, 49 are placed spatially between the gears 63 and 28. This embodiment is functionally close to the previous one. It requires fewer gears.
• the second differential mechanism 49 undergoes substantially the same torques as the first mechanism 13, and no longer couples reduced by overdrive as was the case in the preceding examples.
• FIG. 9 The embodiment of FIG. 9 will only be described for its differences with respect to that of FIG.
• a first series of differences concerns the differential mechanisms 13, 113 which have an identical architecture, in accordance with that of FIG. 1, and identical tooth ratios. Preferably, these two mechanisms are identical components, so as to simplify manufacturing, reduce costs and stocks of spare parts.
• the first transmission path T1 rigidly connects the input shaft 11 with the two planet carriers 17, 117.
• the second transmission path T2 rigidly connects the two planet wheels 14, 114 and the output shaft 12.
• the third transmission path T3 connects the two rings 16, 116 through a kinematic interruption bridged by a dynamic coupling which will be described later.
• the two differential mechanisms are identical, and their planetary wheels 14, 114 rotate in a single block as well as their planet carriers 17, 117, the two rings 16, 116 rotate at the same speed also, and in the same way.
• the rotating elements 22 and 23 have different speeds of rotation because they are coupled by multiplying gears 66, 166 having slightly different ratios, with the crown 16 and respectively with the crown 116.
• the speed difference between the elements 22 and 23 is proportional to the speed of the rings 16, 116, which itself depends on the transmission ratio Vs / Ve.
• the dynamic action exerted by the regulating device 32 makes it possible to influence the difference in speed between the elements 22 and 23, and thus on the overall transmission ratio.
• Another series of differences, independent of the first, relates to the mode of dynamic coupling between the elements 22 and 23.
• the rotor 133 and the stator 134 are no longer directly connected each to one of the elements 22 and 23.
• a means has been installed between the elements 22 and 23 to produce a speed representative of the difference between the speeds of the elements 22 and 23.
• a conventional architecture differential 141 performs this function provided that the shafts 22 and 23 rotate in directions opposed. That is why the multiplier gear 166 comprises an inverter pinion 142 while such a pinion is not provided in the multiplier gear 66.
• Each of the elements 22 and 23 is connected to a respective one of the two planetary gears. input 143 of the comparator differential 141.
• This mode of dynamic coupling is particularly advantageous because it considerably reduces the speed of the rotor and makes it possible to fix the stator of the regulating apparatus.
• the assembly is therefore much more conventional, we no longer need rotating contacts for the stator.
• FIG. 10 The embodiment of FIG. 10 will now be described from its differences with respect to that of FIG. 9.
• the two rings 16, 116 are now rigidly connected to one another.
• the output transmission path T2 connecting the two planetary wheels 14, 114 comprises a kinematic interruption bridged by a dynamic coupling of the same kind as that described in FIG. 9.
• the difference in speed between the rotary elements 22 and 23 would be constant because proportional to the rotational speed of the output shaft 12. Nevertheless, the torque of the generator 32 could be set to regulate the transmission ratio. In other words, the regulation of the rotational speed of the output shaft 12 would at the same time constitute a regulation of the rotational speed of the rotor of the generator 32.
• this embodiment can be achieved with two differential mechanisms such as that of Figure 6, that is to say, single satellite and reverse rotating crown.
• Two differential mechanisms such as that of Figure 6, that is to say, single satellite and reverse rotating crown.
• One can even consider running with a rotating ring alternately in one direction and the other.
• This makes it possible to operate a single-satellite differential mechanism as described in FIG. 6 between a transmission ratio from 30: 1 (crown rotating in reverse at approximately 13.5 times the speed of entry) and a transmission ratio of 1: 1 (crown rotating in the same direction and at the same speed as the input shaft) .
• FIGS. 11 and 12 represent variants for the comparator differential.
• the two planet gears 143 have different diameters and the satellites 144 have oblique axes.
• the cage 141 rotates at a speed proportional to that of the elements 22 and 23 when they have the same speed. With reference to FIG. 9, it is no longer necessary to provide different ratios for the overdrive mechanisms 66 and 166. It is sufficient for one to be an inverter and the other not to be.
• each satellite 144 has two coaxial teeth meshing with one of the planetaries 143.
• the two planetaries 143 are placed on the same side of the axes of the satellites.
• the dynamic coupling system with differential comparator is transferable to other embodiments, in particular those of Figures 4 to 8.
• the comparator differential may be other than the cage type.
• one of the rotary elements could be connected to the ring gear of a conventional planetary gear train, the other rotary element to the planetary wheel of the epicyclic gear train, the two rotary elements rotating in reverse, being driven by multiplier devices having transmission ratios for example turning the crown about half as fast as the planet wheel so that the velocity of the planet carrier is low.
• the kinematic path TC and the dynamic path TD could be installed between the input shaft 11 and the differential mechanism 13.
• the speed difference between the two rotary members 22 and 23 has been described as increasing as the speed of the input shaft increases and the transmission ratio decreases.
• this direction of variation of the speed difference between the two rotary elements contributes to the regulation of the transmission device.
• the regulating device 32 also has, in general, a characteristic of increasing its torque as a function of the speed. But it is also conceivable to ensure that the difference in speed does not vary or varies in the opposite direction to that just discussed.

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